1892 
WATER and AIR 
Circulation 
, IN HEATING 
AND VENTILATING 
ABRAM COX 
5T0VE CO. 
PH I LA. WATER AND AIR 
CIRCULATION 
IN 
HEATING and VENTILATING. 
PHILADELPHIA: 
ABRAM COX STOVE CO. 
1892, Copyrighted, 1892, 
By Abeam Cox Stove Co., 
PHILADELPHIA. Salutatory 
SHIS treatise is addressed to all who are in any way interested in the subject of 
house-heating. We offer it to heating engineers who through this means will 
learn of the new apparatus we have brought out; they will likewise find in it 
much of value in their professional work. We also commend it to architects to 
2 whom the proper heating of buildings is a very important matter; to plumbers 
who are more and more entering into the work of house-warming, and finally 
we address our friends and customers in the furnace trade, many of whom are supplementing their 
business in hot-air furnaces with the sale and erection of heating apparatus of other kinds. 
This book, which has been prepared with the greatest care and at much expense of time, labor, 
and money, contains, we believe, more practical, more reliable, and more complete information than 
can be found anywhere else. We have endeavored to present the subject of water and air circulation 
in heating and ventilating in such simple language as to make it equally plain to journeymen, 
engineers, and architects. It will be noticed in the selection of buildings for illustration, that we have 
chosen examples to represent the various constructions to which the hot-water system is ordinarily 
applied. In each case floor plans and elevations are presented, while in the text accompanying the 
drawings are given all measurements and other information required to install a successful plant in 
the building illustrated. Rules and formulas are also given by which any intelligent mechanic can 
determine the number of the circulator to be employed, the square feet of radiation necessary, size 
and quantity of pipes, etc., required in buildings of similar design and construction. 
The data made use of have been largely compiled from experiments and tests made on our own 
premises, and under conditions commonly met in daily practice. They are therefore much more 
reliable than figures ordinarily given in trade publications, and which are often taken from foreign 
authors who are unfamiliar with American practice and whose instructions are not suited to the 
American climate and conditions. 
We make no mention of the Hovelty Circulator in this place further than to say that while 
it is new in design it is not an untried apparatus. During the past two years it has been in continuous 
operation under all possible conditions which have given it the severest test, and as now placed before 
the public it is a perfect apparatus for liouse-heating. 
ABRAM COX STOVE CO. 
Philadelphia, April, 1892. 
3 Circulation; 
JOHN J. HOGAN. 
HE arrangement of fire and flue surfaces, so as to present the greatest area of each in 
the most advantageous position to receive heat, is generally thought to be of 
first importance in designing boilers, but the extent of these surfaces and their 
|| arrangement with respect to the fire is really of little account if their form be not 
1 ivy such as to promote circulation. The amount of heat transferred from fire to water 
is controlled almost absolutely by the velocity of circulation of water within the 
boiler. 
THE TRANSFERENCE OF HEAT. 
As circulation is effected by heat, it is necessary, in examining the subject of circulation, to 
remember that heat is transferred from one body to another in one of three ways, and in no other way. 
It is transferred either by radiation, convection, or by conduction. 
By radiation heat passes from the radiant body to the absorbent body through the intervening 
medium, as, for example, air, without raising its temperature. The sun gives heat by radiation, and 
it will be noticed that the rays pass through window-glass, for illustration, warming objects beyond the 
glass, as, for instance, the furniture in the room, or the floor, without raising the temperature of the glass. 
The rays of the sun may be passed through a lens in a way to set on fire the object upon which they 
are focused without raising the temperature of the lens itself. A slab of ice may be substituted for 
window-glass, and the rays of the sun, passing through the ice without melting it, will still be per- 
ceptibly warm to the person or will add heat to other objects upon which they may fall. 
Radiant heat reaches the absorbent in radial lines, i.e., straight lines, and its intensity is inversely 
as the square of the distance traveled. This is an important fact, because it bears upon the location 
of the fire with reference to the heat-absorbing surfaces upon which the fire is to act. This principle 
is illustrated in the accompanying diagram, Fig. 1. Point 2 in this sketch is twice the distance from 
the candle A of point 1. A unit of surface, say one square foot, placed at the point indicated by 2 in 
the sketch, receives only one-fourth the quantity of heat that it would if it were placed at 1. At three 
times the distance, or at point 3, the unit receives only one-ninth the quantity that it would at 1, 
and so on. 
The convection of heat is the process of carrying it from one body to another, and is performed 
by fluids, such as water, gas, or air. It is through convection that heat is carried by steam or water 
* Copyrighted, 1892, by John J. Hogan, New York. 
5 6 
THE NOVELTY CIRCULATOR. 
from a boiler to the radiators, and also from indirect radiators or a turnace by means ot air to the 
bodies of lower temperature with which the air comes in contact. To transfer heat by convection 
the fluid which conveys the heat must have motion. It must move from the body of higher tempera- 
ture to the body of lower temperature. This is an important fact, and should be borne in mind in 
planning all sorts of heating systems. If in the use of indirect radiators the air-passage is stopped, 
the useful work at once ceases, and in the same way in steam and hot-water circulation if the flow of 
the fluid through the pipes is stopped the work of heating is also interrupted. Again, if motion to 
the fluid in a heater or boiler is stopped, the useful action of the tire is interfered with. 
Conduction is the transference of heat by direct contact. If a bar of iron be put into a black- 
smith’s forge and heated at one end to a red heat, it will be found that gradually the temperature of 
the opposite end will rise. The heat is transferred from 
the hot end toward the cold end by direct contact of parti- 
cles in the bar. To still further illustrate conduction, it 
may be stated that the heat that is given to the tire side of 
the heating surface of a boiler by radiation from the fire, 
and by the convection of the gases of combustion, is trans- 
ferred by conduction to the opposite side of the surfaces, 
and is there given to the water in contact with them, and in turn is carried oft* by convection- 
currents as already explained. 
Fig. i.—Diagram Illustrating the Intensity of Radiant 
Heat as Influenced by Distance. 
THE CAUSE OF CIRCULATION. 
Natural‘circulation is the operation of the law of gravity exerted upon two columns of fluid, 
as, for example, air or water, when the two columns are of unequal density and are joined at their 
extremities. The columns may be in separate passages or flues, or they may exist side by side in the 
same vessel in any number of pairs. The inequality of density is caused by the application of heat 
to the body of the fluid in one of the columns at some point below its top, or the abstraction of heat 
from the other. That part of the body which is immediately exposed to the heat is expanded in vol- 
ume, and is thereby made lighter than the parts which are unexposed to the heat. The expanded and 
lightened particles are displaced by the colder and denser particles falling by gravity. The latter take 
the places of the warmed particles, and when they have become warmed are driven forward by still 
other colder particles falling into their places. 
This exchange of places of particles, or circulation of air or water, is continuous so long as the 
two columns are prevented from establishing an equilibrium through an equality of temperature. In 
other words, circulation goes on as long as heat is communicated to one column or lost by the other. 
Circulation is the most rapid when the difference in temperature or of density of the two columns is 
the greatest. This condition is best secured when the column of high temperature and the one of 
low temperature are confined in separate passages or Hues. This is because the temperatures of the 
two columns are more easily maintained at the maximum difference, when the opposing columns are ABRAM COX STOVE COMPANY. 
7 
prevented from mingling. A mixture of tlie particles of the two columns tends to an equalization of 
temperature. A common example of the equalization of temperature due to the mingling of currents 
of the two columns is afforded by a kettle of water upon an ordinary cook-stove where the entire bot- 
tom of the kettle is equally exposed to the action of the heat, as shown in Fig. 2. As heat is im- 
parted to the water a circulation is established by the expanding water rising to make place for the 
colder and denser water which descends, but as the opposing currents are unconfined they come into 
more and more intimate contact until the entire body of water approaches a uniform temperature. 
With the continuous application of heat to the bottom of the kettle, steam globules form there which, 
instead of being displaced by the water as they would be with circulation pro- 
moted by separate ways, are held back by the mass above them. The result of 
the conflict of currents is an upheaval of water, so that if the kettle has been 
filled anywhere nearly full in the first place it soon boils over. 
A familiar illustration of circulation promoted by separate passages, tubes 
being provided for the ascending column, is afforded by a kind of wash-boiler 
attachment, which is sold in many parts of the country, a diagram illustrating 
which is given in Fig. 3. In this A A indicates the boiler, B the fire against the 
bottom of the boiler, C the base of the attachment which is open at the bottom 
and perforated along the edge so as to allow the free passage of water within, 
I) D are two spouts or tubes that extend upward from the base and are provided with curved necks. 
The water as it becomes heated is forced up these tubes, as shown by the direction of the arrows, by 
the weight of the descending column which rushes into the holes in the rim of the base already re- 
ferred to. Particles of steam which are generated after the heat has been maintained for some time 
co-operating with the weight of the descending column force the water up the tubes D with such 
power as to carry it above the level E of the water in the 
boiler. This is an example of assisted circulation. The 
apparatus here sketched is something that is frequently sold 
in the trade for laundry purposes. The accelerated circu- 
lation of water which is secured in it is depended upon 
to do part of the washing. If the tube were to be carried up 
straight instead of being bent, as shown in outline at the 
right, the result would be a spouting into the air. 
Referring again to the kettle illustration, Fig. 2: If 
the vessel is so set into the fire-space as to be exposed on 
the sides as well as on the bottom to the action of the heat, as 
indicated in Fig. 4, the results described in connection with Fig. 2 are more quickly reached. 
Again, if instead of a kettle we take a horizontal vessel closed at the top but with ends open 
and extended upwardly, as shown in Fig. 5, the conflict of currents will be still further illus- 
trated. AVdien steam forms, as it will by continued application of heat along the bottom and sides, 
the tendency is to drive the water within the vessel through the upturned ends, and it will thus empty 
Fig. 2.—Mingling Currents 
in Boiling Water in a Common 
Kettle with Fire Applied at 
Bottom. THE N 0 V E L T Y Cl R C U L A T 0 R. 
8 
itself if the heat is continued long enough. If in our experiments we employ a vessel of the shape 
shown in Fig. 6, which has a hollow center, leaving two water columns or legs with the tire applied 
under each column, the conflict will be the same as in the last instance. It the heat is applied evenly 
to the two legs, as shown, and is of sufficient intensity and maintained long- 
enough, it will blow the water all out. 
If, on the other hand, the same shape is employed and the heat is applied 
to one leg only, as shown in Fig. 7, circulation will be promoted. The column 
directly over the fire will be the ascending column, while the opposite, containing 
the relatively colder fluid, will be the descending column. The hotter the fire, 
providing the descending column is giving off heat, the more rapid will be the 
circulation. In this case there is no intermingling of currents of different 
temperatures, and the maximum difference of temperature between the two 
columns is realized. It is under such conditions that the utmost rapidity of 
circulation is secured. 
In Fig. 8 there is shown a vessel com- 
posed of three columns, with the fire applied 
directly under the central column. The con- 
ditions here shown are favorable to circulation. 
The central column will be the ascending 
column because the water contained in it re- 
ceives the heat of the fire, while the outside 
columns will be the descending columns because they contain what is relatively 
colder fluid. If, however, heat be equally applied under the three columns, as 
shown in Fig. 9, the result will be impeded circulation, because the currents of 
the respective columns mingle in each of the divisions of the vessel. This is 
indicated by the broken and twisted arrows shown in the diagram. Fig. 10 
shows a vessel with two columns or water-legs with fire applied above the lowest 
point and to the sides of the legs equally. In this case circulation is impaired 
by reason of the intermingling currents and because the two columns are of 
equal density. Extending water-legs downwardly from such a vessel, as is shown 
in Fig. 9, and applying the heat equally between the legs, as shown in Fig. 11, 
does not affect the results as last described, but produces mixed and conflicting 
currents, as indicated by the arrows in Fig. 11. 
To go back to the original proposition, namely, that the circulation in a vessel is most rapid 
when the difference in temperature of the two columns is the greatest, and when the two columns of 
high and low temperatures are confined in separate passages so as to preserve the difference, it follows 
that the form illustrated in Fig. 19, which affords separate ways for ascending and descending columns 
and at the same time transfers heat only to the ascending column, must give the most rapid and 
positive circulation. 
Pig. 4.—Mingling Cur- 
rents in a Vessel Exposed to 
the Fire at Both Bottom 
and Sides. 
Fig. S-—Conflict of Currents in a Vessel with Closed Top and Open Upturned 
Ends. 
Fig. 6.—Currents in a Ves- 
sel with Hollow Center, with 
Heat Applied under Both 
Columns. ABRAM COX STOVE COMPANY. 
9 
VALUE OF CIRCULATION IN HEATING WATER. 
Water is a good absorbent, but a bad conductor of beat. A given particle of water very 
slowly yields the beat that it possesses to the colder surrounding particles. This has been expressed 
by an eminent writer in the following words: 
“ Water is so bad a conductor that it is only when there exists perfect 
freedom of motion among its particles that it acts at all as a conductor of heat, 
so far at least as regards any practical and useful effect.” 
Another authority says,— 
“ The quantity of heat which can be transmitted to water in a given time 
is only limited by the rate at which it can be carried away from the heating sur- 
faces by the convection-currents.” 
Still another quotation from the same authority may be offered in this 
connection: 
“ Heat can only be effectively ab- 
stracted by liquids from heated surfaces 
by circulation of the liquid, and rapid circulation is essential 
to rapid abstraction of heat.” 
Fig. 7.—Vessel with Two 
Columns, with Heat under 
One Column only. 
These peculiarities of water, so far as heat is concerned, 
may be empha- 
sized by some 
easily performed 
experiments. An 
illustration of its 
absorbent capac- 
ity may be supplied as follows: Form a vessel out of 
writing-paper or any other paper that does not readily 
absorb water. Make it water-tight by folding the edges 
and fastening them in place by pinning near the top of 
the corners. Partly fill this vessel with water and hold 
over a flame. This is very readily done by setting the 
paper vessel on the open work of a gas stove. The gas 
should be lighted after the paper has been placed in 
position. Under these circumstances the heat is so rapidly absorbed by the 
wTater that the paper is not injured by the flame. Water may be even boiled in a paper vessel in the 
way described without scorching the paper. 
The inability of water to conduct heat may also be shown by an experiment. Let a combus- 
tible fluid like alcohol be floated on the surface of water in a vessel. Light the alcohol. It will be 
Fig. 8.—Vessel with 
Three Columns, with Fire 
Applied under the Central 
Column. 
Fig. 9.—Vessel with 
Three Columns, with Fire 
Applied under all the Col- 
umns. 
Fig. ii.—Modification of 
Fig. 9. Water-legs carried 
down and fire evenly distrib- 
uted showing same results. 
Fig. 10.—Vessel withTwo 
Columns or Water-legs, with 
Fire Applied above the 
Lowest Point and to Sides of 
Legs Equally. THE NOVELTY CIRC (TLA TOIL 
10 
found that the latter will be consumed without raising the temperature of the water appreciably, even 
though the quantity of alcohol so burned is sufficient to evaporate the entire body of water if applied 
underneath. If applied underneath, the particles of water would take up the heat by convection, 
resulting in phenomena already given in this chapter. 
Still another experiment illustrating the inability of water to conduct heat may be described. 
If into a vessel containing cold water hot water be carefully poured the latter will spread out over 
the top of the colder water and will give off more of its heat to the air above than to the cold water 
below. This experiment may be tried in a bath-tub when in the act of bathing. If the water sur- 
rounding the person is comparatively cold and a small stream of hot water be allowed to flow into the 
bath-tub, it will be found that the hot water will spread out over the surface of the colder water in a 
way to produce a stinging sensation where it comes in contact with the person. Agitation of the 
water, producing currents, will, on the other hand, distribute the heat through the entire body of water. 
Since motionless water is comparatively incapable of transferring heat, it follows that the tem- 
perature of a body of water cannot be raised except by bringing each particle into contact with heat- 
ing surfaces or by mixing together particles of high and low temperature. We have seen in Fig. 2 
that with a mingling of particles irregularly performed less advantageous results follow than when 
separate passages are provided, as illustrated in Figs. 3, 7, 8, and 19. There are, then, two ideas pre- 
sented : first, of irregular indefinite currents in the body of water in which the hotter particles slowly 
share their heat with the colder particles with which they mingle, and second, the idea of directed 
movement by which every particle of water is brought into contact with heating surface and allowed 
to take up all the heat it is capable of absorbing. When water is warmed chiefly by the mingling of 
currents the process is accompanied by much friction and consequent loss of energy, or, what is the same 
thing, waste of heat. Further, as has already been shown, the result of heating water in this manner 
is the gradual stoppage of circulation with the ultimate effect of forming steam and raising pressure 
at points where it is not only not desired to have pressure, but where pressure is decidedly harmful. 
Surfaces which do not promote the direct contact of water with them by reason of the globules of 
steam formed thereon are relatively feeble transmitters of heat. Under these circumstances 
heat is transferred to the water by convection, or more correctly speaking, by mingling currents. 
For this reason the area of surfaces heated in this manner must be necessarily greater than 
where the water to be heated is brought in direct contact with the heating surface by the proper 
disposition of the ascending and descending columns. A recent writer on boiler construction discuss- 
ing this point says,— 
“ The heating surfaces should be arranged to facilitate the movement of the convection-cur- 
rents and promote free circulation. This is effected in the best manner when the heat is applied 
underneath the water to be heated, and when the shape and position of the heating surfaces facilitate 
the free escape of the heated water in its upward current and the return of the cooler water in its 
downward current.” 
It may be accepted as a fact, then, that water is heated most economically by the contact of 
each particle with heating surface rather than by mingling currents of high and low temperature. A B R A M C OX S T 0 VE C 0 M PA N Y. 
11 
Circulation which brings the particles of water into direct contact with the heating surfaces is accom- 
plished by a separation of the ascending column of heated water from the descending column of 
colder water. This arrangement brings only the particles of lowest temperature into contact with 
the heating surface, which, by reason of their low temperature, are most capable ot absorbing heat. 
It is well known that the capacity of water for absorbing heat is in proportion to the difference in 
temperature between the water and the heating surface. Thus, with fire surfaces at 800° and water 
in contact with them at 100°, the rate of heat transmission may be expressed as 8 —1 = 7. Again, 
with water at 200° and with fire surfaces as already given, the rate of transmission would be expressed 
as 8 — 2=6, or equivalent to one-seventh less. It is apparent from 
this, that any construction which tends to keep water of high tem- 
perature against the fire surfaces is a relatively poor heater, because 
of the comparative inability of water of high temperature to absorb 
heat. Again, if the heat is sufficient to form steam globules upon 
the water side of the surface, the absorbtive efficiency is still 
further diminished. 
Pig. 12.—Adaptation in Practice of Forms 
Shown in Figs. 2 and 10. 
Fig. 14.—Adaptation in Practice of Forms 
Shown in Figs. 2 and 10. 
Pig. 13.—Adaptation in Practice of Forms 
Shown in Figs. 2, 9, and 11. 
Another advantage following upon the use of two passages, one for the descending column and 
the other for the ascending column, so arranged as to cause each particle of water to pass over the 
heating surfaces, is that there is no loss of heat through friction between ascending and descending 
currents. In other words, there is no retardation of circulation through conflict of currents. Again, 
there is no chance for the formation of steam on the inside of the fire surfaces, either to the extent of 
interfering with the transference of heat to the water or of producing pressure. THE NOVELTY CIRCULATOR. 
12 
ADVANTAGES OF INDEPENDENT CIRCULATION. 
The value of independent internal circulation at the heating point, in promoting circulation in 
a system of pipes and radiators, is next to be considered. In Figs. 2 to 11, inclusive, the effect of heat 
upon the circulation of a fluid contained in vessels of certain forms has been indicated, so far as cir- 
culation is confined to the vessel itself. To make a practical application of the illustrations let us 
Fig. 15.—Adaptation in Practice of Forms 
Shown in Figs. 4, 5, and 10. 
Fig. 16.—Adaptation in Practice of Forms 
Shown in Figs. 4, 5, and 10. 
Fig. 17.—Adaptation in Practice of Forms 
Shown in Figs. 9,10, and 11. 
adapt tlie forms to the heating of water for warming purposes in connection with a system of pipes 
and radiators. What is shown in Fig. 12 is adaptation in practice of the forms shown in Figs. 2 and 
10, and may be described as a drop-tube boiler. Each drop-tube, it will he noticed, is equivalent to 
the kettle shown in Fig. 2. The diaphragm or partition which separates the column of water in the 
drop-tube into two parts does not sufficiently destroy the equilibrium between the two columns to 
establish vigorous circulation. Whatever circulation takes place in the tube is a local circulation 
which is entirely nullified when the particles rise to the top of the tube and are compelled to inter- 
mingle with those in the body of water around the mouth of the tube. Excessive firing in this form ABRAM COX STOVE COMPANY. 
13 
will ultimately stop circulation and blow the water out of the tubes by the formation of steam in their 
extremities. Whatever heat is given off by the tire to the water-legs at the sides of the boiler results 
in the same action as was described in connection with Fig. 10. 
Circulation is impaired by mingling currents. 
Fig. 13 exemplifies in boiler construction the features of 
circulation illustrated in Figs. 2, 9, and 11. The columns of 
water over the fire in this case receive heat equally, which, as 
we have shown, is opposed to circulation. This is still further 
proved by the fact that boilers of this kind, when used for steam 
purposes, frequently prime and produce very wet steam. Inas- 
much as the heat is given equally to the several water-spaces 
around the fire, the result produced is the same as that illustrated 
in Fig. 9, and again illustrated, so far as the water-legs and side- 
passages are concerned, by Fig. 11. 
The design of boiler shown in Fig. 14 results from an 
' effort to increase the surfaces within the fire-pot. Fire ascends 
in the central column, and, striking the crown-sheet, produces the 
Fig. 18.—Adaptation in Practice of Forms 
Shown in Figs. 9,10, and 11. 
same results as shown in the case of 
the pot in Fig. 2. Again, whatever 
heat is given oft' at the sides has the 
same action as was explained in con- 
nection with Fig. 10. Tho result is 
that the entire body of water is heated 
by mingling currents. 
In Figs. 15 and 16 are shown 
adaptations in practice of the forms 
shown in Figs. 4, 5, and 10. The water 
passages have tire beneath and around 
them, as shown in Fig. 4, and are 
liable to blow out by the formation of 
steam, as illustrated in Fig. 5, and as 
described in connection with that 
figure. There are also water-legs 
which, although not connected at the 
bottom, as shown in Fig. 10, contain motionless water which cannot be brought into circulation by 
the heat as applied. Steam boilers having water-legs of the type shown in Figs. 15 and 16 are noted 
Fig. 19.—Diagram of Circulating System. 14 
THE NOVELTY CIRCULATOR. 
for the accumulation of sediment in these parts, which fact is still turther proof of the lack of circu- 
lation therein. Boilers of this design, with small increase of tiring, produce steam in the sections 
immediately next to the tire, thus maintaining the water in them at temperatures relatively higher 
than that of the upper sections, producing pressure opposing the inflow of the return water, and im- 
peding the circulation of the entire system. 
Figs. 17 and 18 exemplify forms of construction illustrated 
in Figs. 9, 10, and 11. There is the equivalent of the central 
column shown in Fig. 9 and two outside columns, but free circu- 
lation is not possible because the heat is equally applied under 
the three columns. The water-legs contain motionless water for 
reasons explained in the last instance, and as shown in Figs. 10 
and 11. 
With the impaired internal circulation that is shown in all 
these examples, the warmed water can never rise freely. It 
follows, then, as in the case of the kettle in which the excess of 
temperature resulted in boiling over (Fig. 2), pressure is gener- 
ated at the return opening, the effect of which is to retard the 
general movement of the water contained in the system. What 
is variously called the “belt principle,” “ positive circulation,” “continuous circulation,” etc., shown 
in Figs. 15 and 16, being the development of the principles explained in Figs. 4 and 5, in which 
there is no provision whatever for internal circulation, the general movement of the water is toward 
the points of discharge into the flow pipe, but it comes into interference continually with the 
colder water in the upper passages which is endeavoring to find its proper place at the bottom of 
the boiler. The result, at best, is a feeble and embarrassed advance. In addition to the retarding of 
the water by the conflict of currents, the narrowness of the passages with which these boilers are 
ordinarily provided also tends to produce pressure at the return opening. 
To quote one of the greatest authorities upon boiler designing: 
“ When water-spaces are so cramped that the ascending and descending currents cannot flow 
separately, circulation cannot take place, and the water is put into a state of perturbation.” 
By this is explained the curious fact that with certain forms of waterways increased applica- 
tion of heat not only does not increase circulation in the system, but actually stops it so that the pipes 
and radiators are at a lower temperature with a forced tire than with a moderate fire. 
In Fig. 19 is shown a diagram of a circulating system. It illustrates the application of the 
principles of rapid independent internal circulation in the heat source, as exemplified in Figs. 3, 7, 
and 8. In this the effect of rapid firing is found to be a vastly increased circulation in the entire sys- 
tem instead of the retarded movement which occurs in all other forms. The higher the temperature 
at B and B, the greater is the velocity of descent in the columns D and E E. It is easier for the water 
to descend through E E than to ascend and overflow at P, because in absorbing heat at B' no pressure 
is produced to resist or impair the descent in E E or D. At D' the temperature of the water from E 
Fig. 20. —Adaptation in Practice of Figs. 3, 7, 
and 8. ABRAM COX STOVE COMPANY. 
15 
is increased by mingling currents from D, but at B' the heat is taken up by the water directly in 
contact with the fire surface. 
Fig. 20 exemplifies the practical application in a working apparatus of the form shown in Figs. 
3, 7, and 8. In this design the heat is applied only to the ascending column of water, and the outside 
descending columns are comparatively cold. Though separated from the ascending columns they have 
continuous communication with them at the intersection of the cross passages, thus inviting the easy 
descent of any particles of water in them or in the cross passages which may be of relatively low tem- 
perature. It will be observed that the outside column is provided with a series of downward project- 
ing tubes, so arranged as to deliver descending particles of water from each section at a point some- 
what lower than the portions in the same sections which receive the greatest heat from the fire. This 
construction results in the separation of the ascending and descending columns and is a mechanical 
means of maintaining a condition of inequilibrium between the two columns. It also results in such a 
disposition of the twTo columns of water as to produce a line of greater resistance in the direction of the 
descending column and of less resistance in the direction of the ascending column so far as would be 
affected by the generation of steam in the event of hard firing. This arrangement of parts in turn, 
referring now to the cross passages in combination with the tubes extending downwardly in the outside 
or cold columns, serves to separate and sort the particles of water in a way to keep the hotter particles 
in the center or ascending column, and allow free passage of the colder particles in the direction of 
the descending column. The only conflict from mingling currents that can occur in this type of boiler 
is in the limited space of the cross passages, and here they result in separating particles of unlike tem- 
perature and conducting each class to its own appropriate place in the hoiler without impairing or 
retarding the circulation of the boiler as a whole. The Novelty Circulator 
TWO views of the Xovelty Circulator are presented herewith, one the exterior appearance, and the 
other a vertical section showing the grate, fire-brick linings, water ways, etc. There are also 
presented views of the parts of which the circulator is composed. Referring to the latter, it 
will be seen that there are five in all, namely: the ash-pit, the fire-brick lining, the fire-box, 
the intermediate section, and the top section. The ash-pit, which is of liberal height, contains the 
grate and is provided with doors of ample capacity for removing ashes. These doors, in turn, carry 
Fig. 2i.—Exterior View of the Novelty Circulator. 
Fig. 22.—Vertical Sectional View of the Novelty Circulator 
the draft-doors, which are lifted with latches and adapted to be set as circumstances require. The 
center of the grate is of the anti-clinker variety, and is of such a form as to be revolved by a crank 
in a way to dump ashes, throw down clinkers, and that, too, without danger of dropping the tire. 
The outside part of the grate is arranged to shake by means of the shaking-arm shown in the cut. 
All the shaking may be done while the ash-pit and clinker-doors are closed, thus avoiding all dust. ABRAM COX STOVE COMPANY. 
17 
The shell of the fire-brick lining is a circular frame 
joined at intervals by vertical partitions. The bricks occupy 
the spaces between these vertical partitions, and are put in 
place from the outside, an arrangement of parts permitting 
the exchange of an old brick for a new one without drawing 
the fire. This feature of construction is peculiar to this ap- 
paratus, and is of great advantage. The bricks are held in 
place by hollow frames of cast-iron. The frame which holds 
the front brick is hinged, and is so arranged as to form a 
door, and gives access to the fire for cleaning, stoking, etc. 
It is provided with a bracketed shelf, which carries the 
lining-brick when the door is swung. 
The fire-box (A) is a casting containing two annular 
water-spaces around the fire, the inner one of which is con- 
nected by radial inclined arms with the central water way 
immediately over the center of the fire, while the other is con- 
nected with two outside water ways in the lugs or projections 
at the sides. The return water of the system enters the outer 
annular space at the back of the fire-box and passes around 
to the front, at which point the division between the two 
annular spaces is cut away. The central water way and the 
two outside water ways join corresponding parts in the 
section above, and thus provide a separate passage for the 
ascending and descending columns respectively. 
The intermediate section (B) of the Novelty Circulator 
contains an annular water-space or water-jacket connected 
with the central column by radial arms, the spaces between 
the arms forming smoke passages. From the annular water- 
space lugs are extended at the sides which connect with 
corresponding lugs on the sections above and below. The 
radial arms in this section are so disposed as to be staggered 
over those of the fire-box, thus presenting their surface to 
the radiant heat of the fire. Further, the opposite sides of 
this section are unlike; that is, the number of radial arms 
is odd, not even, and it is adapted to be used either face to 
the front. Where there is more than one intermediate 
section used they are reversed, thus continuing the staggered 
order mentioned. The central water way joins the corre- 
Fig. 23.—The Sections Composing the 
Novelty Circulator. THE NOVELTY CIRCULATOR. 
18 
sponding part of the fire-box below and of the section above. The top section (C) of the Novelty 
Circulator is very much like the intermediate section just described, except that the radial arms are 
replaced by a continuous water way connected with the central ascending water way and also with 
the two outside descending water ways in the lugs already referred to. All three of the water- 
sections, namely, fire-box, intermediate section, and top section, communicate freely through the 
central ascending water way and through the two outside descending water ways. 
The several sections of the Novelty Circulator are joined together by means of nipples in the 
outside water ways, as clearly shown in the sectional view. No bolts are used. The nipples project 
downwardly in the water ways, as will be seen by an examination of the view just referred to, in a 
manner to afford additional safeguard against the mingling of currents of different temperatures. 
In the arrangement of water ways it will be seen that the Novelty Circulator completely 
answers the requirements of perfect circulation. It also meets the demands of good design, such as 
large direct fire surface, ample flue area, accessibility of flue surfaces for cleaning, easy water ways, 
and vertical circulation. It goes still further than this, for in the completeness of its adherence to 
natural laws this apparatus realizes an ideal development. This becomes manifest by an examination 
of the sectional view, and is thoroughly proven by its performance. In operation the water in the 
fire-box is always lower in temperature than that in the upper sections. This is due to the rapidity 
of the internal circulation. The result is the most economical working, because the relatively cooler 
water is always kept against the fire surface, thus taking up the maximum of heat. 
By reason of its rapid and powerful circulation the Novelty Circulator can be depended upon 
to perform satisfactorily under conditions which render other forms of hot-water heating apparatus 
entirely inoperative. It circulates water in a system on the same level with the boiler, with an open 
expansion tank, as low as five feet above the top of the circulator, and with all the radiating surface 
below the top of the circulator, and much of it below the fire-box. This is a feat quite beyond the 
power of any other construction now known. 
To what do these things point? Not to the discovery of a new principle, but to the proper 
application of principles that are as old as nature,—principles which all designers of liot-water boilers 
have recognized in some degree, but to the realization of which none have previously found the key. 
These principles may be briefly stated as follows: The separation of the ascending from the descend- 
ing columns and providing each with proper ways, the maintenance of the greatest difference of 
temperature between them, and prevention of equilibrium by difference in the levels of the columns. 
The operation of the Novelty Circulator may be briefly described as follows: With the parts 
arranged as described, and a tire built upon the grate, circulation begins instantly. Particles of water 
in the bottom of the central column immediately over the tire become rarified and are driven forward 
by the weight of the colder columns at the sides of the boiler pressing downwardly and through the 
passages. As the particles of water which have become warm or rarified leave the fire surface and 
start in their upward course, their places are filled with particles of colder water advancing through 
the inclined water ways leading to the central column. In turn particles of water which become 
heated in the water ways of the several sections are similarly driven toward the central column ABRAM COX STOVE COMPANY. 
through the free passages and upward in that direction. At the same time particles of colder water 
from the exterior columns advance into their places. As the heat of the tire increases, the circulation 
becomes more rapid. 
Connections between sections, both central and at the outside, are such that complete circula- 
tion is maintained in each section independent of all others, and also in the whole apparatus as a unit. 
The downwardly projecting nipples in the exterior columns in combination with the inclined water 
passages in the sections, and the central column, serve to prevent an equilibrium between the two 
columns. The water of relatively low temperature is always at a lower level than the warmer water, 
both in the individual sections and in the apparatus as a whole, and at the same time it is in im- 
mediate contact with the tire surfaces. By reason of the descending water ways which contain water 
relatively cool, being at the exterior of the circulator, combined with the central ascending passage 
directly over the hottest fire, all crossed or mixed currents of various temperatures are avoided. 
Hard firing only drives the circulation; in no case can it impede circulation. Steam serves to rarity 
or lighten the central column, and when produced against the fire surfaces moves forward instantly. 
It never remains in a way to retard heating, and if pressure should be generated it would exert its 
force in the direction of the least resistance, which is upward in the central passage, thus still 
further promoting circulation. 20 
THE NOVELTY CIRCULATOR. 
Dimensions, Ratings, and Prices. 
THE Novelty Circulator is manufactured under 
patents granted to the Ilogau Engineering 
Company, and is supplied of the sizes and di- 
mensions shown in the table on the opposite page. The 
annexed diagram affords a key to the principal dimen- 
sions. 
Each circulator has one How and one return 
pipe only, which are always of like diameters. Ratings 
are given for each size circulator of both direct and 
indirect surface. 
The Novelty Circulator under all ordinary con- 
ditions of piping and distribution of radiation is fully 
guaranteed to supply the radiating surface given opposite 
the several sizes in the table on page 21. 
Diagram Key to Dimensions. ABRAM COX STOVE COMPANY. 
21 
TABLE OF DIMENSIONS, RATINGS, AND PRICES OF THE NOVELTY CIRCULATOR, 
NUMBER. 
Letter in 
Diagram 
1* 
2* 
3* 
4 
5 
6 
7 
8 
9 
10 
11 
12 
13 
14 
15 
16 
17 
18 
Height in inches 
Diameter in inches 
Width over all in inches. 
Diameter of ash-pit at 
base in inches 
Height of ash-pit in 
inches 
Diameter of fire-box in 
inches 
Width of feed-door in 
inches 
Height of feed-door in 
inches 
Height from floor to cen- 
ter of return in inches.. 
Diameter uf flow and re- 
turn in inches 
Diameter of smoke-pipe 
in inches 
A 
B 
C 
D 
E 
F 
G 
H 
K 
r 
\ 
V 
43 
22 
32i 
24 
13i 
16 
11 
8 
22i 
4 
7 
484 
22 
0-2 
24 
18* 
16 
11 
8 
22i 
4 
7 
53J 
22 
32i 
24 
13* 
16 
11 
8 
22i 
4 
7 
-144 
24i 
35 
27 
14 
19 
12 
«* 
23 
4 
7 
50 
24i 
35 
27 
14 
19 
12 
8* 
23 
4 
7 
551 
241 
35 
27 
14 
19 
12 
8* 
23 
4 
7 
47 
27i 
38 
30i 
14f 
22 
13* 
9 
24 
4 
8 
52f 
27| 
38 
30i 
14f 
22 
13i 
9 
24 
4 
8 
584 
27i 
38 
30i 
14f 
22 
13i 
9 
24 
4 
8 
50 
314 
42 
35 
15| 
26 
14 
9§ 
25| 
5 
9 
56 
31* 
42 
35 
154 
26 
14 
9* 
254 
5 
9 
62 
31i 
42 
35 
154 
26 
14 
9* 
254 
5 
9 
364 
46i 
40 
15i 
30 
14i 
9* 
26 
6 
9 
594; 
364 
46i 
40 
15i 
30 
14* 
9* 
26 
6 
9 
65f 
864 
46i 
40 
15* 
30 
14i 
Q1 
26 
6 
9 
551 
40i 
50i 
44i 
16 
34 
15 
10 
27 
6 
10 
62i 
404 
50i 
44i 
16 
34 
15 
10 
27 
6 
10 
691 
404 
50i 
44i 
16 
34 
15 
10 
27 
6 
10 
RATING IN SQUARE FEET OF DIRECT RADIATING 
SURFACE. 
250 
80C 
350 
350 
425 
500 
500 
625 
750 
750 
950 
1150 
115014001650 1650 
1950 2250 
RATING IN SQUARE FEET OF INDIRECT RADIATING SURFACE. 
Prices, F.O.B., Phila. 
185 
200 
285 
235 
285 
335 
335 
420 
500 
500 
630 
770 
770 
935 
1100 
11001300 
. - 
1500 
I87.5C 
100 
112.50 
120. 
135. 
150. 
155. 
180. 
205. 
210. 
240. 
270. 
280. 
320. 
360. 
* In course of construction. Illustrative Examples. 
FOR the purpose of showing how the Novelty Circulator may be advantageously installed, we 
present a number of illustrative examples indicating the runs of pipes, quantity of radiating 
surface, position of radiators, and other features of interest to steam-fitters, builders, house- 
owners, and architects. 
These examples include (1) a cottage residence, (2) a suburban mansion, (3) a city residence, (4) 
a railway station, (5) a church and school, and (6) a city office. Elevations, floor plans, and sections 
are given in each instance with enough of constructive details to make every feature of the work easily 
understood, while the text contains a description with reasons for everything that is done. In the 
calculations of surfaces frequent references are made to the rules given further on in the book. In thus 
presenting the examples before propounding the methods of calculation, we bring to the attention of 
the reader the need of definite and reliable rules and formulae, now for the first time presented, and 
at the same time avoid tiring him with pages of tabular work preceding the illustrations. Tables and 
rules at best find their largest use as references. In each case we have been careful to refer specifically 
to the rule employed in a way we trust to bring the reader into pleasant acquaintance therewith. 
KEY TO THE PLANS AND REFERENCES. 
Double or parallel lines indicate Flow Pipes. 
Single heavy lines indicate Return Pipes. 
Broken lines indicate Air Pipes from radiators, coils, and flow pipes. 
RAD.—“ Radiator.” 
RAD. 44 —“Radiator with 44 square feet of surface.” 
RAD. 7 44D'—“ Radiator No. 7 with 44 square feet of surface.” 
RAD. 16 32D'—“ Radiator No. 16 with 32 square feet of surface.” 
(Nos. 7 and 16 in such instances refer to the numbers of the rooms in the tables.) 
REG.—“ Register.” 
W. REG. or W. R.—“ Warm Air Register.” 
W. REG. XI 8 x 10.—“ Warm Air Register 8x10 inches in room No. 11.” 
W. D. or AY. A. D.—“ Warm Air Duct.” 
D. W.—“Duct for Warm Air.” 
W. D. 5 x 21.—“ Warm Air Duct 5 x 21 inches.” 
C. D. or C. A. D.—“ Cold Air Duct.” 
CIR. REG.—“ Circulating Air Register.” 
22 ABRAM CON STOVE COMPANY. 
23 
E. REG. or E. R.—“Exhaust or Exit Register.” (Exhaust Register” refers to the register connected 
to the ventilating flue and near the floor. “ Exit Register” refers to the register connected to 
ventilating flue and near the ceiling.) 
E. I). or E. A. D.—“Exhaust or Exit Air Duct.” 
V.—“ Ventilating Shaft.” 
F. —“Flow Pipe.” 
F. M.—“ Main Flow Pipe.” 
R.—“ Return Pipe.” 
R. M.—“ Main Return Pipe.” 
V£—“ f-inch Valve on Radiator.” 
G. V.—“ Gate Valve.” 
G. V. F.—“ Gate Valve on Flow Pipe.” 
A. A".—“Angle A7alve.” 
A. V. R.—“ Angle Valve on Return Pipe.” 
S. P.—“ Smoke Pipe.” 
T. —“ Thermometer.” 
EX. TAXK.—“ Expansion Tank.” 
EXP. PIPE.—“ Expansion Pipe.” Heating and Ventilating Cottage Residence 
with the Novelty Circulator, No. 8. 
Fig. 24.—Perspective View (Reproduced from Carpentry and Building by Permission). 
TN Fig. 24 is given the perspective of a typical cottage residence. Fig. 25 is a sectional longitudinal 
elevation in which the location of the radiators is shown, and in which the relative positions of the 
warm-air and exhaust or exit registers are indicated. The inclination of the main flow and 
return pipes in cellar, and the vertical lines of pipes connecting radiators on second floor to main 
pipes in cellar, are also shown. The height of the expansion-tank above the circulator is indicated, as 
well as the location of the emptying or blow-off cock. Fig. 26 is a plan of cellar. The double lines 
24 ABRAM COX STOVE COMPANY. 
25 
denote the flow pipes, and single heavy lines the return pipes. The latter lines are only seen in a few 
places in this plan, as the return pipes, where not indicated, are the same as the flow pipes and pass 
under them. ABDD give the location of the air pipes from the indirect radiators. The position 
of the main cold-air duct is also shown. 
Fig. 27 is a plan of the first floor, and Fig. 28 a plan of the second floor. The location of radiators 
and registers on each floor is shown. The dotted lines indicate the floor-beams and the proper 
Fig. 25.—Sectional Longitudinal Elevation of Cottage Residence Showing Location of Circulator, Position of Radiators, etc. Scale % inch to the foot. 
location for trimmer-beams so as to provide space for the passage of heating pipes and ducts to 
radiators and registers respectively. Fig. 29 is a sectional elevation giving an enlarged view of air 
ducts and air pipes from indirect radiators at A, B, and I), details in hath room, and location and 
connections of expansion-tank. Fig. 30 shows emptying-valve and discharge to sewer. 26 
THE NOVELTY CIRCULATOR. 
Fig. 26.—Plan of Cellar of Cottage Residence. Scale % inch to the foot. 
Fig. 27.—Plan of First Floor. Scale % inch to the foot. ABRAM COX STOVE COMPANY. 
27 
Table I shows the contents, surfaces, and proportions of the apparatus, while Table II gives 
the surfaces in radiators proportioned. 
In proportioning the quantity of surfaces required in radiators by the rule used in Table XIV, 
the temperature of the water in radiators may be taken at from 160° to 180°. Sufficient surface will 
be obtained by so doing. The surfaces in the indirect radiators and direct radiators on first floor, 
except those in pantry and kitchen, are proportioned with the temperature of water at 160°. The 
radiators in pantry and kitchen, and all on the second floor, are proportioned upon the basis of the 
water being at a temperature of 180°. The rooms with the latter temperature of water require less 
heat relatively than the other apartments, and by this change in the calculation less surface in the 
radiators is given. The surface in the bath room is proportioned with the temperature of the water 
Fig. 28.—Plan of Second Floor of Cottage Residence. Scale % inch to the foot. 
iii radiator at 160°, and in order to provide for an increase of temperature, which is sometimes 
desirable in hath rooms, a special multiplier is given in the foot-note. 
The location of radiators and registers is governed by several considerations. Provision for 
their location in planning the house should be made so that their presence will, as far as possible, 
remain unobserved. Such locations for them should be obtained in a way to avoid excessive lengths 
of pipes or ducts, and the introduction of numerous bends or turns. Where direct radiators are 
used they should be placed so that the most exposed wall will receive as directly as possible the heat 
given off by radiation. Warm-air registers should be located so as to produce warm-air currents 
near the exposed walls, and they should he at a higher level than the exhaust registers. Exhaust 
registers should be placed so as to cause the currents of air to tend toward the exposed walls, and 28 
T1IE NOVELTY CIRCULATOR. 
they should be as near the level of the floor as possible. Exit registers should be as near the ceiling 
as possible, and arranged to cause the currents of heated air to flow toward the exposed walls. 
These registers are only opened when it is desired to allow the heated air to escape. The location 
of radiators and registers just suggested cannot always be secured in practice, as is illustrated in the 
cottage residence. 
In the parlor, warm register II is located on the inside wall. As there is no cellar of any 
depth beneath this room, it is more convenient to locate the indirect radiator in the manner shown. 
The registers in the dining room and bed room A are also on inside walls on account of convenience 
of location. The exhaust and exit 
registers in the parlor and bed room 
A are near exposed walls, while the 
register in the dining room is in an 
inside wall. 
The direct radiators are as far 
as possible located near exposed 
walls, except the radiator in the 
back hall, which is placed near the 
inside walls on account of want of 
space. The pantry, Xo. VI, and 
toilet on first floor are heated by the 
flow and return pipe connection to 
the radiators in rooms above on 
second floor. The area of the warm- 
air flue is dependent on the velocity 
of the air, which velocity is due to 
the difference in temperature of the 
air in the room, and at the indirect 
radiator and the relative height of the 
flue. Under the usual conditions the 
natural velocity to the first floor is 
about 1J to 2 feet per second, and 
as the height is greater to the second 
and other floors the velocity in- 
creases to 2§, to 3J, and even to 5 
feet per second. 
The cubic contents of the parlor are 1930 feet, and, as seen in Table 11, the air in this room is 
changed twice each hour, therefore 1930 x.053 (see Table XXVIII) = 102.29 square inches, the area 
of the warm-air duct. The warm-air duct, 21 x 5 inches, is equal to 105 square inches, which multi- 
plied by 1.33 is 139.0 square inches, the area of the opening for warm-air register; that is, a 10 x 14 
Fig. 29.—Sectional Elevation Showing Air Ducts and Air Pipes, also Details in Bath Room, 
with Expansion Tank, etc. ABB AM COX STOVE COMPANY. 
29 
inch register. The exhaust and exit registers are found to he 9x14 inches by multiplying the 
area of warm-air due by 1.2, which is equal to 126 square inches. The warm-air due to bed room A 
on second door is ascertained by multiplying cubic contents in feet, 1800 x.032 (see Table XXVIII) 
= 57.6 square inches. The warm-air due therefore is made 4x15 inches = 60 square inches. The 
register openings are found as already explained. 
The area of the fresh or cold-air duct is obtained by multiplying the area of the warm-air 
duct by .8. For the parlor the cold-air duet is equal to 105 x .8 = 84 square inches. Since 
inches diameter equals 86.6 square inches, it is therefore used. (See cellar plan, Fig. 26.) The main 
cold-air duct is equal to the area of all the cold-air ducts. 
As shown in Fig. 25, sectional elevation, cottage residence, the main dow and return pipes are 
inclined from the circulator to the radiator and vertical rising lines. This necessitates air-emission 
cocks or valves on each direct radiator and air pipes ABDD on indirect radiators, Figs. 25 and 29. 
The air cocks on direct radiators are opened when dlling the system, and the advantage of the air 
pipes on the indirect radiators is the prevention of all air accumulations without necessity of 
operating air cocks. These air pipes are con- 
nected to vertical rising dow pipe to radiators 
Xos. X and XIII, second door (see Fig. 28), 
which pipe is continued to the top of the ex- 
pansion tank, Figs. 25 and 29. To the return 
pipe from radiator Xo. XIII is connected the ex- 
pansion pipe shown in Figs. 25 and 29. The 
overdow pipe from the expansion tank may dis- 
charge into a funnel attached to pipe connected 
to overdow from the bath tub, or this pipe may 
be continued to the cellar and discharge into 
some convenient sink. By the arrangement de- 
scribed separate pipes from the expansion tank 
to the cellar are avoided, and the system is at all 
times freely open to the atmosphere so as to 
prevent air accumulations. 
The area or size of dow and return mains is ascertained by multiplying the total surface in 
radiators in square feet, 516 x .015 (see “Sizes of Flow and lieturn Pipes ”) = 7.74, which is 
approximate area. Since 3J-inch pipe has an area of 9.88 square inches, and is the nearest to the 
approximate area, we use it for both dow and return mains. The size of the expansion tank is 
ascertained in the manner explained under “ Expansion Tanks.” Square feet of surface in system 
516 x .03 = 15.48 gallons capacity of expansion tank, or 516 x 7 = 3612 cubic inches capacity 
of tank. The entire system, as shown, contains approximately 220 gallons, which at 212° 
will approximately expand °f its volume, or about 9J gallons or 2194 cubic inches. 
Therefore the space above the water-line in tank when the apparatus is cold and below the 
Fig. 30.—Emptying-Valve and Discharge into Sewer. 30 
THE NOVELTY CIRCULATOR. 
overflow opening should not be less than 2194 cubic inches. The rest of the space obtained by 
using the multipliers as above is necessary, especially when a ball-cock is attached to the water-supply 
pipe. By the arrangement of pipes shown, the water, on entering the system through the valve 
on water-supply connection to the expansion tank, passes down the expansion pipe into the vertical 
TABLE I —COTTAGE RESIDENCE. CONTENTS, SURFACES, PROPORTIONS, ETC., OF 
HOT-WATER APPARATUS. 
0 
in 
© 
SECOND 
FLOOR. 
FIRST 
FLOOR. 
—f 
* 
3 
(_U 
t—* 
t__* 
J—4 
<Tt- 
—I 
O O* 
4- 
_ 
0* o 
p- 
Oi 
h- 
oc 
*—* 
Pa 
< 
© 
P 
a; 
P 
s* 
© 
1 
3 
D 
/T 
SP 
o 
o 
h 
w 
p 
© 
pr 
W 
p 
S* 
„ 
W 
© 
p- 
H 
b 1? 
<f o 
< 3- 
© 
o 
c 
w 
p 
O 
w 
p- 
W 
© 
p- 
P 
P 
5T 
3# 
r 
u 
s* 
Parlor 
Sitting 
© 
p 
7J 
O 
O 
i 
c*- 
cr 
P 
o 
s 
p- 
p. 
o 
o 
? 
p 
o 
ro 
o 
B 
> 
j E- 
p 
0 
c 
p 
d : 
© : 
EL 
U) 
s 
—L 
1 
«>3 
C 
—I 
i—i 
»—i 
i—i 
I oc 
4-1 
4-1 
44 44 
44 
Contents in cubic feet. 
© O- 4^- 
o 
to 
CO 
o 
co 
05 
oo 
4- 
4- 
44 
co 
co 
A 
05 
4- CO 
0 
rg- 
-I 
01 
CO 
oo 
o 
O' 
4- 
o 
oo oo 
I to 
CO 
co 
Cl 
0 
OO 
44 co 
—1 
o 
o 
—i 
4- 
O' 
44 
4- 
o 
O '05 
1 Cn 
oo 
4-i 
O O' 
44 
CO 0 
h-i 
o 
® p 
2. p 
t—i 
00 
o 
oo 
oo 
oo 
44 
h-i 
CO 
05 
p-i 
05 
h-l 
GO 
t-a 
H-1 CO 
co 
i—i 
4-1 
00 
44 to 
h-l 
f—1 
44 l—l 
4- CO 
Exposed wall exclu- 
sive of glass surface, 
square feet. 
H 
© 
co 
—t 
44 
44 
05 
—J 
Oi 
4- 
—i 05 
05 
to 
4-1 
05 05 
co 
CO 05 
CC 
O 
© J2 
to 
oo 
! 1-1 
[ to 
44 
1—1 
CO 
to 
to 
! 05 
O' 
to 
to to 
IO 
Glass surface, square 
feet. 
r*“ 
oo 
to 
05 
O' 
O' 
O' 
4— 
co 
4- 
i 05 
O' 
o 
05 
44 
05 
05 05 
CC 
3 
P, 
*-♦5 
©CO 
© 42 
44 
05 
to 
M 
l—i 
co 
to 
O' 
4- 
co 
to 
O' 
I—i 
05 
44 
co 
4- 4- 
CO 
1 Equivalent to glass in 
square feet.* 
CO 
M 
44 
CO 
O' 
to 
l—i 
O' 4— ! 
oo 
to 
oo 
44 —J 
00 
O' Cj 
0* 
►© 
P 
to 
to 
M 
M 
44 
to 
to 
to 
i—i 
1—1 
h-l 
to 
1-4 
44 to 
h-l 
Lineal feet of exposed 
wall. 
r 
Cn 
to 
o 
O' 
44 
co 
to 
co 
O' 4- 
co 
OO 
44 
O' O' 
0-' 
—r co 
Cl 
e _ — 
•C 
to 
44 
1—1 
co 
to 
t—‘ 
to 
to 
4- 
to 
-i 
to 
4- 
4- 
4- 
:atii 
fac 
dial 
coil 
uar 
e< t. 
>1 
© 
05 
Cn 
CO 
oo 
o 
o 
4- 
h-l 
4- 
44 
00 
<T 
4- 
S’ 
© 
to 
i-i 
*“5 H—1 h-.®3 
© a a -»Sa 
© 
ro 
-T 
O' 
—r 
OC 
© Pj © q p 
o 
o 
O 
o 
O 
O 
' 1 
5- 
p4 
lp|C0 4|CO tp|C0 |P|C0 
h-* ►Pico 
>P|w 
44 
44 
Hh hh. 
-4 
Diam. flow and return 
pipes to radiators. 
co 
o 
CO 
05 
to 
co 
4- 
4- 
to 
to 
to 
I 05 
CO 
CO 
4- 
—Jl 
to 
co to 
IO 
Proportion of contents 
to surface in radiators 
—+■ 
-b 
CO 
O' 
-J 
O 
C71 
—b 
o 
4-1 
c O' 
44 
IO 4- 
4-. P no fc( 
4- 
O' 
O' 
S q-g o‘S 
X 
X 
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to 
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05 
05 
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Area of warm-air pipe 
Cn 
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O 
O' 
in square inches. 
to 
h-l 
44 
Velocity of air per sec- 
O' 
in 
O' 
ond in feet. 
1 
to 
1 
to 
to 
Changes of air per hour 
p 5\q 
to 
00 
h-l 
0 
0 
K-E'g.3 S.O 
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X 
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to 
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1 *—1 
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h-i 
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to 
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1 Area of exhaust or exit 
to 
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4- 
4- 
1 flue in square inches. 
M.OQ 
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to 
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1-4 
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[ Cold-air duct or fresh- 
ti? 
j air inlet in inches diam 
gjfi 
1 O' 
O' 
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00 
Area of cold-air duet 
a ®.S 
?gr«? 
a © 
h-l 
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p 
O' 
i 
or fresh-air inlet in 
inches. 
return, and thence to return main R M and through pipe N to bottom of circulator, and as the 
water fills the system the air passes up the vertical flow pipe to the air pipe into the expansion tank, 
which is open to the atmosphere through the overflow pipe, thus freeing the system of air. An 
extra pipe from the top of the expansion tank is sometimes carried outside the roof to allow the ABRAM COX STOVE COMPANY. 
31 
vapor to escape. Such a pipe is not necessary in a well-arranged system, as the water in the expan- 
sion tank should not be heated to the extent of giving off vapor or steam. 
The emptying-valve and discharge shown in Fig. 30 should be placed on the lowest pipe hT, 
Fig. 25, in the system. The pipe from this valve should be open and discharge in sight, and it 
should not be connected directly to any waste or sewer pipe, so that any leakage through it may 
be easily observed. This valve need not be large. In ordinary residences f-inch to 1 inch in 
diameter is ample, while inches to inches in diameter is necessary only on large systems. 
TABLE II—COTTAGE RESIDENCE. SURFACES IN RADIATORS PROPORTIONED. 
ROOMS. 
Sq. ft. 
of glass 
and its 
equiva- 
lent in 
exposed 
wall. 
Multi- 
pliers. 
Cubic feet 
of 
air cooled 
per hour 
by glass. 
Contents 
of rooms 
in 
cubic feet. 
Changes 
of air in 
rooms 
per hour 
Total number 
of cubic feet 
of air to be 
warmed. 
Multipliers. 
Sq. ft. 
of surface 
required 
in rooms 
to warm 
air from 
0 to 70°. 
! Remarks. 
1 
i 
i 
f 1. Front hall 
40 
X 75 
= 3000 
-f- (155/ 
x 1) 
= 4557 
X .0092' 
; 42 
i 
2. Parlor 
46 
X 75 
= 3450 
+ (1930 
X 2) 
= 7310 
X .0114,? 
83 
Indirect. 
DC 
0 
3. Sitting room 
40 
X 75 
- 3000 
+ (1449 
X 1) 
= 4449 
X .0092' 
= 41 
o 
-1 
L. 
4. Dining room 
38 
X 75 
= 2850 
+ (1681 
X 2) 
= 6212 
X .0114 
= 70 
Indirect. 
i- 
</> 
5. Toilet 
7 
X 75 
= 525 
+ ( 105 
X 1) 
= 630 
X .0092 
= 6 
DC 
u. 
6. Pantry 
11 
X 75 
= 825 
+ ( 360 
X 1) 
= 1185 
X .0072 
= 8 
7. Kitchen 
68 
X 75 
= 5100 
+ (1391 
X 1) 
= 6491 
X .0072 
= 47 
- 8. Back hall 
26 
X 75 
= 1950 
-f ( 735 
X 1) 
= 2685 
X .0092 
= 25 
10. Alcove 
35 
X 75 
= 2625 
+ ( 480 
X 1) 
= 3105 
X .0072 
= 22 . 
o 
0 
11. Bedroom A 
41 
X 75 
= 3075 
+ (1800 
X 2) 
= 6675 
X .0114 
= 76 
Indirect. 
_J 
Li. 
12. “ B 
51 
X 75 
= 3825 
+ (1644 
X 1) 
= 5469 
X .0072 
= 40 
Q 
Z 
13. “ C 
22 
X 75 
= 1650 
+ ( 954 
X 1) 
= 2604 
X .0072 
= 19 
o 
o 
14. “ D 
35 
X 75 
= 2625 
4- (1005 
X 1) 
= 3630 
X .0072 
= 26 
U) 
15. Bath room 
9 
X 75 
= 665 
+ ( 384 
X 1) 
= 1049 
X .0092* 
= 12 
Use 1.25 for multiplier to raise to 80°. Heating and Ventilating a Suburban Mansion 
with two Novelty Circulators, No. 12. 
RIG. 31 is the front elevation, while Fig. 32 is a sectional elevation in which the course of the ven- 
tilating tines is indicated by dotted lines. Rectangular figures, near each of which is the letter 
R, denote the positions of the exhaust and exit registers. The position of the expansion tank 
is shown with its connections to and from flow, return and air pipes in bath room on second floor. 
The vertical return pipes at hack 
of circulator are shown away from 
center in order to make clear the 
flow-pipe connections. The chan- 
nel for return pipes from radiators 
on basement floor is denoted by 
dotted lines below the level of 
floor. 
Fig. 33 is the basement 
plan. Double lines in it indicate 
the flow pipes, single heavy lines 
the return pipes, dotted lines the 
air pipes, while double dotted 
Fig- 3'-—Front Elevation of Suburban Mansion, 
lines denote the location of chan- 
nel under floor of basement for 
return pipes from radiators on 
basement floor. The positions of 
the direct radiators in the servants’ 
lavatory and dry room are also 
shown. 
Fig. 34 is the ground or 
first-floor plan. The direct radia- 
tor in bath room and coil in lava- 
tory, with the surface in each in 
square feet, are shown. The posi- 
tions of the four vertical lines of 
flow and return pipes to radiators 
Fig. 32.—Sectional Longitudinal Elevation. Scale -jL inch to the foot. ABEAM COM STOVE COMPANY,. 
33 
on chamber floor are indicated by circular points: in corner of landing in entrance ball leading 
to den; in closet oft' maid’s 
room, leading to chamber V; 
in library near door to dining 
room, leading to nursery; and 
in butler’s pantry, leading to 
bath room and chamber IV; 
and also to air and expansion 
pipe connections to expansion 
tank. It will be observed that 
the warm-air registers in the 
library and morning room are 
on the floor. This position 
is made necessary because 
there is no provision for ver- 
tical ducts in the walls. The 
warm-air registers being at as 
great a distance as possible 
from the exhaust register, the 
Fig. 33 — Plan of Basement. Scale -fg inch to the foot. 
arrangement will give satisfac- 
tory heating results. If the 
warm-air register on the floor 
were put near the exhaust 
register in the wall and above 
it, the heated air would pass 
directly out through the ex- 
haust register. In the en- 
trance hall two air-circulating 
registers are placed in the 
floor, through which the air 
within the house may be cir- 
culated when the damper in 
the main cold-air duct is closed. 
Fig. 35 is the chamber 
floor plan. All the apart- 
ments are heated by direct 
radiation except chambers I, 
Fig- 34- —Plan of First Floor. Scale jg inch to the foot. 34 
r HE N 0 V EL T Y Cl R CUE A TO R. 
II, and in. The halls are heated from registers on floor beneath. In the design of this house no 
provision was made for the ventilation of the nursery or bath room. In the bath room the expansion 
tank is placed convenient 
to the vertical rising lines 
to which it is connected. 
Fig. 36 gives details of 
radiator connections in 
basement at K in bath 
room. Fig. 37 shows ele- 
vation of connection in 
basement at M to radia- 
tor in servants’ lavatory. 
Figs. 38 and 39 give de- 
tails of air ducts at E F 
and D E, as well as con- 
nections to radiator in dry 
room. 
Fig. 40 is an ele- 
vation in basement in 
laundry looking toward 
heater room. The circu- 
lator, main flow and return 
pipes are shown, as well as the air-pipe connections and radiator at K in bath room, and Fig. 41 shows 
the double connection of an air pipe at P. 
Table Ho. Ill gives the contents, surfaces, and propor- 
tions, while Table Ho. IV shows the radiators proportioned. 
In proportioning the surfaces in radiators for heating the 
two apartments in basement and all the apartments on ground or 
first floor, the temperature of the water is taken at 160°, and 
the same temperature is used in estimating for the bath room on 
chamber floor. The temperature used in calculating the rest of 
the surface, both direct and indirect, is 180°. 
The location of the registers has already been referred to, 
and an examination of the places will indicate that there is little 
room for selection. The direct radiators on the chamber and 
ground floors have been arranged as far as practicable near 
the exposed walls. The radiator in the nursery is placed so 
as to simplify the piping. This room, it will be observed, projects 
out over the library bay window. The vertical lines to this 
Fig* 35-—Plan of Chamber Floor. Seale fig- inch to the foot. 
Fig* 3<S-—Radia- 
tor Connections at 
K in Basement. 
Fig- 37- — Radiator 
Connections at M in 
Basement. A BRA 31 rOX STOVE COMPANY. 
radiator and the coil in the den are encased between the floor and ceiling in library and on 
landing. 
The position of the radiators in the basement requires some remarks. By referring to Bigs. 
36 to 40 it will be observed that these 
radiators are below the level of the tire 
in circulator, and the return pipes from 
them are under the level of the floor 
of the basement, The flow pipes to 
these radiators are large and are placed 
on the more favorable points of the 
main flow from which the circulation 
to them is taken. The flow pipes 
are connected to the top of one end 
of the radiator, the air pipe being 
connected to the top of the other end. 
The return connection is to the lower 
part of the radiator at the air-pipe 
end. The water in these radiators 
circulates by gravity because there is 
no repulsive motion produced in the 
circulator when the water is taking up the heat, which if present would stop the motion toward 
displacement and hinder circulation. 
The warm-air flues and reg- 
isters and cold-air ducts, as well 
as exhaust and exit registers, have 
been proportioned according to rules 
and tables given under “ Supply 
and Emission of Heat.” Each in- 
direct radiator in addition to dam- 
per in cold-air duct is fitted with 
an air-mixing damper by which the 
air is permitted to pass in above 
the heating surface. This arrange- 
ment for admitting cold fresh air 
is very desirable, as the tempera- 
ture of the air entering the room 
can be readily adjusted. 
The main flow and return pipes have been calculated according to rules given under “ Sizes 
of Main Flow and Return Pipes.” 1655 square feet x.015 = 24.8 approximate area in square inches. 
FigTIJr—Details' of Air Ducts at E F. 
39.—Details of Air Ducts at D E. T1TE NOVELTY CIRC U LA TOR. 
Five-inch pipe area = 19.99 square inches, which therefore is the size selected for the main flow 
and return. This size 
pipe is used from 
each circulator with 
a gate-valve in each 
flow, so that one 
heater may be used 
without the other. 
The valves are not ac- 
tually necessary, and 
may be omitted be- 
cause the circulator 
which is not in use 
will only become 
warm without af- 
fecting the circula- 
tion throughout the 
system to any great 
extent, especially if 
valves are placed on 
Fig. 40.—Elevation in Laundry Looking Toward Heater Room. 
the 2-inch return pipe between the 
two heaters and to which are con- 
nected the radiators on the base- 
ment floor. When either of these 
2-inch valves is closed, the cir- 
culation through the heater not 
in use will have to pass up the 
vertical main return, thus produc- 
ing a slow action. 
The air pipes are connected 
to all the indirect and direct radia- 
tors in basement, and to the verti- 
cal flow and return pipes, Fig. 41. 
The radiators and coils on the 
ground and chamber floors will 
require air cocks. The inclination 
of the main pipes and branches is 
upward from the heater to the 
radiators and vertical lines. 
SCALE IN. = 1 TOOT 
Fig. 41.—Flow and Return Pipes. Connection to Air Pipe at P. ABRAM COX STOVE COMPANY. 
37 
TABLE III—SUBURBAN MANSION. CONTENTS, SURFACES, PROPORTIONS, ETC., OF 
HOT-WATER HEATING APPARATUS. 
1 
SECOND FLOOR. 
FIRST 
FLOOR. 
BASEMENT. 
1 
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square inches. 38 
THE NOVELTY CIRCULATOR. 
TABLE IV.—SUBURBAN MANSION. SURFACES IN RADIATORS PROPORTIONED. 
ROOMS. 
Sq. ft. 
of glass 
and its 
equiva- 
lent in 
exposed 
wall. 
Multi- 
pliers. 
Cubic feet 
of 
air cooled 
per hour 
by glass. 
Contents 
of rooms 
in 
cubic feet. 
Changes 
of air in 
rooms 
per hour. 
Total number 
of cubic feet 
of air to be 
warmed. 
Multipliers. 
Sq. ft. 
of surface 
required 
in rooms 
to warm 
air from 
0 to 70°. 
Remirks. 
g 
6 - 
Dry room 
42 
X 
75 
= 
3150 
+ (5460 
X 
1) 
= 
8610 
X 
.0092 
= 80 
Direct. 
Lavatory 
33 
X 
75 
= 
2475 
+ 
(1280 
X 
1) 
= 
3755 
X 
.0092* 
= 44 
Direct. 
The halls 
251 
X 
75 
= 
18825 
+(12830 
X 
1) 
= 
31655 
X 
.0114 
= 360 
Indirect. 
Lavatory 
11 
X 
75 
= 
825 
+ 
( 336 
X 
1) 
1161 
X 
.0092 
= 11 
Direct. 
. 
Parlors 
108 
X 
75 
= 
8100 
+ 
(3920 
X 
2) 
= 
15940 
X 
.0114 
= 171 
Indirect. 
DC 
O 
Dining room 
84 
X 
75 
= 
6300 
+ 
(3500 
X 
2) 
= 
13300 
X 
.0114 
= 151 
Indirect. 
-1 
Li. 
Library 
108 
X 
75 
= 
8100 
+ 
(2560 
X 
2) 
= 
13100 
X 
.0114 
= 149 
Indirect. 
i- i 
(O 
Butler’s pantry 
22 
X 
75 
- - 
1650 
+ 
( 750 
X 
2) 
= 
3350 
X 
.0114 
= 37 
Indirect. 
iZ 
Maid’s room 
40 
X 
75 
= 
3000 
+ 
(1610 
X 
2) 
== 
6220 
X 
.0114 
= 70 
Indirect. 
Bath room 
26 
X 
75 
= 
1950 
+ 
( 500 
X 
1) 
= 
2450 
X 
.0092 
= 22 
Direct. 
Morning room 
70 
X 
75 
= 
5250 
(1400 
X 
2) 
= 
8050 
X 
.0114 
= 90 
Indirect. 
Sitting room 
46 
X 
75 
= 
3450 
1 
(2070 
X 
2) 
= 
7590 
X 
.0114 
= 90 
Indirect. 
f The Den 
43 
X 
75 
= 
3225 
( 640 
X 
1) 
= 
3865 
X 
.0072 
= 28 
Direct. 
Chamber No. 1 
41 
X 
75 
' = 
3075 
+ 
(1986 
X 
2) 
= 
7047 
X 
.009 
= 63 
Indirect. 
O 
“ No. 2 
51 
X 
75 
= 
3825 
1 
(1568 
X 
2) 
= 
6961 
X 
.009 
■= 63 
Indirect. 
-i 
L. 
“ Xo. 3 ... 
43 
X 
75 
= 
3225 
+ 
(3087 
X 
2) 
= 
9399 
X 
.009 
=-= 84 
Indirect. 
Q 
Z 
Nursery 
63 
X 
75 
== 
4725 
(1975 
X 
1) 
= 
6700 
X 
.0072 
= 48 
Direct. 
o 
o 
Bath room 
29 
X 
75 
= 
2175 
+ 
( 677 
X 
1) 
= 
2852 
X 
.0092 
= 26 
Direct. 
<n 
Chamber No. 4 
28 
X 
75 
= 
2100 
(1396 
X 
1) 
= 
3496 
X 
.0072 
= 25 
Direct. 
“ No. 5 
66 
X 
75 
= 
4950 
+ 
(2261 
X 
1) 
= 
7211 
X 
.0072 
= 52 
Direct. 
* 
Use 1.25 for multiplier to raise to 80°. Heating and Ventilating a City Residence 
with the Novelty Circulator, No. 15. 
BIG. 42 is sectional longitudinal elevation of a city residence. There are shown by dotted lines* 
the smoke flue and ventilating flues for the front end of residence, for the wall in which they 
occur is supposed to be removed. The lines, however, indicate the position and extent of the 
flues, as well also as of the vertical warm-air ducts. Fig. 43 is a transverse sectional elevation in which 
the front wall of building is supposed to be removed. Dotted lines here also denote the vertical warm-air 
ducts, exhaust and ventilating flues. In these views the location of the circulator in basement, the position 
Fig; 42.—Sectional Longitudinal Elevation of City Residence. Scale fy inch to the foot. 40 
THE NO VEL T Y Cl R CUE A TOR. 
of the indirect radiators, the cold-air ducts near basement ceiling, the flow and return mains to vertical 
lines of pipe, to radiators and coils on upper floors, etc., can be readily traced. The position of expansion 
tank on fourth floor is also shown. The exhaust and exit registers to ventilating flues are indicated 
and their sizes are given. 
Fig. 44 is a plan of basement. The circulator, it will be seen, is located in the front room, in 
which are also placed eight stacks of indirect radiators and main cold-air ducts. Two other indirect 
radiators are placed in the central hall of basement to heat dining 
room. The main flow and return pipes, shown in this figure, are 
placed a sufficient distance below the basement ceiling in front room 
to give an ascent to the flow and return connections to indirect radi- 
ators. Before passing into central hall and kitchen these pipes rise 
at L close to ceiling, and the connections to indirect radiators in 
central hall descend. The main flow and return pipes continue to 
ascend from the central hall to connections to coil in conservatory. 
In the plan only a portion of the main return is seen as it is located 
nearly under the main flow pipe. The part that is shown is indi- 
cated by a single heavy line, while the air pipes from the indirect 
radiators are shown by dotted lines. In the main cold-air duct near 
indirect radiator 3 is a damper. This damper is closed when air 
is taken from the hall through the air-circulating duct. By this 
arrangement the air in the hall and other parts of the house is cir- 
culated continuously until warm, through the indirect radiators (3) 
to the hall and (4) to the dining room. In cold weather and during 
the night it is economical to use this method of air circulation. 
Fig. 45 is plan of first floor. In this the location of the warm 
air, exhaust air, and circulating register are shown. The vertical 
lines of pipes to radiator in hall room (16) pass up in partition be- 
tween the parlor (6) and vestibule. Similar lines to radiators in 
bath rooms and rooms at back of residence pass up along dining 
room (4) Avail,but they are encased in a column against Avail, as 
shown. 
Fig. 46 is a plan of second floor. The position of registers 
and radiators is indicated. The vertical line of pipes to hall room (16) on third floor passes up in the 
partition between the library (10) and book room (11). One of the warm-air ducts heating library 
also heats the book room. The area of the top of the duct is divided before the register openings 
are reached. As the two openings are on the same level, the supply of warm air will be in proportion 
to the area of the registers. It is not good practice to supply two registers from the one Avarm-air 
duct, Avlien one register is one floor above the other. The dotted lines on floor of book room and 
library indicate the position of trimmer beams to provide space from the Avarm-air duct to pass up in 
Fig. 43.—Sectional Transverse Elevation of 
City Residence. Scale inch to the foot. ABRAM COX STOVB COMPANY. 
41 
partition. The vertical line of pipes connecting to radiators and coils at back of house on third and 
fourth floors pass up through bath room. By these arrangements no pipes are exposed on first or 
second floor except in the bath room on the latter floor. 
Fig. 47 is plan of third floor. One of the exit registers in ventilating flue of hall (3) is on this 
floor, another being on the fourth floor, each near the ceiling. On plan of fourth floor, Fig. 48, the 
position of expansion tank is shown with the expansion pipe connected from top of vertical return line 
to bottom of expansion tank, with an air pipe at top of tank and connected to top of vertical flow line 
and the overflow and water-supply pipes connected to tank as already described. 
Fig. 49 shows details in basement, being an end view at H. The outline of the cold-air duct 
Fig. 44.—Plan of Basement. 
F'g- 45*—Plan of First Floor. Scale xV inch to the foot. 
chamber is shown with the main branch 40 inches by 10 inches near ceiling, its 12| by 12-inch branch 
to the left, and its 18J by 12-inch branch to the right, with baffle plate B B opposite principal opening 
or inlet, which is 36 inches by 21 inches. The relative positions of the main flow and return pipes 
are indicated and the air pipe from radiator is also shown connected to main air pipe near ceiling. 
Fig. 50 shows details in basement, being a section at H to GL The sectional view of the cold-air 
chamber shows baffle plate B B opposite branch duct 18J by 12 inches, so that the effect of the wind 
will be reduced in this branch duct. The air pipes may be connected to the top of the section of 
radiator farthest from the entrance of the flow as shown in this illustration, or a large nipple may 42 
THE NOVELTY CIRCULATOR. 
he extended through the casing and have a reducing elbow on the end as shown in Fig. 29, cottage 
residence. Fig. 51, of details in basement at L, shows the main flow and return pipes and main air 
pipe as they rise and pass through the wall into central hall. Fig. 52 gives the elevation at M in 
central hall of basement, showing the connections of main flow and return pipes to indirect radiators 
Fig. 48.—Plan of Fourth Floor. Scale N inch to the foot. 
(4) to dining room. These radiators are not connected to the main air pipe because the air in them 
can pass out through main flow pipe to vertical air pipe. In this view doors are shown in the air- 
circulating duct from central hall to cold-air duct. These doors are air-tight and kept closed when 
fresh air only is desired in dining room. Fig. 53 illustrates the main air-pipe connection to the ABRAM COX STOVE COMPANY. 
43 
vertical flow and return pipes the tops of which are directly connected with the expansion tank at 
top and bottom, respectively. By this double connection of the main air pipe circulation is produced 
at all times through the pipe, and circulation is assisted through the indirect radiators. At the same 
time no air can accumulate to impede circulation. 
In Table Xo. V are given the contents, surfaces, proportions, etc., while Table ISTo. VI gives the 
surfaces in radiators as proportioned. 
The surfaces in the indirect radiators in this job are proportioned with the temperature of the 
water at 160°, as shown in Table VI and by the rales given under “ Supply and Emission of 
Ileat.” The surface in pipe coil in conservatory is proportioned per square foot of glass, Table XX. 
The direct radiators are propor- 
tioned with the temperature of the 
water at 180°. In proportioning 
surfaces in similar buildings this 
latter temperature may be usually 
adopted in direct radiators through- 
out the whole house. 
In locating radiators and reg- 
isters in city residences there is not 
much opportunity to exercise judg- 
ment in the selection of positions, 
though it is desirable to keep the 
radiators near exposed walls and 
windows. When deciding the posi- 
tion of the vertical warm-air flues 
or ducts, their openings in the 
basement or cellar should be con- 
veniently arranged so that the in- 
direct radiator will not occupy use- 
ful head room or obstruct the light in the cellar. At the time provision is made for the openings of 
the warm-air flues in the cellar the location of the fresh or cold-air inlet should be decided. It is 
more desirable to make a special opening for the cold-air inlet than to use one of the window open- 
ings. The position of the cold-air inlet should be such as to give ample space about it so that an air- 
receiving chamber may be constructed in order to prevent the blowing of the wind being felt at the 
registers. The register openings in the warm-air flues should be above the base-board. 
The location of direct radiators should be such as to occupy the least useful space in each 
room, at the same time causing the connecting pipes and vertical lines to be exposed to view as little 
as possible. In small rooms, such as bath rooms, return bend wall coils will occupy less space than 
direct radiators. In the residence here illustrated it will be observed that the vertical lines of pipes 
are not exposed, except in the bath rooms, where their surfaces are useful for heating purposes in place 
Fig. 49.—End View at H. Wall Kemoved. 44 
THE N O V EL T Y CIR CUE ATOM. 
TABLE V—CITY RESIDENCE. CONTENTS, SURFACES, PROPORTIONS, ETC, OF 
HOT-WATER HEATING APPARATUS. 
■ 
FOURTH FLOOR. 
THIRD FLOOR. 
SECOND FLOOR. 
FIRST FLOOR. Basement. 
>* 
* 
o 
H 
W 
y 
y 
b 
r/4 
y 
w 
td 
X 
X 
Pj 
td b 
td 
to 
y 
0 
hd 
b 
b 
a a 
a 
X 
© 
p 
P 
s? 
E 
P^ 
& 
£ 
© 
p- 
p 
: 
p 
<5 
p 
p- 
& 
p 
p 
P 
P 
P, 
o $ 
P 
S' 
© 
P- 
P 
© 
P 
o- 
P 
P 
E 
5* 
P £.* 
O. © 
: cr 
£- 
0 
0 
OK? 
© 
© 
a- 
P 
: 
j 
© 
o 
g 
room 
O 
O 
B 
P 
© 
© 
3 
© 
© 
© 
© 
© 
B 
room 
p 
© 
P 
3 $ 
o : 
3 : 
room 
© 
© 
3 
< 
P 
© 
*< 
<*? 
p 
© 
© 
: © 
: ? 
s 
(J) 
“ 
: 
© 
© 
B 
5 
cr 
83 
B 
4-*- 
(-J 
IO 
h-i 
p 
to 
i-i 
co 
co 
to 
to 
co 
co 
co to 
to 
O 
oo 
CD 
p 
p 
4- 
00 
CD 
IO 
IO 
Ol 
—T 
4- 
i—i 
Ol 1 o 
Ol 
to 
—f 
p 
Oi 
Ol 
Oi 
44 co 
co 
Contents in cubic feet. 
00 
co 
4- 
i—i 
4- 
d 
i-i 
oo 
p 
Ol 
4- 
ro 
CO 
O Cl 
p-l 
-4 
—r 
CO 
-7 
Ol 
-7 
to 0 
to 1 
p 
Ol 
ID 
O 
o 
O 
t—i 
to 
oo 
Oi 
o 
o 
o 
o 
p 
o o 
0 
0 
to 
Ol 
Ol 
0 
Ol 
44 4- 
GO 1 
o 
£ 
l—l 
l—l 
pa 
Exposed wall exclu- 
o5 
o 
Ol 
4- 
CD 
co 
co 
03 
to 
Ol 
03 
4- 
03 
4- 
to 
CO GO 
03 
GO 
to 
00 
4- 
co 
! sive of glass surface, 
CD 
o 
CD 
03 
o 
03 
oo 
<-a 
-a 
to 
Ol 
Ol 
00 
03 
03 CO 
4- 
O 
“7 
—7 
co 
LO 
square feet. 
© 
00 
co 
Ol 
P 
44 
p 
M 
i—i 
co 
co 
4- 
1-1 
pa 
4- 
1—1 
4-1 4- 
pa 
Cn 
44 
44 
0 
Ol 
1-4 
44 
O 
co 4-1 
Glass surface, square 
Or 
4- 
OO 
'00 
00 
tO 
00 
cc 
CD 
00 
Ol 
CD 
to 
CD 
03 GO 
Ol 
GO 
GO 
C71 
03 
to 
Oi 
to to 
CO 
CD 
1 C3 
to 
to 
to 
ha 
to 
4- 
4- 
C71 
to 
to 
Ol 
to 
IO Oi 
to 
—7 
to 
44 
0 
03 
44 
44 
44 
CO 44 
Equivalent to glnss in 1 
P- 
O 
O 
co 
oo 
l—l 
03 
Ol 
CO 
4- 
4- 
03 
p 
to 
O -7 
co 
03 
44 
Cn 
Oi 
03 
GO 
to to 
=3 
to 
H-a 
h-i 
ua 
pa 
4-1 
4-1 
to 
44 
to 
Lineal feet of exposed 
oo 
LO 
-I 
to 
Cl 
Oi 
CD 
03 
CD 
l—l 
03 
GO 
CD 
4- 
Ol CO 
GO 
co 
4- 
co 
Ol 
pa 
\Y !ll l • 
© 
k9|M 
v V ' 
PCO 
IC|P 
U|H 
£- 
O 
to 
£ 3 b 
03 
CD 
l—l 
to 
co 
CO 
Pi 
3-1 
4— 
44 
03 
4- 
O 
iQ 
4- 
to 
o 
IC 
IO 
Cn 
CD 
O 
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O 
p 
r 
p © s* 
P 
IO 
P PH 
N-.WJ 
© 
4- 
CD 
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44 
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to 
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® B W 3 oa 
HK 
co 
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© 
o 
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tHco 
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,i-i 
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Diam. flow and return | 
*?. 
rtp 
P|P 
4|M 
Up M4—1 
4p 
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pipes to radiators. ; 
i 
co 
4- 
to 
co 
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co 
to 
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co 
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44 
to 
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J 
Proportion of contents | 
—f- 
4- 
oo 
o 
o 
oo 
co 
03 
oo 
Cn 
4- 
0 
—r 
Oi 
03 
00 
O 
) to surface in radiators. 
to 
1 
tp 
'~A—' 
„ b 
1 
i—i 
4-1 4-1 
44 
44 
44 CO 
p 5 
X 
C i 
X 
03 tO 
X X 
03 
X 
-7 
X 
03 
X 
GO 03 
X X 
onsions 
of 
rrn-air 
pipe 
inches. 
4— 
4- 
Ol P 
03 
03 
03 
03 03 
CD 
i -7 
4- 
03 
4-1 
to 
44 
CD 
4- 
44 
CD 
CO 
to 
Area of warm -air pipe j 
'00 
O 
O 
GO 
to 
to 
to 
4- 
in square inches. 
co 
to 
44 
44 
44 
—4 
Velocity of air per sec- i 
co 
hO|H 
bS|M kO|M Up 
bc|p 
ond in feet. 
to 
to 
to 
to 
to 
to 
44 
"1 
Changes of air per hour, i 
to 
1° 
to 
1 
f A 
4 td 
1 
44 
-4 
44 to 
PK < 0 
M 
O 
X 
l—l 
o 
X 
4-1 
GO O 
X X 
4- 
X 
44 
44 
0 
X 
4- 
X 
-4 
P to 
X X 
4-1 i—i 
© 
“So? 
© P »“4 P 
03 
CO 
Ol Ol 
O 
03 
O 
0 P 
S’55' s 
£ 
l+- 
CD 
CD 
CD 
44 
O 
O 
pa 
j Area of exhaust or exit 
00 
.03 
-03 
00 
GO 
p 
| flue in square inches. 
l—i 
to 
to 
1 
4-1 
to 
1 
44 
to 
1 
44 
to 
1 
44 
to 
S- S 5 
2Jg* B 
b2.£0® 
03 
1 
1-1 
03 
4- 
CD 
CD 
X 
p 
X 
oo 
o 
X 
X 
X 
X 
P- 
P‘ 
X 
X 
4-1 
44 
44 
44 
1-4 
© 
£5 ai 0 
to 
03 
03 
to 
O 
to 
to 
03 
'-A-' 
to 
n 
Diameter of cold-air j 
Ol 
tt>|M 
oo 
—7 O 
44 
0 
44 44 
0 to 
P P 
O Ol 
duct or fresh-air inlet j 
in inches. 
-7 
00 
CO 
Ox 
CO 03 
Cn 
1-4 
—7 -4 
' 
—T —7 
Area of cold-air duct 1 
or fresh-air inlet in I 
03 
CO 
o 
GO CO 
03 
00 co 
OO p 
square inches. | ABRAM COX STOVE COMPANY. 
45 
of adding more to the coils. Each room that is ventilated has a separate ventilating flue. One flue 
should not be used for two rooms. 
The warm-air flues or ducts are calculated with the following velocities in feet per second : 1| 
feet to the first floor, 2J feet to the second floor, 3 feet to the third floor, and 3J feet to the fourth 
floor. The areas of the warm-air flues or ducts are ascertained by using the multipliers given in Table 
XXVIII. The cubic feet of air in the hall, changed once in each hour, 12202 X .0266 = 324.5 square 
TABLE VI.—CITY RESIDENCE. SURFACES IN RADIATORS PROPORTIONED, 
ROOMS. 
Sq. ft. 
of glass 
and its 
equiva- 
lent in 
exposed 
wall. 
Multi- 
plier. 
Cubic feet 
of 
air cooled 
per hour 
by glass. 
Contents 
of rooms 
in 
cubic feet. 
Changes 
of air in 
rooms 
per hour. 
Total number 
of cubic feet 
of air to be 
warmed. 
Multiplier. 
Sq. ft. 
of surface 
required 
in rooms 
to warm 
air from 
0 to 70°. 
Remarks. 
' Halls. 
135 
X 
75 
— 
10125 
+ c 
L2202 
X 
1) 
= 22327 
X 
.0114 
= 254 
Indirect. 
E 
0 
0 
Dining room 
118 
X 
75 
= 
8850 
+ ( 
3575 
X 
2) 
= 16000 
X 
.0114 
= 182 
Indirect. 
-1 
Pantry 
16 
X 
75 
= 
1200 
+ ( 
550 
X 
2) 
= 2300 
X 
.0114 
= 26 
Indirect. 
0) 
E 
Parlor 
65 
X 
75 
= 
4875 
+ ( 
3575 
X 
2) 
=12025 
X 
.0114 
= 137 
Indirect. 
Conservatory 
105 
* 
47 
Direct. 
E 
Bed room 
76 
X 
75 
= 
5700 
+ ( 
2210 
X 
1) 
= 7910 
X 
.0072 
= 58 
Direct. 
0 
U. 
Bath room 
23 
X 
75 
— 
1725 
+ ( 
510 
X 
1) 
= 2235 
X 
.0072 
= 16 
Direct. 
Q 
Zo 
Library ~j 
77 
X 
75 
5775 
+ ( 
3850 
X 
2) 
= 13475 
X 
.0114 
= 154 
Indirect. 
s 
Book room j 
Nursery 
57 
X 
75 
= 
4275 
+ ( 
1430 
X 
1) 
- 5705 
X 
.0072 
= 41 
Direct. 
E 
Nurse’s room 
26 
X 
75 
= 
1950 
+ ( 
720 
X 
1) 
= 2670 
X 
.0072 
= 19 
Direct. 
0 
-l 
k. - 
Bath room 
21 
X 
75 
= 
1575 
+ ( 
540 
X 
1) 
= 2115 
X 
.0072 
= 15 
Direct. 
0 
E 
Bed room 
54 
X 
75 
= 
4050 
+ ( 
2250 
X 
2) 
= 8550 
X 
.0114 
= 97 
Indirect. 
Hall room 
44 
X 
75 
= 
3300 
+ ( 
1275 
X 
1) 
= 4575 
X 
.0072 
= 33 
Direct. 
e (" Servants’ room 
48 
X 
75 
= 
3600 
+ ( 
988 
X 
i) 
= 4588 
X 
.0072 
= 33 
Direct. 
3 
•*- 
.. 
25 
X 
75 
= 
1875 
+ ( 
812 
X 
1) 
= 2687 
X 
.0072 
- 20 
Direct. 
Bath room 
16 
X 
75 
= 
1200 
+ ( 
451 
X 
1) 
= 1651 
X 
.0072 
= 12 
Direct. 
3 1 
2 ! Play room 
28 
X 
75 
= 
2100 
+ ( 
1710 
X 
2). 
= 5520 
X 
.0114 
= 63 
Indirect. 
* Surface obtained by dividing by 2.19 as per Table XX. 
inches, requiring two flues, one 36 by 6 inches, and one 18 by 6 inches. The cubic feet of air in 
parlor, 3575, to he changed twice in one hour X .053 = 189.4 square inches, requiring two flues 
each 16 by 6 inches == 96 square inches, or a total of 192 square inches. The play room on fourth 
floor contains 1710 cubic feet of air, which is to be changed twice in one hour, 1710 X .0228 = 38.98 
square inches, requiring a flue 4 by 10 inches = 40 square inches. The sizes of the registers in 
warm-air and ventilating flues can be readily ascertained by reference to Table XXIX. 46 
THE NOVELTY CIRCULATOR. 
The size of main flow pipe is equal to 1224 (which is the square feet of surface in radiators) 
multiplied by .015 (see “Sizes of Main Flow and Return Pipes”)= 18.36 square inches, which is the 
approximate area. The area of a 5-inch pipe being 19.9 square inches, this is the size for main flow 
and return pipes. 
Fig. 50-—Section II to J 
Fig. 52.—Elevation at M. 
DETAILS IN BASEMENT. 
Fig. 51.—Elevation at L. 
The size of the expansion tank is ascertained by the use of the multipliers 
in Table XXV. Thus 1224 by .025= 30.6 gallons, or 1224 by 5.75= 7038 cubic 
inches or 30.4 gallons. The location of the expansion tank is in the bath room on 
fourth floor, and its connections are similar to those in cottage residence. 
Air-emission valves are necessary on all the direct radiators, on the coil in 
bath room, on third floor, and on coil in conservatory, which is composed of 
lj-inch pipes. The other coils do not require air cocks, as the manner in which 
they are connected to the vertical lines permits the water to displace the air and 
allow it to pass up the vertical pipes to expansion tank. The indirect radiators are 
provided with air pipes and arranged to allow the air to pass to the vertical flow 
and return pipes which are connected, as already shown and described, to expan- 
sion tank. 
Fig- 53-—Elevation at K, Heating a Railway Station with the 
Novelty Circulator, No. 14. 
FIG. 54 is a sectional elevation, and Fig. 55, immediately under it, is the plan. The circulator 
is located in the kitchen, on the same floor and level as the radiators. The main flow pipe 
passes vertically upward above the ceiling and inclines up from the circulator to the main tee 
at A to which the air pipe is connected. From this point all flow pipes incline toward the radiators. 
The main return pipe inclines from the radiators to the emptying-valve beneath the circulator. 
The position of the expansion tank is shown above the ceiling. It is placed as high as possible. 
The air pipe from the tee on main flow is connected to the upper part of the tank above water line, 
and the expansion pipe to the bottom of tank. This latter pipe is there connected directly to the 
lowest pipe of the main return. The flow pipes to all the radiators are connected to the top of the 
radiators. It will be observed that in filling the apparatus the water-supply enters the expansion 
tank and passes down the expansion pipe to the return and up the return into the radiators to the 
flow pipes, forcing the air to the highest point at A, where it finds vent through the air pipe into the 
expansion tank. By this arrangement the use of air cocks on the radiators is dispensed with. The 
overflow pipe from the expansion tank passes downward and discharges through an open end into sink 
in kitchen. This pipe maybe used as an air pipe to expansion tank, if the latter is closed on the top. 
The main flow pipe at A is continued in two parallel branch main pipes, which each have 
sub-branches to two and three radiators. By this arrangement a more uniform distribution of the 
temperature is induced. There is one main return pipe, to which the sub-branches are connected. 
The relative positions of circulator in kitchen and expansion tank above ceiling are shown. 
Fig. 56 gives enlarged view of fittings and pipes at A on flow main. It will be observed 
that a hole for the air pipe is provided on the top or highest point of the main tee. The full size 
of the main pipe is continued in each of the branches to the elbows, where the reduction to the 
size of the branches is made after the change in direction has been given to the currents. 
Fig. 57 shows the arrangement of fittings used at B and similar connections on flow main 
to branches. The central opening on tee in main branch is the same size as the other openings 
of tee. The sub-branch from the 3-inch main branch is connected by a 3-inch nipple into a 3 to 
2-incli reducing elbow; on the 2-inch sub-branch is a 2-inch tee with 2-inch nipples in each outlet 
to radiator. One of these outlets is reduced by a reducing coupling to lj-inch pipe which connects 
to two radiators, and the other outlet on the run is reduced by an elbow 2 to 1 inch, and connects to 
one radiator. 
* In this system, which is an open one, the circulator is on the same level as the radiating surface, and therefore a larger size of circulator is used 
than would otherwise be needed. SECTION THROUGH A. B. 
Fig- 54-—Railway Station. Sectional Longitudinal Elevation. 
STREET 
Fig- 55-—Plan of Railway Station. Scale inch to the foot. 
PLATFORM ABEAM COX STOVE COMPANY. 
49 
Fig. 58 is branch flow pipe, at C, to one radiator. In the 3-inch branch main an even 3-inch 
tee is used, the outlet being the same size as the run. In the outlet is a 3-inch nipple with a 
reducing-coupling 3 to 1 finch, the size of flow pipe to radiator. This is preferable to using a 
bushing in tee 3-inch to lfinch, or a 
tee with an opening reduced to If inch. 
The arrangement of fittings 
shown gives an opportunity for a 
reduction in the velocity of currents 
when a change of direction takes place, 
and tends to produce a more uniform 
distribution of temperature than where 
small openings are used. 
In Fig. 59 the connections to a 
cross-fitting in main return pipe at D 
are shown. The 2-inch return main 
from radiators in baggage room enters 
the back of the cross on the run, and 
is connected to the latter by means 
of a bushing 3-inch to 2-inch, and flows in a direct course to the 3-inch main. The two side branch 
returns are connected to the cross by 3-inch nipples, and reducing couplings 3-inch to 2-inch and 
3-inch to lfinch. By this 
enlargement of the space with 
the use of the 3-inch nipples 
in place of a 3 x 2-inch cross, 
or bushings, the velocities of 
the currents are reduced before change in 
the direction takes place. 
Fig. 60 is another connection of 
branches to main return pipe at E. The 
fitting is a 4finch cross, one end of the 
run being reduced to 4-inch. The side outlets are 
reduced by 4J to lfinch bushings to connect to lfinch 
branches. Bushiug may be used instead of 4finch 
nipples, and reducing couplings lfinch to lfinch in 
such an instance as this on account of the relatively 
small area of the lfinch branches to the internal 
capacity of the lfinch cross and bushings. The full- 
size lfinch cross with bushings is more desirable than a reduced fitting; that is, a cross lfinch on the 
run with lfinch side outlets. These are examples of the manner in which fittings and connections 
may be arranged to obtain the most satisfactory results. 
Fig- 56,—Detail of Main Flow at A, 
Fig- 57-—Detail of Branch Flow Pipe at B. 50 
THE NOVELTY CIRCULATOR. 
TABLE VII.—CONTENTS, SURFACES, PROPORTIONS, ETC., IN HOT-WATER HEATING 
APPARATUS IN A RAILWAY STATION. 
ROOMS. 
Contents 
in 
cubic feet. 
Exposed wall 
exclusive 
of 
glass surface. 
Square feet. 
Glass 
surface 
in 
square feet. 
Equivalent 
to glass 
in 
square feet.* 
Lineal feet 
of 
exposed wall. 
Heating sur- 
face in 
radiators or 
coils in 
square feet. 
Direct. 
Dimensions 
of 
flow and 
return pipes 
to 
radiators in 
inches. 
Proportion 
of 
contents to 
surface 
in radiators. 
1. Kitchen 
2520 
310 
96 
127 
29 
2. Dish room.... 
784 
74 
24 
31 
7 
3. Serving room 
784 
74 
24 
31 
7 
4. Passage 
784 
5. Dining room 
6048 
312 
192 
223 
36 
208 
11and 1 
31 
6. Halls 
3465 
90 
64 
73 
11 
80 
1 
43 
7. Depot master’s room 
560 
52 
18 
23 
5 
20 
1 
28 
8. Dining-room office 
1568 
169 
27 
44 
14 
44 
1 
35 
9. Telegraph office 
1008 
84 
42 
50 
9 
44 
1 
22 
10. Gents’ toilet 
1596 
169 
27 
44 
14 
36 
1 
44 
11. Gents’ waiting room 
6804 
370 
176 
213 
391 
12. Ladies’ waiting room 
6804 
370 
176 
213 
39 
492 
1|and 1 
31 
13. Ticket office 
1463 
150 
60 
75 
15 
14. Passage 
490 
15. Ladies’ toilet 
1197 
90 
36 
45 
9 
36 
1 
33 
16. Baggage room 
7511 
685 
239 
307 
66 
216 
1 ¥ 
34 
17. Mail room 
1260 
98 
28 
38 
9 
36 
1 
35 
Totals 
44646 
3097 
1229 
1537 
309 
1212 
33f 
* On the basis that 10 square feet of exposed wall equals 1 square foot of glass 
t Average. ABRAM COX STOVE COMPANY. 
51 
TABLE VIII.—RAILWAY STATION. SURFACES IN RADIATORS PROPORTIONED 
ROOMS. 
Sq. ft. 
of glass 
and its 
equiva- 
lent in 
exposed 
wall. 
Multi- 
pliers. 
Cubic feet 
of 
air cooled 
per hour by 
glass. 
Contents of 
rooms 
in 
cubic feet. 
Changes 
of air in 
rooms 
per hour. 
Total number 
of 
cubic feet 
of 
air to be 
warmed. 
Multipliers. 
Sq. ft. 
of surface 
required 
in rooms 
to warm 
air from 
0 to 70°. 
Remarks. 
4. Passage ' 
5. Dining room 
223 
X 75 
= 16725 
+ ( 6832 
X 1) 
= 23557 
X 
.0092 
= 208 
Direct. 
fi 
73 
X 75 
= 5475 
+ ( 3465 
+ ( 560 
X 1) 
x 1) 
= 8940 
X 
.0092 
= 82 
Direct. 
7. Depot master’s room 
23 
X 75 
= 1725 
= 2285 
X 
.0092 
= 21 
Direct. 
8. Dining-room office 
44 
X 75 
= 3300 
+ ( 1568 
X 1) 
= 4868 
X 
.0092 
= 45 
Direct. 
9. Telegraph office 
50 
X 75 
= 3750 
+ ( 1008 
X 1) 
= 4758 
X 
.0092 
= 44 
Direct. 
10. Gents’ toilet 
44 
X 75 
= 3300 
+ ( 1596 
1) 
= 4896 
X 
.0092* 
= 35 
Direct. 
11. Gents' waiting room ' 
12. Ladies’ waiting room-. 
13. Ticket office 
14. Passage 
501 
X 75 
= 37575 
+ (15561 
X 1) 
= 53136 
X 
.0092 
= 492 
Direct. 
15. Ladies’ toilet 
45 
X 75 
= 3375 
+ ( 1197 
X 1) 
= 4572 
X 
.0092f 
= 37 
Direct. 
16. Baggage room 
307 
X 75 
= 23025 
+ ( 7511 
X 1) 
= 30536 
X 
.0092| 
= 219 
Direct. 
17. Mail room 
38 
X 75 
= 2850 
+ ( 1260 
X 1) 
= 4110 
X 
.0092 
= 38 
Direct. 
* Use additional multipl 
ier .78 to raise to 60°. 
tUse additional multiplier .88 to raise to 65°. 
1 Use additional multipl 
ier .78 to raise to 60°. 
In proportioning the surfaces in the radiators the temperature of the circulating water has 
been taken at 160°. This is especially desirable in a railway station, as a larger extent of surface 
Fig. 58.—Branch Flow Pipe at C. 
Fig. 59.—Main Return at D, 
is necessary on account of the exposed condition of the rooms and the continuous opening and 
closing of the doors. Again, in a railway station of the kind illustrated the rooms are only 52 
THE NOVELTY CIRCULATOR. 
occupied by a few during the greater portion of the time, so that it is more satisfactory to have a 
certain nortion of*surface at a low temnerature than a smaller quantity of surface at a high 
temperature with a corresponding condition of tem- 
perature in the furnace of circulator. The radiators 
are located, so far as possible, near the doors and 
exposed walls, and each radiator is fitted with one 
valve on return pipe. 
The sizes of flow and return pipes are given 
in accordance with rule explained under “ Sizes of 
Main Flow and Return Pipes.” 1216 square feet of 
surface X .015 = 18.24 square inches. Since the 
area of 5-inch pipe is 19.99 square inches, it is the one 
used. 
The size of the expansion tank is ascertained 
by use of multipliers given under “ Expansion 
Tanks.” 1216 square feet of surface in radiators X .025 (Table XXV—A) = 30.4 gallons, or 
7022 cubic inches; or 1216x5.75 (Table XXV—B) = 6992 cubic inches, the internal capacity 
of the expansion tank. 
The emptying valve is on the lowest pipe of the return main below circulator. (See Sectional 
Elevation.) 
Fig. 6o.—Detail of Main Return at E. Warming and Ventilating a Church and School 
with Two Novelty Circulators, No. 17. 
BIG. 61 is a perspective view of the church and school, the smoke or ventilating flues being 
concealed by the towers and roofs. Fig. 62 is a sectional transverse elevation. In this the posi- 
tion of the circulators is shown, as well as the inclination of the main flow and return pipes 
by double light lines and single heavy lines respectively. The dotted lines indicate the main cold-air 
duct. The location of the indirect radiators near the side walls is seen, 
as well as the connections of warm-air ducts from indirect radiators 
to warm-air registers. The position of the exhaust or ventilating 
register in steps of platform is indicated, and dotted lines denote its 
connecting exit-air duct to ventilating flue. The height of the expan. 
sion tank is shown in class room (see I, Fig. 65,) with its overflow, 
supply, and expansion pipe connections. In the ventilating flue V, the 
height of the heating coil, also of the air pipes and of the 
damper, is shown. These parts are the same in the other 
or front ventilating flue. 
Fig. 63 is a sectional longitudinal elevation. 
The two circulators appear in this view, as well as 
the main cold-air and air-circulating 
ducts. The position of the expansion 
tank is shown, and the warm-air 
registers in auditorium are seen be- 
neath each window. 
Fig. 64 is a plan of basement. 
In this plan the location of the circula- 
tors, the smoke pipes, the main flow and return pipes and branches with sizes, the indirect radiators 
with surfaces in each, the cold- and warm-air ducts with the dimensions, the exit-air ducts and ventilat- 
ing flues, and the air-circulating ducts are all distinctly shown. By the use of the air-circulating 
ducts provided, the air within the building can be at first heated, and when the building is not occupied 
it may be kept warm without taking in cold air or fresh air. The latter need only be used when 
ventilation is recpiired. The air-circulating ducts are fitted with four doors, two of which are shown 
Fig. 61.— Perspective View of Church. Benj. D. Price, Architect, 54 
THE NOVELTY CIBCULATOB. 
closed against the 72 by 27-inch main cold-air duct, the third is closed at the 42 by 27-inch exit-air 
duct, and the fourth is at the 54 by 36-inch exit-air duct. By opening the four doors communication 
is made between the exit-air register and the cold-air ducts, and by closing the two dampers in the 
upper part of the ventilating flues and the damper in cold-air duct at the cold-air inlet the exit and 
entrance of air into the building ceases, and, as the air is heated, the circulation is up through the 
warm-air ducts, and down through the exit-air ducts into the cold-air ducts to indirect radiators. 
When the air in the building has become heated by this plan and ventilation is needed, the doors in 
Fig. 62.—Sectional Transverse Elevation. Scale yg inch to the foot. 
the circulating ducts are closed, and the dampers in ventilating flues and at cold-air inlet are opened. 
If it is desired, the air in basement can be allowed to circulate through the building. 
The flow and return pipes are arranged so that either or both circulators can be used. The 
surfaces heating the auditorium form one portion of the system and those heating the lecture and 
school rooms another portion. This is accomplished by the introduction of a valve on each return 
main near circulator. Continuous circulation passes through each main flow pipe through the heating 
surfaces in the ventilating flues. The return from these surfaces in the small ventilating flue near 
circulators is connected directly to the circulators. 
Fig. 65 is plan of main floor. The position of the warm-air registers is indicated by the 
letters W R, the exhaust or exit-air registers by letters E R. The latter registers are in the floor, ABRAM COX STOVE COMPANY. 
55 
excepting three and the one in the steps to platform. The three registers are placed as low as pos- 
sible and the warm-air register in auditorium between the vestibules is placed as high as possible 
beneath the window. Direct radiators heat the two vestibules. 
Fig. 66 illustrates the connections to direct radiator in vestibule. This radiator has double 
flow and return pipes. The object of this arrangement is to secure heat in this radiator with either 
portion of the system in use. A is flow pipe from auditorium main, B flow pipe from lecture-room 
main, D return pipe to auditorium main, E return pipe from lecture-room main. When the valve on 
main return of auditorium portion is closed, the circulation will be through the auditorium and lecture- 
room flow main and through the lecture-room return main to circulator. When this valve is open 
and the other closed on lecture-room return main, the circulation is through the two main flow pipes 
and the return main of the auditorium portion. 
Fig. 67 gives details of heating surfaces in front or large ventilating flue or shaft. A is audi- 
torium main flow, A1 auditorium flow to coil in ventilating flue and air pipe, B is lecture-room flow, 
Fig. 63.—Sectional Longitudinal Elevation. Scale inch to the foot. 
Bl lecture-room flow to coil and air pipe. C provides continuous circulation in return main of either 
portion, D auditorium main return, D1 auditorium return from coil, E lecture-room return, E1 lec- 
ture-room return from coil. Air pipes extend above the coil and the level of expansion tank. 
Fig. 68 and Fig. 69 are elevations and a plan of the heating surfaces and connections of expan- 
sion tank in and near the back or small ventilating shaft. A1 and A are air pipes extending above the 
level of the expansion tank from the coil in ventilating shaft. B1 is flow pipe from and air pipe to 
lecture-room main, B flow pipe from and air pipe to auditorium main. C1 and C are return pipes of 
coils to the top of which is connected the expansion pipe D; the other ends of these pipes R1 and R 
are connected direct to circulators; that is, between the circulators and the gate valves on the main 
return pipes. E is the water-supply pipe to expansion tank. It is passed up through the ventilating 
shaft, as well as G, the overflow pipe, in order to be concealed from view in class room. The end of 56 
THE NOVELTY CIRCULATOR. 
overflow pipe is open and discharges into a sink in cellar and can be used as an air pipe to expansion 
tank if the latter is covered. From the details of connections described and illustrated in Figs. 68 
and 69 it will be observed that a continuous circulation is secured in the main flow pipes. This is 
done in order to assist in maintaining a low temperature in whichever portion of the system is not in use. 
Fig. 64.—Basement Plan. Scale inch to the foot. 
The air emission from the direct radiator is provided for by air cocks or valves. The arrange- 
ment of the main flow pipes provides for the continuous escape or emission of the air from the indirect 
radiators. The points A1 and B1, Fig. 67, are respectively the highest points on the front end of the 
auditorium and lecture-room flow pipe. The points F1 and F, Fig. 69, are the highest points on the back 
main flow pipes of the lecture room and auditorium respectively. The main flow pipes incline upward ABRAM COX STOVE COMPANY. 
57 
from the circulator to the points just mentioned where they are open to the atmosphere through four 
air pipes. The branches from the main flow to the indirect radiators incline from the flow main to 
the radiator. This is shown in Fig. 70, where the point A A is higher than the point B B and the 
point C C higher than D D. The return main has its inclination downward toward the circulators 
and parallel to the main flow pipes. 
Fig. 65.—Plan of Main Floor. Scale A inch to the foot. 
The expansion tank is located as shown in class room I. Its contents are found by multiplying 
the square feet of surface in radiators 2502 by .02 and the product is the contents, namely 50 gallons, 
or 2502 by 4.5 = 11,259 cubic inches, or 48.7 gallons. (See Table XXY.) 
Fifif. 70 ffives details of the cold and warm-air ducts and the relative inclinations of the flow 
and return mains and branches. The point F is higher than the point A A on the flow pipe at back 58 
THE NOVELTY CIRCULATOR. 
of basement; the pipe at F connects to coil and air pipe in the back or small ventilating shaft, A A 
and D D are higher than E E on the central or main flow pipe and G G on the central main return. 
The levels at A, B, C, and I) on the branch flow and return pipes have been described. 
The warm-air ducts have a short part horizontal. This is necessary in order to keep the casing 
of the radiator out from the window of basement. Preferably the passages of warm-air ducts should 
be vertical and as straight as possible. To the casing of the indirect radiators are connected the cold- 
air duct and an air-mixing passage or duct, Each of these is fitted with damper, as shown. By 
reversing the levers on these dampers the cold-air duct damper will be kept closed and the air-mixing 
damper open, or either may be adjusted so as to be partially open or closed. 
Fig. 66.—Connections to Direct Radiator in Vestibule. 
Fig. 67.—Front Ventilating Shaft. 
In proportioning the surface in radiators in church and school rooms, the temperature of the 
water has been taken at 180°. Such buildings do not require as much heat relatively as dwellings, on 
account of the number of people assembled in them. As soon as such places are occupied the tem- 
perature increases, and provision should be made to meet this addition to the temperature. It is there- 
fore desirable not to provide too much surface in the radiators, but preferably to make arrangements 
for quick heating up with a relatively small amount of heating surface and a proportionate increase in 
the temperature of the water. In quickly heating up, the circulating-air ducts will be found econom- 
ical and useful, and with the proper use of the air-mixing dampers the temperature of buildings heated 
in the manner described will be under perfect control. ABRAM COX STOVE COMPANY. 
59 
TABLE IX.—CHURCH AND SCHOOL ROOM. CONTENTS, PROPORTIONS, SURFACES, ETC. 
w 
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0 
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3 
3 
o 
® 
© 
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P 
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® 
cr 
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S1 
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£ 
3 
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in 
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cr 
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ID 
ID 
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square feet. 
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1—L 
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Glass surface, square 
LD 
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05 
1 
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X 
Size 
cold- 
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-i 
TABLE X.-CHURCH AND SCHOOL ROOM. SURFACES IN RADIATORS PROPORTIONED 
Square 
feet of 
glass and 
ROOMS. its equiva- 
lent in 
exposed 
wall. 
Multipliers. 
Cubic feet 
of aii- 
cooled per 
hour 
by glass. 
Contents 
of rooms in 
cubic feet. 
Change Total number 
•of. of 
air in cubic feet 
rooms 0f ajr |)e 
per warmed, 
hour. 
Multipliers. 
Square feet of surface 
to each room required 
to warm air from 0 to 
degree indicated in 
next column. 
Remarks. 
Class room No. 1 171 
X 75 
=12825 
+(11646 
x 2 ) = 36117 
X.009 
= 325 
Indirect for 70°. 
Lecture room 174 
X 75 
=13050 
+(29970 
X 3 ) =102960 
X.009 x.78 
= 722 
Indirect for 60°. 
Class room No. 2 11 — 
X 75 
= 8400 
+( 4950 
X 2 ) = 18300 
X.009 
= 164 
Indirect for 70°. 
Auditorium 497 
X 75 
=37275 
+(70642 
X li) =143238 
X.009 X.78 
= 1005 
Indirect for 60°. 
Tower vestibule —67 
X 75 
=20025 
4 ( 3456 
x 1 ) = 23481 
X.0072 X.78 
= 132 
Direct for 60°. 
Central vestibule 110 
X 75 
= 8250 
+ ( 2590 
XI)--- 10842 
X.0072 X.78 
= 60 
Direct for 60°. 60 
THE NOVELTY CIRCULATOR. 
TABLE XL—PROPORTIONING MAIN FLOW AND RETURN PIPES IN CHURCH AND SCHOOL. 
ROOM HEATED. 
Square feet 
of 
surface supplied. 
Multipliers. 
Approximate 
area of 
pipe. 
Square inches. 
Actual area 
of pipe. 
Square inches. 
Size of pipe- 
Nominal inside 
diameter. 
First Main: 
Class room I and ventilating flue 
355 
.015 
5.32 
4.78 
2| in. 
Lecture and school rooms, etc 
1384 
.015 
20.76 
19.99 
5 “ 
Lecture room, etc 
879 
.015 
13.18 
12.73 
4 “ 
“ “ 
729 
.015 
10.93 
12.73 
4 “ 
“ “ “ 
579 
.015 
8.68 
7.38 
3 “ 
“ “ 
429 
.015 
6.43 
7.38 
3 “ 
Class room II, vestibule, etc 
279 
.015 
4.18 
4.78 
91 “ 
-2 
Second Main: 
Auditorium and ventilating flue 
365 
.015 
5.49 
4.78 
91 <( 
"2 
Auditorium, etc 
525 
.015 
7.87 
7.38 
3 “ 
Auditorium, vestibule, and ventilating flues 
1272 
.015 
19.08 
19.99 
5 “ 
“ 
747 
.015 
11.20 
12.73 
4 “ 
“ 
577 
.015 
8.65 
9.88 
H “ 
“ 
417 
.015 
6.25 
7.38 
3 “ 
“ “ “ “ “ 
289 
.015 
4.33 
4.78 
91 u 
*2 
QUANTITY OF AIR TO BE PASSED THROUGH VENTILATING FLUES PER HOUR, AND 
AREAS REQUIRED. 
Class room I cubic contents X 2 changes = 23,292 cubic feet of air per hour. 
Lecture room “ “ X 3 “ = 89,910 “ “ “ 
Class room II “ “ X 2 “ = 9,900 “ “ “ 
Auditorium “ “ X 1J “ =105,963 “ “ “ 
Total, 229,065 cubic feet of air per hour. 
229,065 cubic feet of air at a velocity of 3 feet per second X .0133 = 3046 square inches area 
in openings to vertical ventilating flues. 
Openings to vertical ventilating flues. 
1 opening 18 inches X 17J inches = 315 square inches. 
1 “ 30 “ X 27 “ = 810 “ 
1 “ 54 “ X 36 “ =1944 “ 
Total in three openings, 3069 square inches. ABRAM COX STOVE COMPANY. 
CHANGES OF AIR IN ROOMS RELATIVE TO VENTILATION, CUBIC CONTENTS OF ROOM 
AND QUANTITY OF AIR PER HOUR BEING KNOWN. 
Class room I is furnished for forty occupants, who each require an 
average of 600 cubic feet of air per hour. 
24,000 cubic feet of air per hour 
600 X 40 =^rwxa—u- x. ■ ■ = 2.06 
11,646 cubic feet of air in room 
the number of times the air 
in room should be changed 
per hour. 
Lecture room is arranged to seat 200 persons, who each require an 
average of 400 cubic feet of air per hour. 
400 X 200 = CVCfe11a!rPerhOnl= 2.66 
29,970 cubic feet of air 111 room 
the number of times the air 
in room should be changed 
per hour. 
Fig. 68.—Elevation and Plan of Back Ventilating 
Shaft. 
Fig. 69.—Elevation at Lower Part of 
Back Ventilating Shaft. 
Class room II is to seat 20 occupants, and 450 cubic feet of air per 
person per hour should be provided. 
™ 9000 cubic feet of air per hour _ 
450 X 20= -Tr-r A.n.n.. = 1.81 
4950 cubic feet of air m room 
the number of times the air 
in room should be changed 
per hour. 
Auditorium seats 300 occupants, for whom 350 cubic feet of air 
per person per hour should be provided. 
o£A \/ Qun 105,000 cubic feet of air per hoar 1 AQ 
70,642 cubic feet of air in auditorium 
the number of times the air 
in room should be changed 
per hour. 
“Air required for Ventilation,” in chapter on “Air,” 62 
THE NOVELTY CIRCULATOR. 
PROPORTIONING WARM-AIR DUCTS. THE VELOCITY OF AIR IN FEET PER SECOND AND THE 
NUMBER OF TIMES THE AIR IN ROOM IS CHANGED, PER HOUR, BEING KNOWN. 
Class Room I.—11,646 cubic feet in room X.04 (multiplier*) = 465.8 square inches 
2 ducts 6 X 40 inches = 480 square inches area. 
Lecture Room.—29,970 cubic feet in room X.06 (multiplier*) = 1798.2 square inches 
5 ducts 8| X 42 inches = 1785 square inches. 
Fig. 70.—Details of Cold and Warm-Air Duets. 
Auditorium.—70,612 cubic feet in room X-03 (multiplier*) = 2119.2 square inches. 
6 ducts 8| X 42 inches = 2142 square inches. 
ClassRoom II.—4950 cubic feet in room X.04 (multiplier*) = 198 square inches. 
1 duct 6 X 33 inches = 198 square inches. 
* See Table XXVIII for multipliers. ABRAM COX STOVE COMPANY. 
63 
In this case the velocity is taken at 2 feet per second and the air is changed in the auditorium 
14 times per hour, in class rooms I and IT 2 times per hour, and in lecture room 3 times per hour. 
PROPORTIONING WARM-AIR REGISTERS, THE AREAS OF WARM-AIR DUCTS BEING KNOWN. 
Class Room I.—480 X 1.33 = 638 square inches. 
2 registers 24 X 16 inches = 768 square inches. 
Lecture Room.—1785 X 1.33 = 2374 square inches. 
5 registers 26 X 20 inches = 2600 square inches. 
Class Room II—198 X 1.33 = 263 square inches. 
1 register 14 X 22 inches = 308 square inches. 
Auditorium.—2142 X 1.33 inches = 2849 square inches. 
6 registers 26 X 20 inches = 3120 square inches. 
The register sizes taken are somewhat larger than the figures show to be necessary, but are 
preferred because larger openings tend to reduce the velocity of the air at its entry into the room. 
See “ Air ” and rules therein. 
PROPORTIONING HORIZONTAL EXHAUST AND VENTILATING DUCTS, IN WHICH THE 
VELOCITY OF THE AIR DOES NOT EXCEED 3 FEET PER SECOND. 
Class Room I.—11,646 cubic feet of air in room X.0266 (multiplier) = 310 square inches. 
1 duct 18 X inches = 315 square inches. 
Lecture Room.—29,970 cubic feet of air in room X.0399 (multiplier) = 1195 square inches. 
4 ducts 30 X 10 inches = 1200 square inches. 
Class Room II.—4950 cubic feet of air in room x.0266 (multiplier) = 131 square inches. 
1 duct 22 X 6 inches = 132 square inches. 
Auditorium.—70,642 cubic feet of air in room X.0199 (multiplier) = 1406 square inches. 
3 ducts 12 X 27 inches =972 square inches. 
1 duct 12 X 42 inches =504 square inches. 
1476 
The air is changed twice per hour in the class rooms, three times in the lecture room, and one 
and one-half times in the auditorium. For multipliers see “ Air ” and rules therein. 
PROPORTIONING REGISTERS TO EXHAUST AND VENTILATING DUCTS WHEN THE VELOCITY 
IN THE LATTER EXCEEDS THE VELOCITY IN THE WARM-AIR DUCTS. 
Class Room I.—315 square inches area of exhaust and ventilating duct X 1.5 = 472 square 
inches. 
1 register 24 X 20 inches = 480 square inches. 64 
THE NOVELTY CIRCULATOR 
Lecture Room.—1200 square inches area of ventilating ducts X 1.5 = 1800 square inches. 
4 registers 24 X 20 inches = 1920 square inches. 
Class Room II.—132 square inches area of ventilating duct X 1.5 = 198 square inches. 
1 register 12 X 19 inches = 228 square inches. 
Auditorium.—1476 square inches area of ventilating ducts X 1.5 = 2214 square inches. 
3 registers 24 X 20 inches = 1440 square inches. 
1 register 60 X 12 inches = 720 square inches. 
2160 
See “ Air ” and rules therein. 
PROPORTIONING FRESH OR COLD-AIR DUCTS, THE AREAS OF WARM-AIR DUCTS BEING KNOWN. 
Class Room I.—465.8 square inches area of warm-air duct X.8 = 372 square inches. 
1 duct 18 X 20 inches = 360 square inches. 
Lecture Room.—1798 square inches area of warm-air duct X.8 = 1438 square inches. 
5 ducts 42 X 7 inches = 1420 square inches. 
Class Room II.—198 square inches area of warm-air duct X.8 = 158 square inches. 
1 duct 20 X 8 inches = 160 square inches. 
Auditorium.—2119 square inches area of warm-air ducts X .8 = 1695 square inches. 
6 ducts 46 X 6 inches = 1656 square inches. 
See “ Air ” and rules therein. 
VERTICAL VENTILATING FLUES. 
Each flue is 60 feet high. The small hue is 30 X 12 inches = 360 square inches = 2.5 square 
feet. The large hue is 54 X 12 inches =648 square inches = 4.5 square feet. Total vertical hue 
area 1008 square inches = 7 square feet. 
At a velocity in vertical hue of 10 feet per second 229,065 cubic feet of air will be discharged 
in one hour through a hue area of 916 square inches, or 6.36 square feet. 
229,065 X.004 = 916.2 square inches. (See Table XXVIII in “ Air.”) 
To maintain a velocity of 10 feet per second in a ventilating hue 60 feet high, calculate as 
follows : 
Velocity squared = 10 X 10 = 100 divided by constant A 5.375 (see Table XXX) = 18.6° 
excess of temperature required in ventilating hue above outside temperature. Therefore if the tem- 
perature of the air in the ventilating hues is 50°, and the external atmosphere 30°, a velocity a little 
in excess of 10 feet per second is maintained in the ventilating hue. As the outside temperature 
decreases, the velocity in hue increases. These are the velocities and proportions of temperatures and 
areas necessary to simultaneously ventilate the school rooms, lecture room, and auditorium. ABEAM COX STOVE COMPANY. 
65 
To ventilate the school rooms and lecture room at one time, and the auditorium at another, 
since all the apartments may not be used at the same time, reduces the velocity in the ventilating flues 
to a great extent. 
The school rooms and lecture room require 123,102 cubic feet of air per hour through ventilat- 
ing flue of 1008 square inches area, 1008 123,102 = .0081, which in Table XXVIII indicates that the 
velocity in a flue of this area is 5 feet per second. The velocity squared, 5 X 5 = 25 5.375 (see Table 
XXX) = 4.6°, which is the excess of temperature required above that of the outside temperature to 
maintain a velocity of 5 feet per second. 
For the auditorium the calculation may be thus given : = .0094,which indicates a velocity 
according to Table XXVIII of feet per second. The velocity squared, 4.25 X 4.25 = 18.06 
5.375 = 3.54°, which is the excess of temperature required above that of the outside atmosphere. 
To use the large ventilating flue only for the school rooms and lecture room requires a velocity 
of 7J feet per second, and an excess of temperature of 10|° above that of the outside atmosphere. 
The calculation is as follows: T2ETfr2 = *0052, or a velocity of 7\ feet per second. (See table XXVIII.) 
56 7 5 
The velocity squared, 7.5 X 7.5 = 5,875(constant A, Table XXX) = 10-5° excess of temPerature' 
HEATING SURFACE IN EXHAUST OR VENTILATING FLUES. 
It is an advantage to place a small quantity of heating surface in the ventilating Hue in order 
to heat the surfaces of the flue so that the temperature of the air exhausted from the rooms will 
not be quickly reduced on entering the ventilating flue. This heating surface also tends to create a 
velocity at the flrst application of heat to the system, and prevents tendency to down currents by 
irregular winds. 
An approximate way of proportioning this heating surface is to divide the surface of the 
sides of the flue in square feet by 12; the result will be the square feet of heating surface. 
The large flue in the church and schools measures 11 lineal feet in its side walls, which 
multiplied by 60 feet its height equals 660 square feet of surface in walls, and this divided by 12 
equals 55 square feet of surface in heating pipes. 
The surface required in the small flue is thus ascertained : 7 X 60 = — 35 square feet in 
heating pipes. 
To ventilate the school rooms and lecture room in the summer time it will he necessary to 
increase the temperature of the air from these rooms about 5° above the temperature of the outside 
atmosphere. Taking the temperature of the rooms at the same temperature as the outside atmos- 
phere, say 70°, 123,102 cubic feet of air is to be raised 5°. The surface required in ventilating flues 
to heat this quantity of air 5° may be thus ascertained: 
Multiply the weight of a cubic foot of air at 70°, .0748 pounds (see Table XXII), by the 
specific heat of air, .238 (see Table XXXII); the result is .0178 unit of heat necessary to raise 1 cubic 66 
THE NOVELTY CIRCULATOR. 
foot 1°. The increase of temperature 5° multiplied by .0178 gives .089 unit of heat required 
to raise the temperature of 1 cubic foot of air 5° in 1 hour. The cubic feet of air to be heated are 
123,102, which X .089 = the total number of units of heat per hour, 10,956. One square foot of 
surface with water at 160°, and surrounding air 75°, will approximately emit 127.5 units of heat per 
hour. Hence 10,956 divided by 127.5 equals 86 square feet of heating surface necessary in flues to 
maintain a velocity of 5 feet per second. It therefore appears that with 90 square feet of surface in 
ventilating flues an adequate ventilation may be had in the summer time. 
To maintain a velocity of 10 feet per second with an excess of temperature in the flues 
of 20°, which is more desirable than 5°, in order to ventilate all the building at one time in the 
summer, will require a greater quantity of surface, which may be ascertained as follows: 
Weight in pound or cubic foot 
of air at stated temperature 
[■ X specific heat of air X -j 
Number of degrees difference between 1 
air in flue and outside atmosphere J 
j Cubio feet of air to be 
l heated per hour , 
X 
Number of square 
feet required in 
heating surface. 
Units of heat emitted approximately per square foot of surface 
Substituting figures in this formula, we have the following as the calculation for ventilating 
the entire building: 
.0748 X .238 X 20 X 229,065 r1Q , 
— L— — 518 square feet of heating surface. 
((160-90) X 2.25) = 157.5 1 
The heating surface should be placed at the base of the Hue, or extended up from the base, 
preferably to putting this surface at the top of the Hue. 
The number of heat units emitted per 1° difference between temperature of surface and 
temperature of air is increased with the increase in volume of air. Warming and Ventilating a City Office, using 
the Novelty Circulator No. ii.* 
Fig. 71.—Floor Plan of City Office. Approximate scale Jg- inch to the foot. 
SHE premises herein referred to are the offices of the Iron Age, Metal Worker, etc., Nos. 96- 
102 Reade street, New York, in which the Novelty Circulator was installed in October, 
1890. Gas is used as fuel, and nothing could better demonstrate the practical economy 
of the Novelty Circulator than the experience of the two seasons which have passed, and the small 
cpiantity of gas required. The premises have been abundantly and thoroughly warmed, and yet the 
consumption of gas through ordinary winter weather has averaged as little as 500 feet per day, and 
in the severe weather of January, 1892, it averaged less than 800 feet per day. (See Metal Worker, 
January 80, 1892.) 
* In this system, which is an open one, the circulator is on the same level as the radiating surface, and therefore a larger size of circulator is used 
than would otherwise be needed. 68 
THE NOVELTY CIRCULATOR. 
Fig. 71 is floor plan, indicating the manner in which the space is apportioned to the various 
oflice requirements. The position of the circulator is shown to be nearly central. The distribution 
of the heating surface in the pipes and coils is also given. The blow-off or emptying pipe and 
water supply pass between the beams and beneath the floor from the heater to the west wall, and 
these are the only two pipes connected with the system which are not between the floor and ceiling 
of the floor heated. 
Fig. 72 is an elevation of the apparatus to larger scale, and shows the relative levels of the 
circulator, the floor main, the coils, and the one radiator employed, the return main, and the 
expansion tank. This view is taken in the west room looking east. By referring to the numbers 
of the coils they can be readily located on plan, Fig. 71. The distance of each coil from circulator 
is given. It will be noticed that one coil is no less than 74 feet away, and that the upper pipe of all 
the coils is about level with the return inlet on heater. It will also be observed that the circulation 
passes directly through the flow mains and not to the tank, thus heating the surfaces by circulation 
Fig. 72.—Sectional Transverse Elevation Showing Circulator, Coils, etc 
direct from the heater without having the temperature of the water reduced in a tank, as is 
sometimes done to assist circulation in the return pipes. The location of the gas meter is shown, 
through which city gas is passed to the fire-box of the circulator and used as fuel. By this use of 
gas all the inconvenience, dust, and labor of coal tires is dispensed with, and the cost in this instance, 
as already mentioned, scarcely exceeds coal and the accompanying expense of handling and storing, 
removing ashes, etc. 
Fig. 73 shows No. 5 coil on partition. The flow and return connections are seen coming 
through the partition. Fig. 74 is section through ventilating duct which passes along the outside 
walls, the top forming an extension to the window-sills and the sides forming supports for the coils 
and pipes as shown. Fig. 75 shows the manner of connecting coils Nos. 9 and 10 to the 2-inch flow 
and return pipes. Fig. 70 gives the manner of connecting coil No. 12 and others of the same kind, ABRAM COX STOVE COMPANY. 
Fig. 77 shows details at A (Fig. 71) of the blow-off, water supply, and return main. The 
waste tank below the door is also shown. This tank is made necessary on account of the trimmer 
beam over which the blow-off* pipe and overflow pass, as in the installation of this work no beams 
were allowed to be cut. When emptying the system the water flows out until the level of the 
bottom of the pipe over trimmer beam is reached. The plug in blow-off is then opened, and the 
rest of the water flows into the waste tank, from which it is removed by hand pump and pail. In 
Fig. 78 are shown details at F in the plan, indicating the relative positions of main flow pipe, air 
pipe, expansion pipe, and expansion tank. 
Fig* 73*—Coil Xo. 5 on Partition. 
In proportioning the surfaces in coils and radiators for this office the external temperature 
was taken at zero, and the internal temperature at 70°. The east office contains in actual space, 
exclusive of halls and elevator shaft, 26,373 cubic feet of air, 572 square feet of exposed wall, and 
352 square feet of glass. Taking the wall at a ratio of 20 square feet of its exposed surface 
as equivalent in cooling effect to one square foot of glass, the calculation is 352 -f- 28 = 380 square 
feet of glass and its equivalent. This multiplied by 75, a constant = 28,500 + 26,373 = 54,873. 
Multiplying this in turn by .0072 constant for water temperature of 180° = 394 square feet of heating 
surface in coils. 70 
THE NOVELTY CIRCULATOR. 
The west office contains 27,003 cubic feet of space exclusive of stairways, 680 square feet 
of exposed wall, and 352 square feet of glass. Taking the wall at the same ratio to glass as in the 
east office the figures are 352 + 34 = 386 square feet of glass and its equivalent. This multiplied 
by 75 = 28,950 + 27,003 = 55,953. This in turn multiplied by .0072 = 403 square feet. To this 
15 per cent, more surface was added on account of the space being divided into 
several small compartments and therefore more difficult to heat, making the surface 
required in coils 463 square feet. 
The surface actually installed is as follows: East office, 274 square feet in 
coils and radiator, and 135 square feet in 2-inch flow and return pipes, making 
a total of 409 square feet, which is equal to a proportion of 1 square foot of surface 
to 64 cubic feet of space. In the west office there are 290 square feet in coils and 
177 square feet in 2- and 3-inch flow and return pipes, making a total of 467 square 
feet, which is equal to a proportion of 1 square foot of surface to 58 cubic feet 
of space. The east and west offices together contain a total of 53,376 cubic feet 
of space, and have 876 square feet of direct heating surface in coils, radiators, and 
pipes, which is equal to a proportion of 1 square foot of heating surface in coils, etc., 
to 60 cubic feet of space. 
The entire system contains 350 gallons of water. The expansion tank has 
a total capacity of 31 gallons, and below overflow a capacity of 24 gallons. This rather large 
capacity was provided on account of the shape of the tank. 
Fig. 74.— Section 
Through Ventilating 
Duct. 
Fig. 75.—Detail of Coils Nos. 9 and 10. 
Fig. 76.—Detail of Coil No. 12. 
To more fully describe this system, which is uncommon in hot-water heating practice, the 
specification of the work, and in accordance with which the apparatus was installed, is appended. 
It is of use here also as a specimen of short specifications, which are at the same time inclusive and 
descriptive,—something much needed in hot-water heating work. ABRAM COX STOVE COMPANY. 
71 
SPECIFICATION 
of certain pipes, valves, and fittings, etc., to be erected on third floor at 96, 98, 100, and 102 Reade 
street, Kew York. 
Fig- 77-—Details at A of Blow-off Waste Tank, etc, 
The pipes are to be arranged as shown on plan, Fig. 71. From top of heater a 6-inch 
vertical flow pipe is to be connected to elbow (6 inch). In this pipe there is to be a flange union and 
a hole tapped (f-inch pipe) for thermometer at T. The pipe will be about 4 feet from heater to 
elbow. From elbow 6-inch pipe leads to 6-inch tee as shown on plan; the top of this tee is to be 
tapped (lj-inch pipe), F, Fig. 71, for air-vent. For 3 feet on north side of tee the 6-inch pipe is to be 72 
THE NOVELTY CIRCULATOR. 
continued (see plan) to flange union, one flange for 6-inch pipe and the other tapped eccentrically 
for 3-inch pipe, so that the top of 3-inch pipe will be level with top of 6-incli pipe, and on south 
side to tee H, Fig. 71. These 6 and 3-inch pipes are to be level from end to end, and about 30 
inches from ceiling. At each end, B and C, Figs. 71 and 72, there are to be vertical 3-inch pipes 
about 7 feet long, at the lower end of which pipes there are to be 3-inch tees, 2-inch on the run, to 
be reduced by nipples and reducing couplings 3-inch to 2-inch at C, south end, a 3-inch to 2-inch 
reducing elbow may be used in place of one reducing coupling. On the north side, B, the center 
of this tee is to be 24f inches from the floor 
(new floor), and on the south side, C, 26 
inches from the floor (new floor). At these 
levels 2-inch mains continue, without any 
inclination whatever, to the east as far as 
coils Xos. 14 and 15, and to the west as far 
as reducing coupling to coil Xo. 6 and point 
marked D. 
MAIN RETURN PIPES 
From coils Nos. 15 and 16 on the 
south side the 2-inch return pipes begin 
and incline at C where the 3 x 2 x 2-inch tee 
is 3-inch to center above floor and from coil 
No. 14 on the north side and point marked 
II, the 2-inch return pipes begin and incline 
to B, where the center of the 2 x 2 x 3-inch 
tee is 2f inches above the floor. From B 
and C the main returns are of 3-inch pipe 
and incline to A, where the center of the 
3-incli pipe is 2 inches above the floor. 
Between A and B is a flange union. At 
A (see Fig. 77) a 4-inch tee receives the 3-inch return mains and a vertical 4-inch pipe goes upward 
to level of opening in the circulator. The under side of this 4-inch tee is tapped (f-inch pipe) for 
blow-off or emptying pipe and water supply f-inch connection. In the 4-inch between elbow and 
heater is 4-inch tee with lf-inch outlet for expansion pipe; there is also a flange union, and the top 
of pipe is tapped (f-inch pipe) for thermometer marked T on plan. 
Fig. 78.—Details at P of Air Pipe, Expansion Tank, etc. 
BRANCH FLOW PIPES. 
The branch flow pipes to coils Nos. 4 and 5, Fig. 73, are 2-inch pipe perfectly level with 2-inch 
main with 2-inch elbows, nipples, and eccentric reducing couplings. The 1 f-inch flow pipes to coils ABRAM COX STOVE COMPANY. 
73 
Nos. 6 and 7, also to Nos. 9 and 10 (Fig. 75), and Nos. 14, 15, and 18, are level and connect 
to main by 2-inch nipple and eccentric reducing couplings. These couplings are used so that the 
top of all flow pipes are level. The coils Nos. 1, 2, 3, 8, and 11, and also No. 12 (Fig. 76), and Nos. 
13, 16, and 17, are connected to 2-inch mains by 2-inch tees, facing down, with 2-inch nipple and 
2-inch to lf-inch reducing elbows, and coil No. 19 by lf-inch pipe. 
BRANCH RETURN PIPES. 
The lowest pipes of coils Nos. 14 and 15 are connected to 2-inch main return pipe by 2 to 
lf-inch eccentric couplings, so that the under side of lf-inch and 2-inch pipes will be level. The 
lowest pipes of coils 4 and 5 are connected to 2-inch branch return pipes by 2-inch to lf-inch 
reducing elbows. The lowest pipes of coils Nos. 9, 10, and 18 are connected to 2-inch main returns 
to tees 2 x 2x lf-inch, and coils Nos. 1, 2, 3, 8, 11, 12, 13, 16, and 17 are connected to 2-inch main 
return by tees 2 x 2 x lf-inch, with outlet facing horizontally. The position of these tees will be 
about 6 inches beyond return bends so as to allow for valve. Coil No. 19 is connected bj" lf-inch 
pipe to 2 x If x lf-inch tee. 
RADIATORS AND COILS 
There are to be nineteen return bend coils, as shown on plan, and of the sizes given, of lf-inch 
pipe, and also one radiator 45 inches high with 45 square feet of surface of the “Perfection” pattern. 
VALVES. 
Six coils Nos. 4, 5, 6, 14, 15, and 18, the radiator and circulating pipes are to have gate valves 
of the Rensselaer pattern and the other coils are to have ordinary angle valves, with hard seats. 
Valves are to he nickel-plated and fitted with keys; in all, fourteen (14) angle valves and eleven (11) 
gate valves. 
CIRCULATING PIPES. 
At the points marked E E E (see Fig. 71) there are to be f-inch pipes between the flow and 
return pipes. On these pipes are to he the f-inch gate valves above mentioned. The flow pipes are 
to be connected to these pipes E by 2 x 2 x 1 f-inch crosses, and If to f-inch bushings, and 2 x f-inch 
tees on the return connection. At D and TV the circulating pipes for heating ventilator shafts are to 
he placed as shown on plan. 
CONNECTIONS, BRACKETS, AND HOOK PLATES 
At flow and return end of each coil are to be means of disconnection, either right and left 
couplings and nipples, or other approved methods. On the circulating pipes right and left couplings 
are to he used. 74 
TIIE NOVELTY CIRCULATOR. 
The 3-inch main flow pipe is to be supported on brackets of approved pattern from wall. 
Single 2-inch hook plates are to be used on the 2-inch flow and return mains and branches where nec- 
essary. Hook plates 4, 5, 6, and 8 pipes high are to be used on the coils, and the coil pipes are to be 
level and kept on the same vertical center line as the 2-inch pipe by the use, if necessary, of a neat 
wood filling piece to be supplied by contractor. All hook plates are to be screwed to the wood casing 
and partitions which will be provided for the purpose. 
FINISHING PLATES. 
Where the flow and return pipes pass through the office partitions, wall plates or casings at 
each side are to be provided; these arc to be for 2-inch and lf-inch pipes. 
HOLES IN WALLS. 
At B two holes for 2-inch flow and return pipes are to be cut and the same number at C and 
H through 16-inch walls. At B near ceiling a hole through main wall tor air pipe is to be cut, and 
near C in 8-inch wall in elevator shaft two holes for 2-inch pipes are to be cut. These holes when the 
pipes are in are to be neatly fitted up and finished at each side round the pipes. 
BLOW-OFF. 
Connection between main 4-inch return tee and waste pipe is to be made with f-incli pipe and 
f-incli gate valve. The waste pipe will have a 1-inch tec on it to receive blow-oft and it will be below 
the 4-incli main tee. (See Fig. 77.) 
OVERFLOW. 
The overflow of 1-inch pipe is also to be connected to tee on waste pipe and to 1-inch outlet 
on reducing elbow (2-inch to 1-inch) on bottom of expansion tank. (See Fig. 78.) 
EXPANSION TANK. 
The location of this tank is shown on plan by dotted lines, directly above heater. It is to be 
placed as near ceiling as possible. The main 6-inch x 3-inch flow pipes are to be at least 6 inches 
below it. It is to be fitted with a ball and cock which is to be connected to the water-supply pipe 
(f-inch) which is near the circulator. The tank is to have a 1-inch pipe overflow connected to waste 
as above described. The expansion pipe is to be connected to bottom of tank of If pipe to tee on 
4-inch main return pipe. To this expansion pipe the f-inch air pipe from 6-inch tee on main flowr is 
to be connected to the outlet of a horizontal If x If x f-inch tee, the position of this tee to be such as ABRAM COX STOVB COMPANY. 
75 
to cause tlie f-inch pipe to incline down from it to the |-incli elbow on nipple in 6-inch tee. From 
this tee (1| x 1J x|-inch) is to be a l]-inch elbow with IJ-incli pipe to elbow (1|) on bottom of tank. 
This pipe is to incline up to elbow on bottom of tank. (See Fig. 78.) 
The tank is to he of plate-iron or cast-iron, and bottom and top are to he properly stayed. The 
top is to have opening with cover of sufficient size to get at ball cock for repairs, etc. The joint of 
this cover to be tight. The joint of 1-inch air pipe to top of tank is also to he tight. The dimen- 
sions of the tank inside are 32 inches long by 30 inches wide. A height of 5 inches is necessary for 
expansion of water. To edge of vertical overflow pipe (2 inches) the height will be 6 inches and to 
under side of top of tank 7| inches, making the tank measure 32 inches long, 30 inches wide, and 
7J inches deep with a pocket or drop from bottom of tank 4J inches by 16 inches long by 8 inches 
wide for ball of supply cock, making the greatest depth of tank 12 inches. To the bottom of this 
drop or pocket the expansion pipe is to be connected and at the lower part of the pocket near the 
bottom and near the top of tank a water gauge with glass is to be fitted. In addition to the supply 
through ball cock in tank, there is to be a f-inch supply with gate valve already specified, through 
emptying pipe to 4-inch tee on return main pipe. (See Fig. 77.) Under this contract the expansion 
tank furnished with the pipes and fittings as described, is to be provided and placed in position with 
all requisite supports from wall to partition. 
PROTECTION FROM FIRE. 
Wood-work near pipes is to be protected in accordance with the rules and regulations which 
apply to steam pipes of the Fire Department and Board of Fire Underwriters of New York. 
MATERIALS AND WORKMANSHIP. 
All the materials described and referred to in this specification and the accompanying plan 
and details are to he supplied, placed in position, and left in complete working order. The entire 
apparatus is to he tested by the contractor, who is to make all joints tight. The workmanship is to 
be of the best kind, and all levels are to be accurately adhered to and carried out. Supply and Emission of Heat 
JOHN J. HOGAN. 
IN order to ascertain the number of square feet of surface in radiators or pipes required to heat a 
definite space or an apartment, some of the enclosing walls of which are exposed to the exterior 
atmosphere and have windows, it is necessary to know the cooling effect of such exposed 
surfaces. The quantity of heat required to warm incoming air, and the loss of heat through such 
surfaces, may be closely approximated through the assistance of tables and formulas here given. 
The quantity of air to be warmed can be definitely ascertained, and knowing its temperature, the 
quantity of heat needed to warm it the requisite number of degrees, is readily determined. 
The heat given off by each square foot of surface at certain temperatures under given 
conditions has been approximately determined by experiment. When these data are known it is 
not a difficult matter to ascertain the quantity of surface in radiators required for direct radiation. 
In deciding the surfaces required for indirect radiation, attention is necessary to other points, in 
addition to the loss of heat through glass and walls, the air to be warmed, and the heat given oft' by 
each square foot of surface. 
An examination of Table XII shows that the temperature which the incoming air has to 
acquire to provide for the loss of heat through glass, etc., is greater than is possible in hot-water 
circulation, if the quantity of incoming air is less than half the quantity of air cooled. Under such 
circumstances more air must be admitted at the lower temperature. To admit more air proper 
provision is necessary in the ventilating flues to allow the air to ascend freely from the radiators. 
This is especially desirable in well constructed and tightly finished buildings where there are no 
openings left near windows or doors through which the heated air may escape. Any one of the 
following tables or forms may be used to ascertain the quantity of surface required in direct or 
indirect radiation. It will be observed that forms 1, 2, and 3 give more definite results than forms 
4 and 5, which are mere approximations. 
From Table XII it is apparent that a square foot of indirect radiating surface does relativelv 
less heating than a square foot of direct radiating surface when the incoming air is less than the 
quantity ol the air cooled by glass and exposed wall. When the quantity of air passing over the 
surfaces of the indirect radiator is greatly in excess of the air cooled by the exposed walls and glass, 
the average temperature within the casing of an indirect radiator is low, and each square foot of 
* Copyrighted, 1892, by John J. Hogan. ABRAM COX STOVE COMPANY. 
surface does more effective beating than the same surface in a direct radiator. It is therefore 
evident, in designing an indirect beating apparatus, that particular care should be taken to provide a 
circulation of air through the indirect radiators. 
TABLE XII.—TEMPERATURES OF AIR IN CASINGS OF INDIRECT RADIATORS 
WHEN TEMPERATURE OF AIR IN ROOM IS 70° FAHR. AND TEMPERATURE 
OF EXTERNAL ATMOSPHERE IS ZERO* 
Proportion of 
incoming air to 
quantity of air 
cooled by glass and 
its equivalent. 
Temperature of 
air in casing at 
bottom of 
radiators. 
Temperature of 
incoming air in 
casing at top of 
radiators required 
to offset cooling 
effect of walls and 
windows. 
Internal tempera- 
ture of air in 
room. 
Total tempera- 
ture of air in 
casing at top of 
radiator required 
to offset cooling 
effect of walls and 
windows. 
Average tem- 
perature of air in 
casing. 
DEGREES FAHR. 
.25 
0 
280° 
+ 70° 
= 350° 
175° 
.5 
0 
140° 
+ 70° 
= 210° 
105° 
.75 
0 
93.3° 
+ 70° 
= 163.6° 
81.8° 
1. 
0 
70° 
+ 70° 
= 140° 
70° 
2. 
0 
35° 
+ 70° 
= 105° 
52.5° 
3. 
0 
23.3° 
+ 70° 
= 93.3° 
46.6° • 
4. 
0 
17.5° 
+ 70° 
= 87.5° 
43.75° 
5. 
0 
14° 
+ 70° 
= 84° 
42° 
6. 
0 
11.6° 
+ 70° 
= 81.6° 
40.8° 
7. 
0 
10° 
+ 70° 
= 80° 
40° 
8. 
0 
8.75° 
+ 70° 
= 78.75° 
39.37° 
9. 
0 
7.75° 
+ 70° 
= 77.75° 
38.87° 
10. 
0 
7° 
+ 70° 
= 77° 
38.5° 
For the purposes of this treatise, rules and directions for proportioning surfaces in radiators 
under various specified conditions may be arranged in five forms or propositions: (1) General For- 
mulae ; (2) Proportioning Surfaces in Radiators to Glass, Exposed Wall, and Cubic Contents of Apart- 
ments; (3) Surfaces required to Warm Incoming Air; (4) Proportioning Surfaces in Radiators to 
Cubic Contents of Apartments, and (5) Proportioning Surfaces in Radiators to Lineal Feet of 
Exposed Wall. 
♦Copyrighted, 1892, by John J. Hogan. 78 
THE NOVELTY CIRCULATOR. 
FORM i.—FORMULAE FOR PROPORTIONING RADIATING SURFACES* 
DEFINITIONS. 
Reference letter or 
constant. 
1. 
2. 
3. 
4. 
5. 
6. 
7. 
Square feet of glass and its equivalent in exposed wall 
Number of degrees of difference between outside and inside temperatures 
Cubic feet of air cooled per square foot of glass (1.279 per minute Hoodi per hour for each degree of difference in tem- 
perature between the inside and outside atmosphere 1.279 X 60 minutes 
Thermal capacity of one cubic foot of air at 0 = weight of one cubic foot of air at 0 or .0864 X specific heat of air or .238 
Loss of heat through glass and its equivalent in exposed wall in units of heat per hour 
Cubic feet of air to be warmed per hour 
Units of heat required to warm air per hour 
G. X D. X 76.74 X .02056= H. U. G. 
D. X .02056 XC. = H. U. A. 
= (1. 
= 1). 
= 76.74 
= .02056 
= 11. U. G. 
= C. 
= H. U. A. 
8. 
Degress of heat to be added to air in rooms in indirect heating to overcome cooling effect of glass and exposed wall .... 
d 
.02056 X C. 
= A. D. 
9. 
10. 
11. 
Inside temperature of room or apartment in degrees Fahr 
Total heat of incoming air in degrees Fahr 
A. D. + 1. T. = T. 11. 
Outside temperature 
= 1. T. 
= T. H. 
= 0. T. 
= A. T. 
12. 
Average temperature of air in degrees Fahr. within the casing of indirect radiators 
tp T. H.-f-O. T. . m tp u i T. H.— O.T. A 
If above zero = A. I. If below zero =-= A. I. 
13. 
14. 
15. 
= R. 
= 11. U. D. 
= H. U. S. 
Temperature of surface of radiators in degrees Fahr 
Heat units emitted per square foot of surface of radiator for each degree of difference between the temperature of 
the surface of radiator and the internal temperature of room or apartment (I. T.) for direct radiation or the 
average temperature of air within the casing (A. T.) for indirect radiation . 
Heat units emitted por square foot of surface of radiators per hour 
R.— I. T. X H. U. D.= H. U. S. for direct radiation. 
R. — A. T. X H. U. D. = H. U. S. for indirect radiation. 
16. 
H. U. Gr. + H. U. A. a I? o u t> 
=Square Feet of Surface Required iv Radiator. 
xl. IJ. te. 
17. 
For direct radiation H. U. D 
= 1.6 to 1.8. 
18. 
For indirect radiation when the quantity of air to be warmed does not exceed three times the quantity of air to be 
cooled by glass and exposed wall, H. U. D 
= 1.3 to 1.5. 
19. 
For indirect radiation when the quantity of air to be warmed exceeds three times the quantity of air cooled by glass 
and exposed wall, H. U. D. 
= 1.6 to 2.5. 
20. 
When the air is forced through radiators mechanically by means of fans, blowers, etc., H. U. D 
= 3 to 7. 
* Copyrighted, 1892, by John J. Hogan. ABRAM COX STOVE COMPANY. 
79 
FORM 2.—PROPORTIONING SURFACES IN RADIATORS TO GLASS, EXPOSED WALL, AND CUBIC 
CONTENTS OF APARTMENTS* 
Multiply the square feet of glass and its equivalent by 1.25 and the resulting product by 60. 
This gives the cubic feet of air cooled per hour by the glass. To this add the cubic feet of air to be 
warmed per hour, which may be the cubic contents of the room, multiplied by 1, 2, 3, or 4, depend- 
ing on the number of times it is proposed to change the air, and the result will be the total cubic feet 
of air to be warmed per hour. 
Multiply the total cubic feet of air to be warmed per hour by the units of heat required to 
raise 1 cubic foot of air to the required temperature, as given in Table XVI, and divide this product 
by the number of units of heat per square foot per hour emitted from radiators according to Table 
XIII. The result is the square feet of surface required in radiator. 
TABLE XIII—UNITS OF HEAT PER SQUARE FOOT OF SURFACE PER 
HOUR EMITTED IN DIRECT AND INDIRECT RADIATORS (APPROXI- 
MATE).! 
A. 
B. 
c. 
Average 
temperature 
of water 
in radiators 
in degrees Fahr. 
Units of heat emitted 
approximately per square 
foot per hour by direct 
radiators, the temperature 
of room being 70°. 
Units of heat emitted 
approximately per square 
foot per hour by indirect 
radiators to maintain 
incoming fresh air 
in room at 70°, when the 
quantity of air to be 
warmed does not exceed 
three times the quantity 
of air to be cooled by 
glass and exposed wall. 
Units of heat emitted 
approximately per square 
foot per hour by indirect 
radiators to maintain 
incoming fresh air 
in room at 70°, when the 
quantity of air exceeds 
three times the quantity 
of air to be cooled by 
glass and exposed wall. 
140° 
115° 
92 
174 
150° 
135° 
109 
198 
160° 
155° 
126 
222 
170° 
177° 
143 
247 
180° 
199° 
161 
274 
190° 
222° 
179 
301 
200° 
246° 
198 
330 
0 
O 
'M 
270° 
217 
418 
* Copyrighted, 1892, by John J. Hogan, 
t Copyrighted, 1892, by John J. Hogan. 80 
THE NOVELTY CIRCULATOR. 
FORM 3.—SURFACES REQUIRED TO WARM INCOMING AIR. 
The foregoing rule may he simplified as follows : The square feet of glass and its equivalent mul- 
tiplied by 75, (1.25 X 60) equals the number of cubic feet of air cooled by the glass and its equivalent in 
exposed wall per hour. To this product add the cubic feet of air to be warmed per hour and the sum 
is the total work to be done expressed in the number of cubic feet of air to be warmed per hour. The 
total number of cubic feet of air to be warmed per hour when multiplied by the multiplier in Table 
XIV opposite any desired temperature of water in the radiators, and in the column for direct or 
indirect radiation, gives as the product the required number of square feet of surfaces in radiators, 
when the external temperature is 0 Fahr. and the temperature of the apartment warmed 70° Fall. 
TABLE XIV.—MULTIPLIERS FOR ASCERTAINING SQUARE FEET 
OF SURFACE REQUIRED IN RADIATORS* 
External temperature 0 Fahr. 
Temperature in apartment 70° Fahr. 
Average 
temperature 
of 
j water in radiators 
in degrees 
Fahr. 
Indirect Radiation. 
Direct Radiation. 
When the quantity of air 
to be warmed does not 
exceed three times the 
quantity of air to be cooled 
by glass and exposed 
walls, the 
When the quantity of air 
to be warmed 
exceeds three times the 
quantity of air to be cooled 
by glass and exposed 
wall, the 
Square feet of surface in radiators = total number of cubic feet of air to be 
warmed, multiplied by, 
Multiplier A. 
Multiplier B. 
Multiplier C. 
140° 
.0123 
.0155 
.0082 
150° 
.0106 
.013 
.0072 
160° 
.0092 
.0114 
.0064 
170° 
.0081 
.01 
.0058 
O 
O 
00 
r—i 
.0072 
.009 
.0052 
190° 
.0064 
.008 
.0047 
200° 
.0068 
.0072 
.0043 
210° 
.0053 
.0066 
.0034 
For other temperatures, see Table XXI. 
♦Copyrighted, 1892, by John J. Hogan. ABRAM COX STOVE COMPANY. 
81 
FORM 4-—PROPORTIONING SURFACE IN RADIATORS TO CUBIC CONTENTS 
OF APARTMENTS. 
External temperature 0 Falir. 
Internal temperature 70° Fahr. 
Temperature of water in radiators 160° Falir. 
Description of Apartments 
Direct Radiation. 
Indirect Radiation. 
Warmed. 
One square foot of surface in radiators, heats. 
25 to 35 cubic feet. 
30 to 45 “ 
15 to 25 cubic feet. 
20 to 30 “ 
Dwelling apartments on second and upper 
floors 
Dwelling bath rooms 
15 to 25 “ 
10 to 20 “ 
Dwelling halls 
20 to 30 “ 
15 to 25 “ 
School rooms, offices, etc 
30 to 60 “ 
25 to 40 “ “ 
Factories, stores, etc 
45 to 70 “ 
25 to 40 “ “ 
Auditoriums, churches, etc 
80 to 100 “ 
50 to 80 “ 
RELATIVE COOLING EFFECT OF GLASS AND WALLS APPROXIMATELY STATED FOR 
PRACTICAL PURPOSES. 
One square foot of glass will cool 75 cubic feet of air one degree per hour for each degree of 
difference of temperature between the external and internal atmospheres. 
The cooling effect of 10 square feet of exposed wall, 8 to 12 inches in thickness, is equal to one 
square foot of glass. 
The cooling effect of 15 square feet of exposed wall, 14 to 26 inches in thickness, is equal to 
one square foot of glass. 
The cooling effect of 20 square feet of exposed wall, 28 to 38 inches in thickness, is equal to 
one square foot of glass. 
LOSS IN UNITS OF HEAT PER SQUARE FOOT OF GLASS PER HOUR FOR A DIFFERENCE OF 
i° BETWEEN THE EXTERNAL AND INTERNAL AIR.* 
Window glass, single 1.57 
Window glass, double 83 
Glass of large surface as in conservatories, greenhouses, etc 1.05 
* Copyrighted, 1892, by John J. Hogan. 82 
THE NOVELTY CIRCULATOR. 
FORM 5.—PROPORTIONING SURFACES IN RADIATORS TO LINEAL FEET OF EXPOSED WALL 
IN APARTMENTS.* 
EXTERNAL TEMPERATURE o FAHR. INTERNAL TEMPERATURE 70° FAHR. 
RULE FOR DIRECT RADIATION. 
Multiply the number of lineal feet of exposed wall by 7 for apartments having a height of 10 
feet or under, and to the product for every addition to the height of 2 feet or fraction thereof, add 
one (or fraction of one) and divide the sum by 3. The result will be the number of square feet of 
surface in radiator. 
a. For apartments with one wall exposed, or in which the exposed walls do not exceed two- 
fifths of all the surrounding walls, add one-fifth of the length of the exposed wall to the lineal feet and 
proceed as above stated. 
b. For entrance halls of rectangular form, multiply the width of the exposed wall or end by 
the height of the hall and by .9 and the result will be the number of square feet required in radiator. 
RULE FOR INDIRECT RADIATION. 
Multiply the number of lineal feet of exposed wall by 11 for apartments having a height of 10 
feet or under, and to the product for every addition to the height of 2 feet or a fraction thereof add 1, 
(or a fraction of 1) and divide the sum by 3. The result will be the square feet of surface for indirect 
radiation. 
a. For apartments with one wall exposed, or in which the exposed walls are less than two- 
fifths of all the surrounding walls, add one-fifth of the length of the exposed wall to the lineal feet, 
and proceed as above stated. 
b. For entrance halls of rectangular form, multiply the width of the exposed end by the 
height of the hall and by 1.4, and the result is the number of square feet of indirect radiating surface. 
TABLE XV.—MULTIPLIERS FOR ASCERTAINING THE SURFACES IN RADIATORS 
PER LINEAL FOOT OF EXPOSED WALL.f 
External temperature 0 Falir. 
Internal temperature 70° Falir. 
HEIGHT OF ROOMS. 
10 FT. 
12 FT. 
14 FT. 
16 FT. 
18 FT. 
20 FT. 
| Direct. 
Indirect. 
Direct. 
Indirect. 
Direct. 
; Indirect. 
Direct. 
i Indirect. 
Direct. 
1 Indirect. 
■ Direct. 
i Indirect. I 
7 
11 
8 
12 
9 
14 
10 
15 
11 
17 
28 
12 
18 
11 
17 
12 
18 
18 
20 
14 
21 
15 
16 
24 
For intermediate heights allow proportionately. For other differences of temperature, 
see Table XXI. 
* Copyrighted, 1890, by David Williams, 
t Copyrighted, 1890, by David Williams. ABRAM CO A' STOVE COMPANY. 
83 
TABLE XVI.—UNITS OF HEAT REQUIRED PER HOUR TO 
HEAT ONE CUBIC FOOT OF AIR AT DIFFERENT TEM- 
PERATURES. 
Temperature 
of 
external air. 
Temperature of air in room. 
50° 
60° 
70° 
80° 
90° 
Units of heat required per hour. 
0 degrees 
1.028 
1.234 
1.439 
1.645 
1.851 
10 
.805 
1.007 
1.208 
1.409 
1.611 
20 “ 
.59 
.787 
.984 
1.181 
1.378 
30 
.385 
.578 
.77 
.963 
1.155 
40 
.188 
.376 
.564 
.752 
.94 
TABLE XVII—LOSS IN UNITS OF HEAT PER 
SQUARE FOOT PER HOUR THROUGH EX- 
POSED WALL FOR A DIFFERENCE OF 
1° BETWEEN THE EXTERNAL AND IN- 
TERNAL AIR WHEN ALL SIDES OF 
ROOM ARE EXPOSED. 
TABLE XVIII.—LOSS IN UNITS OF HEAT 
PER SQUARE FOOT PER HOUR THROUGH 
EXPOSED WALL FOR A DIFFERENCE OF 
1° BETWEEN THE EXTERNAL AND IN- 
TERNAL AIR WHEN ONLY ONE WALL 
OF THE ROOM IS EXPOSED. 
Thickness of 
wall 
in inches. 
Brick. 
Thickness of 
wall 
in inches. 
Stone. 
41 
.231 
6 
.261 
9 
.191 
12 
.234 
14 
.159 
18 
.212 
18 
.14 
24 
.194 
27 
.111 
30 
.179 
36 
.092 
36 
.166 
Thickness of 
wall 
in inches. 
Brick. 
Thickness of 
wall 
in inches. 
Stone. 
4* 
.371 
6 
.453 
9 
.275 
12 
.379 
14 
.213 
18 
.324 
18 
.182 
24 
.284 
27 
.136 
30 
.257 
36 
.108 
36 
.228 84 
THE NOVELTY CIRCULATOR. 
TABLE XIX—SURFACES REQUIRED IN HEATING PIPES OR RADIATORS TO MAINTAIN 
VARIOUS TEMPERATURES IN CONSERVATORIES, THE EXTERNAL TEMPERATURE 
BEING 0 FAHR* 
Temperature of house in 
degrees Fahr. 
Units of heat lost per square foot 
of glass per hour. 
Units of heat required to heat one 
cubic foot of air per hour 
from 0 Fahr. 
Temperature of water in heating pipes. 
140° 
160° 
180° 
200° 
Ratio of heat 
units emitted 
per square 
foot of heat- 
ing surface 
in pipes, 
approxi- 
mated. 
Square feet 
of surface 
in heating 
pipes or 
radiators 
required per 
100 square feet 
of glass. 
Ratio of heat Square feet 
units emitted of surface 
per square in heating 
foot of heat- 1 pipes or 
ing surface radiators 
in pipes, required per 
approxi- 100 square feet 
mated. of glass. 
Ratio of heat 
units emitted 
per square 
foot of heat- 
ing surface 
in pipes, 
approxi- 
mated. 
Square feet 
of surface 
in heating 
pipes or 
radiators 
required per 
100 square feet 
of glass. 
Ratio of 
heat units 
emitted per 
square foot 
of heating 
surface in 
pipes, ap- 
proximated 
Square feet 
of surface 
in heating 
pipes or 
radiators 
required per 
100 square feet 
of glass. 
A. 
B. 
C. 
D. 
E. 
D. 
E. 
D. 
E. 
D. 
E. 
40 
44 
.822 
207 
23 
251 
19 
318 
15 
367 
13 
45 
47.25 
.925 
195 
27.5 
249 
21.5 
298 
18 
358 
15 
50 
52.5 
1.028 
183 
32.5 
234 
25.5 
284 
21 
341 
17.5 
55 
57.75 
1.130 
172 
38 
222 
29.5 
273 
24 
328 
20 
60 
63 
1.234 
157 
45.5 
207 
34.5 
251 
27.5 
318 
23 
65 
68.85 
1.336 
145 
53.5 
195 
39.5 
249 
31 
298 
26 
70 
73.5 
1.439 
132 
133 
183 
45.5 
234 
35.5 
284 
29 
75 
78.75 
1.542 
123 
72.5 
172 
52 
222 
40 
273 
32.5 
80 
84 
1.645 
111 
86 
157 
61 
207 
46 
251 
36.5 
85 
89.25 
1.747 
99 
102 
145 
70 
195 
52 
249 
40.5 
B = A X 1.05 average loss in units of heat per square foot of glass per hour for the difference of 1° Fahr. 
C = 0.238 specific heat of air X .0864 weight of 1 cubic foot of air at 0 in pounds X A, number of degrees difference between internal and external 
temperatures. 
D = approximated ratio of emission of heat in units from heating surfaces of pipes or radiators by contact of air per square foot per hour at various 
differences of temperatures. 
E = B— -jy-X 7) X 100. 
7 = proportion of space in cubic feet to 1 square foot of glass. When this proportion is increased to 8, add 4 per cent, to the surface in pipes, and when 
increased to 9 add 8 per cent, to the surface in pipes. 
When 4-inch pipe is used, add 7.5 per cent, to the actual surface obtained in the foregoing tables. 
•Copyrighted, 1892, by John J. Hogan. ABRAM COX STOVE COMPANY, 
85 
TABLE XX—GLASS SURFACE AND ITS 
EQUIVALENT, IN PROPORTION TO 
HEATING SURFACES IN PIPES, RE- 
QUIRED TO MAINTAIN VARIOUS 
TEMPERATURES IN CONSERVA- 
TORIES, EXTERNAL TEMPERATURE 
BEING 0 FAHR * 
TABLE XXI—RELATIVE PROPORTIONS OF SUR- 
FACES FOR DIFFERENT TEMPERATURES.! 
Temperature of 
external 
atmosphere. 
Temperature of air in rooms. 
Degrees Fahr. 
60° 
65° 
70° 
75° 
80° 
30° 
Falir. 
(above) 
.39 
.48 
.57 
.67 
.78 
25° 
44 
44 
.46 
.54 
.64 
.74 
.86 
20° 
44 
44 
.52 
.61 
.71 
.82 
.94 
15° 
u 
44 
.59 
.68 
.78 
.89 
1.02 
10° 
u 
44 
.65 
.75 
.85 
.97 
1.09 
5° 
u 
44 
.72 
.82 
.92 
1.04 
1.17 
0 
u 
44 
.78 
.88 
1. 
1.12 
1.25 
5° 
Fahr. 
(below) 
.85 
.95 
1.06 
1.19 
1.33 
10° 
44 
44 
.91 
1.02 
1.13 
1.26 
1.41 
15° 
44 
44 
.97 
1.09 
1.21 
1.34 
1.48 
20° 
44 
44 
1.04 
1.15 
1.28 
1.41 
1.56 
25° 
44 
44 
1.11 
1.22 
1.35 
1.49 
1.64 
30° 
44 
44 
1.17 
1.29 
1.42 
1.56 
1.71 
35° 
44 
44 
1.24 
1.36 
1.49 
1.64 
1.79 
40° 
44 
44 
1.30 
1.43 
1.56 
1.71 
1.88 
45° 
44 
44 
1.37 
1.5 
1.63 
1.79 
1.95 
50° 
44 
44 
1.43 
1.56 
1.7 
1.85 
2.03 
Temperature 
of 
air in house. 
Temperature of water in heating 
pipes. 
140° 160° 180° 200° 
Square feet of glass and its equiva- 
lent proportioned to one square 
foot of surface in heating 
pipes or radiators. 
40° 
4.33 
5.25 
6.66 7.69 
45° 
3.63 
4.65 
5.55 6.66 
50° 
3.07 
3.92 
4.76 5.71 
55° 
2.63 
3.39 
4.16 5. 
60° 
2.19 
2.89 
3.63 4.33 
65° 
1.86 
2.53 
3.22 3.84 
70° 
1.58 
2.19 
2.81 3.44 
75° 
1.37 
1.92 
2.5 3.07 
oo 
o 
o 
1.16 
1.63 
2.17 2.73 
00 
Cn 
0 
.99 
1.42 
1.92 2.46 
For other temperatures, see Table XXI 
NOTE TO TABLE XXI. 
When the quantity of surface required for zero external and 70° internal temperature is ascer- 
tained by any of the preceding rules, the surface necessary for other external temperatures varying 
from 30° above to 50° below zero and internal temperatures varying from 60° to 80° above can he 
ascertained by decreasing or increasing the surface in the proportion given in Table XXI, zero 
externally and 70° internally being unity. 
* Copyrighted, 1892, by John J. Hogan, 
t Copyrighted, 1891, by David Williams. 86 
THE NOVELTY CIRCULATOR. 
TABLE XXIL—WEIGHT OF DRY AIR. 
Fahr. 
Weight per 
cubic foot, 
pounds. 
Fahr. 
Weight per 
cubic foot, 
pounds. 
Fahr. 
Weight per 
cubic foot, 
pounds. 
Fahr. 
Weight per 
cubic foot, 
pounds. 
Fahr. 
Weight per 
cubic foot, 
pounds. 
0° 
.0864 
24° 
.0821 
48° 
.0782 
72° 
.0746 
142° 
.0659 
1° 
.0861 
25° 
.0819 
49° 
.078 
73° 
.0745 
152° 
.0649 
2° 
.086 
26° 
.0817 
50° 
.078 
74° 
.0743 
162° 
.0638 
3° 
.0858 
27° 
.0816 
51° 
.0776 
75° 
.0742 
172° 
.0628 
4° 
.0855 
28° 
.0814 
52° 
.0774 
76° 
.0741 
182° 
.0618 
5° 
.0853 
29° 
.0813 
53° 
.0773 
77° 
.0739 
192° 
.0609 
6° 
.0852 
30° 
.0812 
54° 
.0772 
78° 
.0738 
202° 
.06 
7° 
.085 
31° 
.0809 
55° 
.0771 
79° 
.0736 
212° 
.0595 
8° 
.0848 
32° 
.0807 
56° 
.0769 
80° 
.0735 
250° 
.0559 
9° 
.0846 
33° 
.0805 
57° 
.0767 
81° 
.0734 
300° 
.0522 
10° 
.0845 
34° 
.0804 
58° 
.0766 
82° 
.0733 
350° 
.049 
11° 
.0843 
35° 
.0802 
59° 
.0765 
83° 
.0731 
400° 
.0461 
12° 
.0842 
36° 
.0801 
60° 
.0763 
84° 
.073 
450° 
.0436 
13° 
.084 
37° 
.0799 
61° 
.0762 
85° 
.0728 
500° 
.0413 
14° 
.0838 
38° 
.0797 
62° 
.0761 
86° 
.0727 
600° 
.0376 
15° 
.0837 
39° 
.0796 
63° 
.0758 
87° 
.0725 
-a 
o 
o 
o 
.0338 
16° 
.0835 
40° 
.0794 
64° 
.0757 
88° 
.0724 
o 
O 
o 
00 
.0315 
17° 
.0833 
41° 
.0793 
65° 
.0756 
89° 
.0723 
900° 
.0292 
18° 
.0831 
42° 
.0791 
66° 
.0754 
90° 
.0721 
1000° 
.0268 
19° 
.083 
43° 
.0789 
67° 
.0752 
92° 
.072 
20° 
.0828 
44° 
.0788 
68° 
.0751 
102° 
.0707 
21° 
.0826 
45° 
.0786 
69° 
.075 
112° 
.0694 
22° 
.0824 
46° 
.0784 
70° 
.0748 
122° 
.0684 
23° 
.0822 
47° 
.0783 
71° 
.0747 
132° 
.0671 
TABLE XXIII-VOLUME OF AIR AT VARIOUS TEMPERATURES. 
Fahr. 
Volume. 
Fahr. 
Volume. 
Fahr. 
Volume- 
Fahr. 
Volume. 
0° 
.933 
55° 
1.047 
130° 
1.204 
240° 
1.433 
5° 
.943 
60° 
1.058 
140° 
1.224 
250° 
1.453 
10° 
.954 
65° 
1.068 
150° 
1.245 
275° 
1.505 
15° 
.964 
70° 
1.079 
160° 
1.266 
300° 
1.558 
o 
O 
CM 
.975 
75° 
1.089 
170° 
1.287 
350° 
1.662 
25° 
.985 
80° 
1.099 
180° 
1.308 
400° 
1.765 
30° 
.996 
85° 
1.11 
190° 
1.329 
450° 
1.87 
32° 
1. 
90° 
1.121 
200° 
1.349 
500° 
1.974 
35° 
1.006 
95° 
1.131 
210° 
1.37 
550° 
2.078 
o 
o 
1.0113 
100° 
1.141 
212° 
1.374 
600° 
2.183 
45° 
1.027 
110° 
1.162 
220° 
1.391 
700° 
2.391 
50° 
1.037 
120° 
1.183 
230° 
1.412 
1000° 
3.016 Flow and Return Pipes 
50 proportion pipe areas to radiating surface the use of multipliers is convenient. When 
the surface to be supplied exceeds 2500 feet, multiply the number of square feet by .01 
for indirect radiation, and by .008 for direct radiation, and the product gives the approxi- 
mate area of pipe in square inches. The actual size of the pipe will be the pipe which has the area 
nearest to that found by the calculation. 
TABLE XXIV.—SIZES OF FLOW AND RETURN PIPES APPROXIMATELY PROPORTIONED TO 
SURFACE IN RADIATORS.* 
Size of pipe. 
Nominal 
diameter, 
inches. 
Mains. 
Branches and Risers. 
Square feet of surface 
in indirect radiators 
in cellar or basement. 
Square feet of surface 
in direct radiators 
on one or more floors. 
Average. 
Square feet of 
surface in radiators 
on first floor, or 10 ft. 
to 15 ft. above level 
of fire in circulator. 
Square feet of 
surface in radiators 
on second floor, or 15 
ft. to 25 ft.above level 
of lire in circulator. 
Square feet of 
surface in radiators 
on third floor, or 25 ft. 
to 35 ft. above level 
of fire in circulator. 
Square feet of 
surface in radiators 
on fourth floor, or 35 
ft. to45ft. above level 
of lire in circulator. 
1 
40 
45 
50 
1 
50 
75 
80 
85 
n 
100 
135 
110 
120 
135 
150 
it 
135 
220 
180 
195 
210 
230 
2 
225 
350 
290 
320 
350 
370 
2* 
320 
460 
400 
490 
525 
550 
3 
500 
675 
620 
650 
690 
730 
3| 
650 
850 
820 
870 
920 
970 
4 
850 
1100 
1050 
1120 
1185 
1250 
4J 
1050 
1350 
1325 
1400 
1485 
1560 
5 
1350 
1700 
6 
2900 
3600 
7 
3900 
4800 
8 
5000 
6200 
9 
6300 
7700 
10 
7900 
9800 
11 
9500 
11800 
12 
11400 
14000 
♦Copyrighted, 1892, by John J, Hogan, 88 
THE NOVELTY CIRCULATOR. 
P'K- 79*—Diagram of Vertical Lines of Pipe Proportioned to Obtain Uniform Temperatures. ABRAM COX STOVE COMPANY. 
89 
When the surface to be supplied does not exceed 2500 feet, multiply the number of square 
feet by .015 for indirect radiation, and by .011 for direct radiation, and the product gives the 
approximate area of pipe in square inches. The size of pipe to be used will be that having area 
nearest to the figures given by the calculation. These rules are applicable where 2-inch and larger 
pipes are used. 
In Fig. 79 are diagrams of vertical lines of pipes proportioned to the surfaces in radiators 
from TableXXIV. The object of these proportions is to attain as uniform a temperature as possible 
in all radiators on all floors at the same time. The use of reducing fittings is illustrated in these 
diagrams. It is generally more desirable to supply the circulation to radiators on the first floor 
direct from the horizontal main pipe in cellar, as shown in “Line B,” than from the lower part 
of the vertical line, as shown in “Line A.” By maintaining the side opening at the same area as 
the “run” the velocity of the current is diminished at the moment a change in direction takes 
place, on account of the increased space within the fitting. To accomplish this, reducing couplings 
and reducings elbows are used. 
To ascertain the actual and exact size of tlie expansion tank, the internal cubic capacity, or 
capacity in gallons, of all the pipes, radiators, coils, and boiler in the apparatus has to he determined. 
If the water in the system is raised to a temperature of 212° Fahr., its volume will he increased by 
2-tj, or 4|- per cent, of its bulk; and this is the least space that may be provided. In practice, the actual 
size of the expansion tanks is much larger, as when the system is tilled there are generally several 
inches of water in the tank, so that its level is noticeable in the glass water-gauge. Above this 
level, space for the expansion of the heater water is provided, and it is desirable that some height 
be added, so that the overflow pipe and air pipe may be connected to the expansion tank in such 
manner that the greatest increase of volume in the water will not cause overflow into either of these 
pipes. The actual size of the expansion tank may therefore be from 6 per cent, to 8 per cent, of the 
internal capacity of the entire apparatus. 
The calculation of the internal capacity of the pipes, radiators, coils, and circulator will be 
assisted by the use of the table (XL1I), which gives the capacity of pipes. The length of the pipes 
is to be taken from center to center of fittings, and 5 per cent, added to provide for the larger 
internal diameter of elbows, tees, and couplings. The internal capacity of radiators varies. Some 
are equal to 1-inch pipe, others to and lj-inch pipe per square foot of surface. To the capacity 
of these two items is to be added the capacity of the circulator. In order to dispense with the 
calculations just described, the use of the multipliers is suggested as a ready means of obtaining 
sizes of expansion tanks. (See Table XXY.) 
EXPANSION TANKS 90 
THE NOVELTY CIRCULATOR. 
TABLE XXV—PROPORTIONING EXPANSION TANKS* 
A.—To ascertain required capacity of 
expansion tank in gallons. 
B.—To ascertain required capacity of 
expansion tank in cubic inches. 
For heating 
apparatus 
having less 
than 1000 
square feet of 
surface in 
radiators. 
For heating 
apparatus 
having from 
1000 to 2000 
square feet of 
surface in 
radiators. 
For heating 
apparatus 
having over 
2000 square 
feet of surface 
in radiators. 
For heating 
apparatus 
having less 
than 1000 
square feet of 
surface in 
radiators. 
For heating 
apparatus 
having from 
1000 to 2000 
square feet of 
surface in 
radiators. 
For heating 
apparatus 
having over 
2000 square 
feet of surface 
in radiators. 
Multiply the 
sq uare feet of 
surface in 
radiators by 
.03 
.025 
.02 
Multiply the 
square feet of 
surface in 
radiators by 
7. 
5.75 
4.5 
TABLE XXVI—SIZES OF EXPANSION TANKS PRO- 
PORTIONED TO SURFACES IN RADIATORS.f 
Surface in radiators. 
Capacity of tank 
(approximate). 
Capacity of tank 
(approximate). 
225 
square 
feet. 
7 
gallons. 
1575 cubic inches. 
320 
44 
44 
10 
44 
2240 
4 4 4 4 
475 
44 
44 
15 
44 
3500 
4 4 4 4 
675 
44 
44 
20 
44 
4725 
4 4 4 4 
<350 
44 
4 4 
26 
44 
6050 
4 4 4 4 
1100 
44 
44 
28 
44 
6325 
4 4 4 4 
1350 
44 
44 
34 
44 
7763 
4 4 4 4 
1900 
44 
44 
48 
44 
10925 
4 4 4 4 
2600 
44 
44 
52 
44 
11700 
4 4 4 4 
3800 
44 
U 
76 
44 
17100 
a a 
5000 
a 
44 
100 
44 
22500 
a a 
6500 
44 
44 
130 
44 
29250 
a a 
8000 
<< 
a 
160 
44 
36000 
u a 
9500 
44 
44 
190 
44 
42750 
a u 
11500 
44 
44 
230 
44 
51750 
4 4 4 4 
— 
— 
u- 
— 
TABLE XXVII—INCREASE IN 
VOLUME OF WATER AT 
VARIOUS TEMPERATURES. 
1 ncrea.se of Percentage 
temperature of water of increase in 
from volume. 
Proportion 
of increase in 
volume. 
39° to 100° 
.0068 
1-148 
39° “ 110° 
.0089 
1-112 
39° “ 120° 
.0114 
1-88 
39° “ 140° 
.0166 
1-60 
39° “ 160° 
.0231 
1-43 
39° “ 180° 
.0303 
1-33 
39° “ 200° 
.0382 
1-26 
39° “ 212° 
.044 
1-23 
♦Copyrighted, 1892, by John J. Hogan. 
+ Copyrighted, 1892, by John J. Hogan. Air 
FOIi each Fahrenheit degree of change in its temperature air expands or contracts * or 
.002088 of its volume. 
faking o2 f alir. as unity and multiplying the number of degrees below or above this 
tcmpeiature by .002088, the result is the contraction or expansion, as the case may be, of the 
volume of air. The volume of air at 32° Fahr. is 7 per cent, greater than at 0 Fahr., at 70° 15 per 
cent, greater than at 0 Falir., and at 120° 20 per cent, greater than at 0 Fahr. 
At 0° Fahr. 11.574 cubic feet of air weighs 1 pound. 
At 32° “ 12.39 “ “ “ « 
At 62° “ 13.14 
At 70° “ 13.35' “ “ “ « 
At 120° “ 14.66 “ “ 
At 0 Fahr. .02056 unit of heat will raise one cubic foot of air one degree in temperature. 
From this we derive the following: 
.02056 X 70° = 1.439 units required to heat one cubic foot of air from 0 to 70°. 
.02056 X 65° = 1.336 units required to heat one cubic foot of air from 5 to 70°. 
.02056 X 60° = 1.233 units required to heat one cubic foot of air from 10 to 70°. 
Specific gravity of water = 1. 
Specific gravity of air= .001293 under one atmosphere. 
Volume of water = 1. 
Volume of the same weight of air at 32° = 773.283. 
AIR REQUIRED FOR VENTILATION. 
Each adult requires from 250 to 300 cubic feet of air per hour in sparsely occupied rooms. In 
theaters, assembly rooms, churches, etc., provision should be made to admit from 400 to 1500 cubic 
feet of air per hour for each person, and where prolonged sittings take place this quantity should 
be increased to 2000 cubic feet per hour per person. In school rooms children should be provided 
with 600 cubic feet and grown persons 1200 cubic feet of air per hour, unless the space is crowded, 
and then the quantity should be increased. In enforcing the Massachusetts law the chief of the 
district police requires 30 cubic feet of fresh air per minute for each pupil, or 1800 cubic feet per 92 
THE NOVELTY CIRCULATOR. 
hour. This requirement represents the most advanced American practice. From 2000 to 3000 
cubic feet of air per hour per occupant is required in hospitals and workshops. Each cubic foot of 
gas burned for illumination will consume from 8 to 12 cubic feet of air per hour. 
In indirect radiation in dwellings the air in the rooms should be changed at least twice every 
hour. Less frequent changes may be provided in halls and other buildings, dependent of course on 
the quantity of air required for ventilating purposes. By dividing this latter quantity by the cubic 
contents in feet in the apartment, the number of times the air is to be changed each hour is ascer- 
tained. Thus : 
. . . . , | . Cubic feet of air per hour required for ventilation. 
Xumber of times air is to be changed per hour = mr-—?—z—2?— —---a— 
0 r Cubic feet of contents of apartment. 
ASCERTAINING THE AREA OF WARM-AIR FLUES. 
To ascertain the area of warm-air flues in square inches when the velocity of air in flue in feet 
per second is known, multiply the contents of the room in cubic feet by the number in the column, 
which gives the required number of changes of air in Table XXVIII. 
TABLE XXVIII-WARM-AIR FLUES.* 
Velocity 
in flue in 
feet per 
second. 
One change 
of air 
per hour. 
Two 
changes 
of air 
per hour. 
Three 
changes 
of air 
per hour. 
Four 
changes 
of air 
per hour. 
Five 
chnnges 
of air 
per hour. 
1* 
feet. 
.0266 
.053 
.079 
.106 
.133 
2 
« 
.02 
.04 
.06 
.08 
.1 
2* 
U 
.016 
.032 
.048 
.064 
.08 
3 
U 
.0133 
.0266 
.0399 
.053 
.066 
81 
u 
.0114 
.0228 
.0342 
.0457 
.057 
4 
u 
.01 
.02 
.03 
.04 
.05 
4* 
u : 
.0089 
.0178 
.0267 
.0346 
.0445 
5 
u ; 
.008 
.016 
.024 
.032 
.04 
H 
u { 
.0073 
.0146 
.0219 
.029 
.0365 
6 
a 
.0066 
.0133 
.0198 
.026 
.033 
6J 
u 
.0061 
.0122 
.0183 
.0244 
.03 
7 
U 1 
.0057 
.0114 
.0171 
.0228 
.028 
7i 
U I 
.0053 
.0106 
.0159 
.0212 
.26 
10 
a 
.004 
.008 
.012 
.016 
.02 
* Copyrighted, 1892, by John J. Hogan. ABRAM COX STOVE COMPANY. 
The velocity ot the air in main vertical ventilating Hues should not be less than 6 feet per 
second. 
The velocity in horizontal exit ducts from apartments to main ventilating tine should not 
exceed 3 feet per second. 
The velocity of the incoming air at registers should not exceed 3 feet per second, and if 
the velocity in Hue exceeds this it may be reduced at the register by enlarging area of register beyond 
that of Hue. 
In a dwelling room the air may be moved with the temperature at 60° to 70°, at a velocity of 
2\ to 3| feet per second. It should not be permitted to exceed a velocity of 5 feet per second. 
In proportioning warm-air hues for dwellings the velocity to first floor may be estimated at 1J 
feet per second, to second floor 2| feet per second, and to the upper floors at 4 feet per second. 
The areas of fresh or cold-air inlet hues or ducts are equal to the areas of the warm-air hues 
or ducts multiplied by .75. 
TABLE XXIX—DIMENSIONS OF REGISTERS FOR 
WARM-AIR AND VENTILATING DUCTS. 
Size of 
opening. 
Inches. 
Nominal area 
of opening. 
Square 
inches. 
Effective area 
of opening. 
Square 
Inches. 
Opening to 
admit body of 
register. 
Inches. 
Extreme 
dimensions of 
register face. 
Inches. 
6x10 
“* 
60 
40 
6| X 10 
7|xl2 
8x10 
80 
53 
8 x 10 
9f x Ilf 
8x12 
96 
64 
8 x 12 
9f x 13f 
8x15 
120 
80 
8 x 15 
9f x 16f 
9x 12 
108 
72 
9 xl2i 
lOf xl3f 
9 x 14 
126 
84 
9 x 14 
11 x 16 
10 x 12 
120 
80 
10 x 12 
Ilfx13i 
10 x 14 
140 
93 
lOJxWi 
12f x16^ 
10x16 
160 
107 
I 10 x16 
12 x 18 
12x15 
180 
120 
12^x151 
13ixl6f 
12 x 19 
228 
152 
12£x 19± 
14f x 21 
14 x 22 
308 
205 
14± x 22 
16ix 24i 
15 x 25 
375 
250 
15fx 25i 
17|x 27f 
16x20 
320 
213 
16^x20| 
17|x 22* 
16x24 
384 
256 
16fx 24i 
18f x 27 
20x20 
400 
267 
20£ x 20£ 
22f x 22f 
20 x 24 
480 
320 
20 x 24 
22f x 26 
20x26 
520 
347 
20ix 26£ 
22|x28^ 
21 x 29 
609 
403 
20| x 29 
23f x31i 
27 x 27 
729 
486 
27 x 27 
29ix 29i 
27x38 
1026 
684 
27 x 38 
29fx 40f 
30x30 
900 
600* 
30f x 30f 
32f x 32f 94 
THE NOVELTY CIRCULATOR. 
PROPORTIONING AREAS OF WARM-AIR FLUES TO SQUARE FEET OF SURFACE IN 
INDIRECT RADIATORS. 
Proportions sometimes used in practice are as follows: 
For each square foot of surface in indirect radiator 2 square inches in warm-air Hue to first floor. 
For each square foot of surface in indirect radiator square inches in warm-air Hue to second 
floor. 
For each square foot of surface in indirect radiator 1 square inch in warm-air Hue to third and 
other Hoors. 
Cold-air ducts have one-quarter less area in square inches than warm-air flues. 
VENTILATING FLUES AND CHIMNEYS. 
The following rules for ascertaining the velocity of air currents at various temperatures in 
ventilating Hues and chimneys will he found useful: 
If the height of a chimney in feet he multiplied by 43 and divided by 480, the result will he 
the constant A which appears in Table XXX. 
Height in fe6t X 43 = Constant A. 
4oU 
In this equation 43 equals the accelerating force of gravity (32.2 feet per second) multiplied by 
2 and divided by the coefficient of friction .5 plus 1, thus : 
32.2 X 2 _64.4_ 
.5 + 1 1.5 
The square root of the product of the difference in degrees of temperature between the inside 
and outside atmosphere multiplied by A (as given in Table XXX) equals the velocity of draft in Hue 
in feet per second, thus: 
VTHfference in degrees of temperature X A = the velocity of draft in feet per second. 
TABLE XXX—THE CONSTANT “A” IN VENTILATING FLUES AND CHIMNEYS.* 
Height of chimneys in feet. 
30 
35 
40 
45 50 
55 
60 
65 70 
75 80 90 100 110 120 
130 
140 
Constant “A.” 
2.687 
3.134 
3.582 
4.031 
4.472 
4.923 
5.375 
5.822 
6.269 
6.716 
7.164 
8,062 
8.956 
9.847 
10.750 
11.610 
12.513 
♦Copyrighted, 1892, by John J. Hogan. ABRAM COX STOVE COMPANY. 
Again, the velocity in feet per second squared and’ divided by A (as given in the table) equals 
the difference in temperature in degrees between the inside atmosphere and the outside atmosphere 
necessary to maintain the velocity, thus: 
Velocity in feet per second2 ,.rt, . . 
= ditterence in temperature in degrees. 
The following formula is also of frequent use: 
Cubic feet of air discharged per second „ _ 
—=f^i——t— ■ ■ , — area ot flue in square feet. 
V elocity m teet per second. 
TABLE XXXI.—SIZES OF SMOKE FLUES IN CHIMNEYS FOR HOT-WATER HEATING SYSTEMS* 
Diameter 
in inches. 
Area in 
square inches. 
Area in 
square 
feet. 
Square of 
approxi- 
mate area, 
in inches. 
50 FT. 
HEIGHT OF CHIMNEY. 
60 FT. 70 FT. 80 FT. 
Surface in radiators in square feet. 
90 FT. 
Contents of building to be heated 
in cubic feet. 
9 
63.6 
.44 
8x8 
800 
1000 
up to 
40,000 
12 
113. 
.79 
11x11 
1200 
1400 
1600 
40,000 to 
60,000 
15 
176.7 
1.23 
14x14 
1800 
2200 
2600 
60,000 to 
100,000 
18 
254.4 
1.78 
16x16 
3000 
3400 
3800 
100,000 to 
150,000 
21 
346.3 
2.4 
19x19 
4200 
4600 
5000 
150,000 to 
300,000 
24 
452.3 
3.14 
22x22 
6000 
6500 
7000 
7500 
200,000 to 
450,000 
27 
572.5 
3.97 
24x24 
8000 
8500 
9000 
10000 
300,000 to 
600,000 
30 
706.8 
4.9 
27x27 
10000 
11000 
12000 
13000 
14000 
400,000 to 
800,000 
33 
855.3 
5.93 
30x30 
14000 
15000 
16000 
17000 
500,000 to 1,000,000 
30 
1017.8 
7.06 
32x32 
17000 
18000 
19000 
20000 
600,000 to 1,250,000 
* Oopyrighted, 1892, by John J. Hogan. 
No flue, whether for fresh air, warm air, foul air, or smoke should be less than 32 square inches 
in area. Heat 
SHE quantity of heat which it is necessary to impart to 1 pound of water at 32° Fahr., to 
raise its temperature 1°, is sufficient to raise 769 pounds 1 foot high in 1 minute. This is 
termed the mechanical equivalent of heat. 
A unit of temperature is 1° Fahr., or yly part of distance between freezing point, 32,° and 
boiling point, 212°, on Fahrenheit scale. 
A unit of heat (British thermal unit) is the quantity of heat required to raise 1 pound of water 
1° Fahr. in temperature. 
A French calorie, or unit of heat, is the quantity of heat required to raise 1 kilogramme 
(2.204 pounds) of water 1° centigrade (1.8° Fahr.) in temperature. 
A French unit of heat is equal to 3.96832 British units. 
Degrees Fahr. equal degrees centigrade, multiplied by 9 and divided by 5, plus 32, thus: 
Degrees Fahr. = Degrees Cent. X 9 
5 + 
Degrees Cent, equal degrees Fahr., less 32 multipled by 5 and divided by 9, thus 
J Decrees Fahr. — 32 X 5 
Degrees Cent. = —5 
Degrees Cent. X 1.8 + 32 = Degrees Fahr. 
Degrees Fahr. — 32 1.8 = Degrees Cent. 
The melting point of ice is 32° Fahr. and 0° Cent. 
The boiling point of water is 212° Fahr. and 100° Cent 
The specific heat of a body is its capacity for heat, or the quantity of heat required to raise 
the temperature of the body 1° Fahr., compared with that required to raise the temperature of a 
quantity of water of equal weight 1°. The unit of heat (B. T. U.) is that which is required to raise 
the temperature of 1 pound of water 1° from 32° to 33° Fahr., and the specific heat of another body 
is expressed by the quantity of heat, in units, necessary to raise the temperature of 1 pound weight 
of such body 1°. 
The specific gravity of solids and liquids and of gases and vapors is their relative weight or 
density, water being taken as unity, at atmospheric pressure, and a certain temperature, say 62°, 
as in Table XXXII. 
It will be noticed in Table XXXII that the specific heat of water increases with the 
temperature. The increase being so little, 1T37 per cent, at 212°, it is usual to consider the specific 
heat uniform at all ordinary temperatures for practical purposes. ABRAM COX STOVE COMPANY. 
Specific heat. 
Specific gravity. 
One cubic foot. 
Weight in pounds. 
One cubic inch. 
Weight in pounds. 
AVater at 30° Fahr 
1. 
.9999 
62.38 
.03610485 
Water at 39° Fahr 
1. 
1. 
62.39 
.03610842 
Water at 62° Fahr 
1.0004 
1. 
62.32 
.03606 
Water at 212° Fahr 
1.013 
.9585 
59.76 
.03461322 
Ice at 32° Fahr 
.504 
.93 
57.96 
.03354 
Cast-iron 
.1298 
7.087 
441.6 
.2556 
Wrought-iron 
.11379 
7.788 
485.3 
.2809 
.0955 
6.861 
427.6 
.2474 
Copper 
.0951 
8.607 
536.4 
.3104 
Tin 
.0569 
7.291 
454.4 
.263 
.0314 
11.352 
707.3 
.4094 
Pine wood 
.65 
.483 
30.1 
.01742 
Oak wood 
.57 
.777 
48.42 
.02802 
.19768 
2.76 
172. 
.0995 
Burnt clay or brick 
.185 
1.841 
114. 
.0664 
Air at 62° Fahr 
.238 
.001293 
.0761 
Vapor of water (steam) 
Steam at 212° Fahr 
.475 
.000805 
.000621 
.0475 
Cubic feet of air at 62° Fahr. in 1 pound. =13.14. 
TABLE XXXII—SPECIFIC HEAT AND SPECIFIC GRAVITY. 
Water with perfect freedom of motion is the best absorbent of heat, excepting mercury. 
The effects of heat may be summarized: 
Water boils (under atmospheric pressure, 14.7 pounds absolute) at 212° Falir. 
Mercury “ “ “ “ at 676° u 
Sulphur “ “ “ “ “ 838° “ 
Cast-iron melts (maximum) at 2786° “ 
“ “ (minimum) “ 1920° “ 
Wrought-iron melts (maximum) at 3945° “ 
“ “ (minimum) “ ...: 2730° “ 
Zinc melts at 773° “ 
Copper melts at 1996° “ 
Tin “ “ 442° “ 
Lead “ “ 612° “ 
Iron red-hot in daylight at 1272° “ 
“ “ in the dark 800° “ 98 
THE NOVELTY CIRCULATOR. 
Lowest luminosity of iron in the dark at 635° Fahr. 
Steel becomes dark blue at 600° 
Steel “ purple at 530° 
Steel “ brown at 490° “ 
Steel “ faint yellow at 430° 
Water freezes at 32° “ 
Sea-water freezes at 28° 
Heat of a common fire 790° 
TABLE XXXIII.—EXPANSION OF BODIES BY HEAT. 
EXPANSION 
FOR 1° FAHR. 
In length. 
In volume. 
Water 40° to 212° 
.0002519 
Ice—17° to + 30 
.0000843 
.000253 
Cast-iron 
.000006167 
.000018501 
Wrouglit-iron 
.000006689 
.000020067 
Zinc 
.000017268 
.000051806 
Copper 
.000010088 
.000030264 
Tin 
.000013102 
.000039307 
Lead 
.000015876 
.000047628 
Brick 
.000003057 
.00000917 
The use of Table XXXIII is simple. For example, the temperature of a wrought-iron pipe is 
increased 200° above the temperature at which it was when placed in position, and its length is 120 
feet. Then 120 X 12 = 1440 inches X .000006689 (found in column opposite wrought-iron) = .00963 
X 200° increase of temperature = 1.926, or nearly 2 inches is the additional length to the pipe when 
heated. 
A system of heating contains 1000 gallons of water at 40° Falir., and is to be heated to 
200°. The form by which to ascertain the increase in volume of water at the high temperature is 
1000 X .0002519 = .2519 X (200 — 40) 160° = 40.3 gallons. 
TRANSMISSION OF HEAT. 
Heat is transmitted by radiation, by contact of air, and by conduction. From the heating 
pipes or radiator heat is transmitted by radiation to the walls, floors, ceiling, furniture, and other solid 
bodies which have surfaces of a lower temperature than the temperature of the pipes or radiator. ABRAM COX STOVE COMPANY. 
From the heating pipes or radiators heat is transmitted to the air by contact, if the air is of a lesser 
temperature than that of the surfaces of the pipes or radiators. From the water within the heating 
pipes or radiators heat is transmitted by conduction to the external surfaces of the metal forming the 
heating pipes or radiators. The heat transmitted to the walls and ceilings by radiation is lost through 
them by conduction, when the temperature of the sides of the walls or ceilings affected by radiation 
is greater than the temperature of the outer side of the walls or ceilings. 
The heat transmitted to the surfaces of furniture and other bodies by radiation is absorbed by 
conduction until their surfaces have attained a higher temperature than the air when these surfaces 
transmit heat to the air by contact and to the walls, if of a lower temperature, by radiation. The 
power of the air to absorb heat by contact with heated surfaces is owing principally to the extreme 
mobility of its particles, the disturbed condition of the air when in contact with these surfaces, and 
the rapidity of its motion over the heated surfaces. Air without motion absorbs and conducts heat 
slowly. Air cannot be appreeiabl}7 heated directly by radiant heat, but only by contact with heated 
bodies. When the heating pipes or radiators are enclosed, as in the case of indirect radiators, the 
walls of the case being approximately of the same temperature as the heating surfaces, heat is given 
off by contact only to the air passing through. The radiating and heat-absorbing powers of bodies 
are equal. The reflective power is inversely as the radiating power. 100 
THE NOVELTY Cl 11 CULATOII. 
TABLE XXXIV—HEAT UNITS IN WATER AND WEIGHT OF WATER IN POUNDS 
PER CUBIC FOOT. 
Temperature 
Fahr. 
Heat units 
per pound. 
Weight, 
pounds per 
cubic foot. 
Tempera- 
ture 
Fahr. 
Heat units 
per pound. 
Weight, 
pounds per 
cubic foot. 
Tempera- 
ture 
Fahr. 
Heat units 
per pound 
W eight, 
pounds 
per cubic 
foot. 
Tempera- 
ture 
Fahr. 
Heat units 
per pound. 
AVeight, 
pounds 
per cubic 
foot. 
32° 
0. 
62.38 
110° 
78.11 
61.89 
145° 
113.28 
61.28 
179° 
147.53 
60.57 
35° 
3. 
62.42 
112° 
80.12 
61.86 
146° 
114.28 
61.26 
180° 
148.54 
60.55 
40° 
8. 
62.42 
113° 
81.12 
61.84 
147° 
115.29 
61.24 
181° 
149.55 
60.53 
45° 
13. 
62.42 
114° 
82.13 
61.83 
148° 
116.29 
61.22 
182° 
150.56 
60.50 
50° 
18. 
62.41 
115° 
83.13 
61.82 
149° 
117.30 
61.20 
183° 
151.57 
60.48 
52° 
20. 
62.40 
116° 
84.13 
61.80 
150° 
118.31 
61.18 
184° 
152.58 
60.16 
54° 
22.01 
62.40 
117° 
85.14 
61.78 
151° 
119.31 
61.16 
185° 
153.59 
60.44 
56° 
24.01 
62.39 
118° 
86.14 
61.77 
152° 
120.32 
61.14 
186° 
154.60 
60.41 
58° 
26.01 
63.38 
119° 
87.15 
61.75 
153° 
121.33 
61.12 
187° 
155.61 
60.39. 
60° 
28.01 
62.37 
120° 
88.15 
61.74 
154° 
122.33 
61.10 
188° 
156 62 
60.37 
62° 
30.01 
62.36 
121° 
89.15 
61.72 
155° 
123.34 
61.08 
189° 
157.63 
60.34 
64° 
32.01 
62.35 
122° 
90.16 
61.70 
156° 
124.35 
61.06 
190° 
158.64 
60.32 
66° 
34.02 
62.34 
123° 
91.16 
61.68 
157° 
125.35 
61.04 
191° 
159.65 
60.29 
68° 
36.02 
62.33 
124° 
92.17 
61.67 
158° 
126.36 
61.02 
192° 
160.67 
60.27 
70° 
38.02 
62.31 
125° 
93.17 
61.65 
159° 
127.37 
61. 
193° 
161.68 
60.25 
72° 
40.02 
62.30 
126° 
94.17 
61.63 
160° 
128.37 
60.98 
194° 
162.69 
60.22 
74° 
42.02 
62.28 
127° 
95.18 
61.61 
161° 
129.38 
60.96 
195° 
163.70 
60.20 
76° 
44.03 
62.27 
128° 
96.18 
61.60 
162° 
130.39 
60.94 
196° 
164.71 
60.17 
78° 
46.03 
62.25 
129° 
97.19 
61.58 
163° 
131.40 
60.92 
197° 
165.72 
60.15 
80° 
48.04 
62.23 
130° 
98.19 
61.56 
164° 
132.41 
60.90 
198° 
166.73 
60.12 
82° 
50.04 
62.21 
131° 
99.20 
61.54 
165° 
133.41 
60.87 
199° 
167.74 
60.10 
84° 
52.04 
62.19 
132° 
100.20 
61.52 
166° 
134.42 
60.85 
200° 
168.75 
60.07 
86° 
54.05 
62.17 
133° 
101.21 
61.51 
167° 
135.43 
60.83 
201° 
169.77 
60.05 
88° 
56.05 
62.15 
134° 
102.21 
61.49 
168° 
136.44 
60.81 
202° 
170.78 
60.02 
90° 
58.06 
62.13 
135° 
103.22 
61.47 
169° 
137.45 
60.79 
203° 
171.79 
60. 
92° 
60.06 
62.11 
136° 
104.22 
61.45 
170° 
138.45 
60.77 
204° 
172.80 
59.97 
94° 
62.06 
62.09 
137° 
105.23 
61.43 
171° 
139.46 
60.75 
205° 
173.81 
59.95 
96° 
64.07 
62.07 
138° 
106.23 
61.41 
172° 
140.47 
60.73 
206° 
174.83 
59.92 
98° 
66.07 
62.05 
139° 
107.24 
61.39 
173° 
141.48 
60.70 
207° 
175.84 
59.89 
100° 
68.08 
62.02 
140° 
108.25 
61.37 
174° 
142.49 
60.68 
208° 
176.85 
59.87 
102° 
70.09 
62. 
141° 
109.25 
61.36 
175° 
143.50 
60.66 
209° 
177.86 
59.84 
104° 
72.09 
61.97 
142° 
110.26 
61.34 
176° 
144.51 
60.64 
210° 
178.87 
59.82 
106° 
74.10 
61.95 
143° 
111.26 
61.32 
177° 
145.52 
60.62 
211° 
179.89 
59.79 
108° 
76.10 
61.92 
144° 
112.27 
61.30 
178° 
146.52 
60.59 
212° 
180.90 
59.76 Miscellaneous Data. 
RAVITY or gravitation is downward pressure or weight. All bodies possess this property 
proportionate to their various degrees of density. 
The force of gravity is an accelerated velocity which heavy bodies acquire in falling 
freely from a state of rest. 
The velocity that a body will acquire in one second of time is equal to 32.2 feet, the distance 
fallen being 16.1 feet; therefore the velocity in feet that a body will acquire is equal to 32.2 feet mul- 
tiplied by the number of seconds occupied in falling; or it is equal to the square root of the product 
of the distance in feet multiplied by 32.2 X 2. 
TABLE XXXV—PRESSURE OF WATER IN POUNDS PER SQUARE INCH FOR EACH 
FOOT IN HEIGHT. 
Feet in 
height. 
Pressure 
per 
square 
inch. 
Feet in 
j height. 
Pressure 
per square 
inch. 
Feet in 
height. 
Pressure 
per square 
inch. 
Feet in 
height. 
Pressure 
per square 
inch. 
Feet in 
height. 
Pressure 
tier square 
inch. 
Feet in 
height. 
Pressure 
per square 
inch. 
! Feet in 
; height. 
Pressure 
per square 
inch. 
1 
.43 
21 
9.09 
41 
17.75 
61 
26.42 
81 
35.08 
101 
43.75 
121 
52.41 
2 
.86 
22 
9.53 
42 
18.19 
62 
26.85 
82 
35.52 
102 
44.18 
122 
52.84 
3 
1.3 
23 
9.96 
43 
16.62 
63 
27.29 
83 
35.95 
103 
44.61 
123 
53.28 
4 
1.73 
24 
10.39 
44 
19.05 
64 
27.72 
84 
36.39 
104 
45.05 
124 
53.71 
5 
2.16 
25 
10.82 
45 
19.49 
65 
28.15 
85 
36.82 
105 
45.48 
125 
54.15 
6 
2.59 
26 
11.26 
46 
19.92 
66 
28.58 
86 
37.25 
106 
45.91 
126 
54.58 
7 
3.03 
27 
11.69 
47 
20.35 
67 
29.02 
87 
37.68 
107 
46.34 
127 
55.01 
8 
3.16 
28 
12.12 
48 
20.79 
68 
29.45 
88 
38.12 
108 
46.78 
128 
55.44 
9 
3.89 
29 
12.55 
49 
21.22 
69 
29.88 
89 
38.55 
109 
47.21 
129 
55.88 
10 
4.33 
30 
12.99 
50 
21.65 
70 
30.32 
90 
38.98 
110 
47.64 
130 
56.31 
11 
4.76 
31 
13.42 
51 
22.09 
71 
30.75 
91 
39.42 
111 
48.08 
131 
56.74 
12 
5.2 
32 
13.86 
52 
22.52 
72 
31.18 
92 
39.85 
112 
48.51 
132 
57.18 
13 
5.63 
33 
14.29 
53 
22.95 
73 
31.62 
93 
40.28 
113 
48.94 
133 
57.61 
14 
6.06 
34 
14.72 
54 
23.39 
74 
32.05 
94 
40.72 
114 
49.38 
134 
58.04 
15 
6.49 
35 
15.16 
55 
23.82 
75 
32.48 
95 
41.15 
115 
49.81 
135 
58.48 
16 
6.93 
36 
15.59 
56 
24.26 
76 
32.92 
96 
41.58 
116 
50.24 
136 
58.91 
17 
7.36 
37 
16.02 
57 
24.69 
77 
33.35 
97 
42.01 
117 
50.68 
137 
59.34 
18 
7.79 
38 
16.45 
58 
25.12 
78 
33.78 
98 
42.45 
118 
51.11 
138 
59.77 
19 
8.22 
39 
16.89 
59 
25.55 
79 
34.21 
99 
42.88 
119 
51.54 
139 
60.21 
20 
8.66 
40 
17.32 
60 
25.99 
80 
34.65 
100 
43.31 
120 
51.98 
140 
60.64 the novelty circulator. 
The space in feet fallen through is equal to 16.1 multiplied by the square of the number ol 
seconds. 
The force of gravity is a cause of retarded and ol accelerated motion: ascending an in- 
clined plane, the force of gravity retards the motion; descending an incline plane, the torce ol gravity 
accelerates the motion. 
TABLE XXXVI.—CAPACITIES OF ROUND AND SQUARE TANKS 
Diameter 
of 
Round Tank 
and side of 
Square Tank 
in feet 
and inches. ; 
CIRCULAR TANK. 
SQUARE TANK. 
Cubic feet. 
Gallons. 
Cubic feet. 
Gallons. 
1 
.7845 
5.8735 
1 
7.4805 
1-6 
1.7671 
13.215 
2.25 
16.8311 
2 
3.1416 
23.494 
4 
29.922 
2-6 i 
4.9087 
36.7092 
6.25 
46.7531 
3 
7.0686 
52.8618 
9 
67.3245 
3-6 
9.6211 
73.1504 
12.25 
91.63 
4 
12.5664 
93.9754 
16 
119.68 
4-6 
15.9043 
118.9386 
20.25 
151.47 
5 
19.635 
146.8384 
25 
187. 
5-6 
23.7583 
177.6740 
30.25 
226.27 
6 
28.2744 
211.4472 
36 
269.28 
6-6 
33.1831 
248.1564 
42.25 
316.03 
7 
38.4846 
287.8032 
49 
367.52 
7-6 
44.1787 
330.3859 
56.25 
420.75 
8 
50.2656 
375.9062 
64 
478.72 
8-6 
56.7451 
424.362 
72.25 
540.43 
9 
63.6174 
475.756 
81 
605.88 
9-6 
70.8823 
530.086 
90.25 
675.07 
10 
78.54 
587.353 
100 
748.05 
11 
95.0334 
710.697 
121 
955.08 
12 
113.0976 
848.189 
144 
1077.12 
13 
132.7326 
992.627 
169 
1264.12 
14 
153.9384 
1151.212 
196 
1466.08 
15 
176.7150 
1321.545 
225 
1683. 
16 
201.0624 
1503.625 
256 
1914.88 
17 
226.9806 
1697.451 
289 
2161.72 
18 
254.4696 
1903.025 
324 
2423.52 
19 
283.5294 
2120.346 
361 
2700.28 
20 
314.16 
2349.414 
400 
2992. 
21 
346.3614 
2590.229 
441 
3298.68 ABRAM COX STOVE COMPANY. 
103 
COMPARATIVE VALUE OF BOILER AND PIPE COVERINGS. 
(From the Metal Worker.) 
A mass of each material to be experimented upon, 1 inch thick, was carefully prepared and 
placed on a perfectly fiat iron plate or tray, which was then carefully maintained at a constant tem- 
perature of 810° Fahr. The heat transmitted through each non-conducting mass was calculated in 
pounds of water heated 10° Fahr. per hour. The author summarized his results in two convenient 
tables, which are given below : 
TABLE XXXVII—BOILER AND PIPE COVERINGS: VARIOUS SUBSTANCES. 
3 
p 
3 
cr 
o 
p 
Substance 1 inch thick (in mass); 
heat applied, 310° F. 
Pounds of 
water heated 
10° F. per 
hour through 
1 square foot. 
Solid matter 
in 1 square 
foot 1 inch 
thick, parts 
1000. 
Air included, 
parts 1000. 
1 
Hair felt 
11.4 
189 
957 
2 
Cotton felt 
10.6 
75 
930 
3 
Jute felt 
13.2 
162 
921 
4 
Linen felt 
11.7 
64 
753 
5 
Loose cotton felt 
9.3 
17 
990 
6 
Carded cotton 
8.1 
16 
987 
7 
Rabbit-hair “ wool” 
7.1 
43 
912 
8 
Poultry feathers 
6.2 
44 
976 
9 
Cork powder 
13.6 
66 
931 
10 
Sawdust powder 
14.2 
141 
793 
11 
Asbestos powder 
47.9 
67 
961 
12 
Fossil meal 
52.1 
78 
910 
13 
Plaster of Paris 
36.2 
371 
598 
14 
Calcined magnesia 
14.7 
24 
979 
15 
Compressed calcined magnesia..- 
53.4 
291 
711 
16 
jFine sand 
66.3 
533 
473 
TABLE XXXVIII.—BOILER AND PIPE COVERINGS: PREPARED MIXTURES. 
52! 
£ 
B 
cr 
® 
Prepared mixtures for covering steam pipes, etc. 
Pounds of 
water heated 
10° F. per 
hour by 1 
square foot. 
l 
Ciay, dung, and vegetable fiber paste 
39.6 
2 
Fossil meal and hair paste 
10.4 
3 
Fossil meal and asbestos powder 
26.3 
4 
Paper pulp, clay, and vegetable fiber 
44.6 
5 
Paper pulp alone 
14.7 
6 
Stag wool, hair, and clay paste 
10.0 
7 
Asbestos fiber, wrapped tightly.— 
17.9 
8 
Coal ashes and clay paste wrapped with straw 
29.9 104 
TEE NOVELTY CIRCULATOR. 
TABLE XXXIX-DIMENSIONS OF ELBOWS AND COUPLINGS FOR 
WROUGHT-IRON PIPE * 
ELBOWS. 
COUPLINGS. 
inside 
diameter 
Center to 
Depth of 
of pipe 
External 
Length 
in inches. 
end in 
end in 
inches. 
inches. 
diameter 
in 
C E 
O D 
D 
in inches. 
inches. 
1 
u 
4 
1 
2 
Ill 
4 
1 
1 5 
a8 
4 
1JT 
If1 
if 
4 
1 7 
91 
2 
5 
8 
2 
m 
4 
2 
9£ 
“4 
5 
8 
9 3 
Z1 6 
2 
2f 
3J 
5 
8 
2H 
9 5 
2* 
3 
4 
l 
3^2 
2ff 
3 
4f 
ItV 
4^V 
3 
3* 
3f 
4 
4 
4| 
3* 
4 
41 
*8 
6 
4 
SeV 
3| 
41 
4f 
6* 
4 
4* 
3| 
5 
4f 
n 
4 
6* 
3|f 
6 
2 
8f 
4 
3ff 
7 
6* 
10 
4 
8|| 
4 5 
M 6 
8 
6f 
11 
4 
9t76 
4t96 
9 
10|f 
4 
10 
14 
6i 
11 
13M 
6± 
12 
* Copyrighted, 1892, by John J. Hogan. ABRAM COX STOVE COMPANY. 
105 
TABLE XL—DIMENSIONS OF STANDARD WROUGHT-IRON PIPE 
Nominal 
inside diam- 
eter. 
Inches. 
Actual diameter. 
Inches. 
Thickness. 
Inches. 
Circumference. 
Inches. 
Length of pipe in feet per 
square foot of surface. 
Area. 
Square inches. 
Inside. 
Outside. 
Internal. 
External. 
Inside. 
Outside. 
Internal. 
External. 
l 
8 
.27 
.4 
.07 
.84 
1.27 
14.15 
9.44 
.06 
.12 
1 
4 
.36 
.54 
.08 
1.14 
1.69 
10.50 
7.07 
.1 
.22 
3 
8 
.49 
.67 
.09 
1.55 
2.12 
7.67 
5.65 
.19 
.35 
1 
2 
.62 
.84 
.10 
1.95 
2.65 
6.13 
4.5 
.3 
.55 
3 
4 
.82 
1.05 
.11 
2.58 
3.29 
4.63 
3.63 
.53 
.86 
1 
1.04 
1.31 
.13 
3.29 
4.13 
3.67 
2.9 
.86 
1.35 
H 
1.38 
1.66 
.14 
4.33 
5.21 
2.76 
2.3 
1.49 
2.16 
1* 
1.61 
1.9 
.14 
5.06 
5.96 
2.37 
2.01 
2.03 
3.83 
2 
2.06 
2.37 
.15 
6.49 
7.46 
1.84 
1.61 
3.35 
4.43 
2* 
2.46 
2.87 
.20 
7.75 
9.03 
1.54 
1.32 
4.78 
6.49 
3 
3.06 
3.5 
.21 
9.63 
10.96 
1.24 
1.09 
7.38 
9.62 
31 
3.56 
4. 
.22 
11.14 
12.56 
1.07 
.95 
9.83 
12.56 
4 
4.02 
4.5 
.23 
12.64 
14.13 
.94 
.84 
12.73 
15.9 
4.5 
5. 
.24 
14.15 
15.7 
.84 
.76 
15.93 
19.63 
5 
5.04 
5.56 
.25 
15.84 
17.47 
.75 
.62 
19.99 
24.29 
6 
6.06 
6.62 
.28 
19.05 
20.81 
.63 
.57 
28.88 
34.47 
7 
7.02 
7.62 
.30 
22.06 
23.95 
.54 
.5 
38.73 
45.66 
8 
7.98 
8.62 
.32 
25.07 
27.09 
.47 
.44 
50.03 
58.42 
9 
9. 
9.68 
.34 
28.27 
30.43 
.42 
.4 
63.63 
73.71 
10 
10.01 
10.75 
.36 
31.47 
33.77 
.38 
.35 
78.83 
90.79 
11 
11. 
11.75 
.37 
34.55 
36.91 
.34 
.32 
95.03 
108.43 
12 
12. 
12.75 
.37 
37.7 
40.05 
.32 
.3 
113.09 
127.67 
13 
13.25 
14. 
.37 
41.62 
43.98 
.29 
.27 
137.88 
153.94 
14 
14.25 
15. 
.37 
44.76 
47.12 
.27 
.25 
159.48 
176.71 
15 
15.4 
16. 
.28 
48.48 
50.26 
.25 
.24 
187.04 
201.06 
16 
16.4 
17. 
.30 
51.52 
53.41 
.23 
.23 
211.24 
226.98 
17 
17.3 
18. 
.34 
54.41 
56.55 
.22 
.21 
235.61 
254.47 TTIE NOVELTY CIRCULATOR. 
TABLE XLI.—WEIGHTS, CAPACITIES, AND THREADS OF STANDARD WROUGHT-IRON PIPE* 
Nominal 
inside 
diameter. 
Nominal 
weight per 
lineal foot. 
Number of 
threads per 
inch. 
Size to drill 
for thread. 
Length to 
thread. 
Length of 
pipe contain- 
ing one cubic 
foot. 
Length of 
pipe contain- 
ing one 
gallon. 
Contained 
gallons per 
lineal foot. 
Contained 
cubic inches 
per lineal foot. 
Continued 
pounds of 
water per lineal 
Inches. 
i Pounds. 
Inches. 
Inches. 
Feet. 
Feet. 
foot. 
i 
8 
.24 
27 
2 1 
64 
9 
3 2 
2500. 
336.6 
.0029 
, 
.686 
.024 
1 
4 
.42 
18 
2 9 
6 4 
3 
8 
1385. 
184.8 
.0054 
1.249 
.044 
3 
8 i 
.56 
18 
1 9 
3 2 
7 
T6 
751.5 
100.8 
.0099 
2.299 
.082 
1 
.84 
14 
2 3 
3 2 
1 
2 
472.4 
63.2 
.0158 
3.657 
.132 
3 
4 
1.12 
14 
1 5 
1 6 
9 
1 IT 
270. 
36.1 
.0277 
6.399 
.23 
1 
1.67 
Hi 
1_3_ 
1 1 6 
8 
166.9 
22.3 
.0448 
10.352 
.373 
It 
2.64 
Hi 
115 
L 3 2 
11 
TF 
96.25 
12.8 
.0777 
17.952 
.648 
1* 
2.68 
Hi 
12 3 
13 
1 6 
70.65 
9.4 
.1058 
24.456 
.883 
2 
3.61 
Hi 
9 3 
t 
42.36 
5.7 
.1742 
40.26 
1.454 
01 
5.74 
8 
2f 
1 
30.11 
4.02 
.2484 
57.396 
2.072 
3 
7.54 
8 
3i 
1 
19.49 
2.6 
.3837 
88.656 
3.202 
3i 
9. 
8 
3f 
41*6 
14.56 
1.95 
.5136 
118.644 
4.285 
4 
10.66 
8 
H 
H 
11.31 
1.51 
.6612 
152.76 
5.517 
41 
12.34 
8 
4| 
H 
9.03 
1.2 
.828 
191.268 
6.908 
5 
14.5 
8 
£ 5 
°T6 
H 
7.2 
.96 
1.0388 
239.988 
8.668 
6 
18.76 
8 
6 5 
°T6 
if 
4.98 
.66 
1.5007 
346.668 
12.521 
7 
23.27 
8 
73 
' 8 
ii 
3.72 
.49 
2.0123 
464.844 
16.79 
8 
28.18 
8 
«3 
°8 
if 
2.88 
.38 
2.5998 
600.468 
21.688 
9 
33.7 
8 
qi 9 
if 
2.26 
.3 
3.3056 
763.596 
27.58 
10 
40.06 
8 
1013 
XUTS 
if 
1.8 
.24 
4.0954 
946.056 
34.171 
11 
45. 
8 
1.5 
.2 
4.9366 
1140.36 
41.189 
12 
49. 
8 
1.27 
.17 
5.8748 
1357.08 
49.017 
13 
54. 
8 
1.04 
.139 
7.1625 
1645.56 
59.762 
14 
58. 
8 
.9 
.12 
8.2933 
1913.76 
69.125 
15 
62. 
8 
.77 
.102 
9.7163 
2244.48 
81.07 
16 
8 
.68 
.091 
10.9734 
2534.88 
91.559 
17 
8 
.61 
.081 
12.2394 
2827.32 
102.122 
* Copyrighted, 1892, by John J. Hogan. ABRAM COX STOVE COMPANY. 
107 
Sizes of pipes. 
Yi inch. 
% inch 
1 inch. 
134 inch 
1J4 inch 
2 inch. 
2)4 inch 
3 inch. 
3V, inch. 
4 inch. 
434 inch. 
5 inch. 
6 inch. 
7 inch. 8 inch. 
J-2 inch 
1. 
1.7 
2.8 
4.9 
6.6 
11. 
15.6 
24. 
32. 
41. 
52. 
65. 
94. 
123. 167. 
1. 
1.6 
2 6 
3 8 
6 2 
8 9 
13 8 
18 
•>q 
:40 
‘-17 
- i 
1 inch 
1. 
1.7 
2.3 
3.8 
5.5 
8.5 
11. 
j • 
14. 
18. 
23. 
33. 
i -. yo. 
44. 57. 
ll4 inch 
1. 
1.3 
2.2 
3.1 
4.9 
6.6 
8. 
10. 
13. 
19. 
25. 33. 
1)4 inch 
1. 
1.6 
2.3 
3.6 
4.8 
6.2 
7.7 
9.7 
14. 
19. 24. 
1. 
1.4 
9 9 
2.9 
3.8 
4.7 
5 3 
8.6 
6. 
11 14 
1. 
1.5 
2. 
2.6 
3.3 
4.1 
8 10 
1. 
1.3 
1.7 
2.1 
2.7 
3.9 
5 2 6 7 
1. 
1.2 
1.6 
2. 
2.9 
3 9 5 
1. 
1.2 
1.5 
2.2 
3 3 9 
1. 
1.2 
1.8 
2 4 3.1 
1. 
1.4 
1 9 2.5 
1. 
1.3 1.7 
1. 1.2 
1. 
Internal areas 
of pipes. 
.3048 
.5333 
.86271.496 
2.038 
3.355 
4.783 
7.388 
9.887 
12.73 
15.93 
19.99 
28.88 
38.73 50.03 
TABLE XLII—EQUALIZATION OF PIPE AREAS. 
TABLE XLIII—INCHES IN FRACTIONAL AND DECIMAL PARTS OF A FOOT. 
Inches. 
Fraction of 
foot. 
Decimal part 
of foot. 
Inches. 
Fraction of 
foot. 
Decimal part 
of foot. 
1 
1 
1 2 
.0838 
6* 
1 3 
"24 
.5417 
u 
A 
.125 
7 
A 
.5833 
2 
% 
.1667 
A 
44 
.625 
01 
-2 
A 
.2083 
8 
A 
.6667 
3 
X 
.25 
84 
A 
.7083 
8* 
A 
.2917 
9 
A 
.75 
4 
/3 
.3383 
9J 
1 9 
¥¥ 
.7917 
4* 
A 
.375 
10 
5 
¥ 
.8333 
5 
5 
TT 
.4167 
101 
74 
.875 
H 
A 
.4583 
11 
11 
1 2 
.9167 
6 
V* 
.5 
11* 
2 3 
¥1 
.9583 108 
THE NOVELTY CIRCULATOR. 
TABLE XLIV-DECIMAL EQUIV- 
ALENTS OF FRACTIONS OF 
AN INCH. 
1 
FT 
of ill) 
inch 
= 
.015625 
1 
FF 
U 
b 4 
— 
.03125 
1 
TF 
U 
44 
— 
.0625 
3 
FT 
U 
44 
= 
.09375 
i 
U 
44 
= 
.125 
F + FT 
U 
44 
= 
.15625 
1 1 
8 1 IF 
u 
44 
= 
.1875 
1 i 3 
8 1 3F 
u 
44 
= 
.21875 
1 
¥ 
u 
44 
= 
.25 
l 4- i 
4 r ff 
u 
44 
= 
.28125 
1 _L i 
4 1 TF 
u 
44 
= 
.3125 
1 _L_ 3 
¥ t FF 
u 
44 
= 
.34375 
3 
8 
u 
44 
= 
.375 
3 1 1 
8 ~i FF 
u 
44 
= 
.40625 
3 1 1 
8 1 IF 
u 
44 
— 
.4375 
3 1 3 
8 T FF 
u 
44 
— 
.46875 
1 
2 
u 
44 
= 
.5 
2 + fV 
u 
44 
= 
.53125 
2 + TF 
u 
44 
= 
.5625 
i + F3F 
44 
44 
= 
.59375 
5 
8 
44 
44 
= 
.625 
5. 1 1 
8 1 FF 
44 
44 
— 
.65625 
5 11 
F ~r TF 
44 
44 
= 
.6875 
5 1 3 
F I FF 
44 
44 
— 
.71875 
3 
¥ 
44 
44 
= 
.75 
A _L_ 1 
¥ ' FF 
44 
44 
= 
.78125 
A _L 1 
4 ! 1 6 
44 
44 
— 
.8125 
A 1 3 
4 TFF 
44 
44 
= 
.84375 
7 
8 
44 
44 
= 
.875 
F H FT 
44 
44 
= 
.90625 
F + TF 
44 
44 
= 
.9375 
1 _L 3 
8 r ft 
44 
44 
= 
.96875 
1 inch 
~~ 
1. 
TABLE XLV-RECORDED TEMPERATURES 
STATION. 
No. of 
months 
fire is 
required. 
Mean 
temp, of 
fire mos. 
A v reage 
No. of 
degrees 
temp, to 
be raised. 
Max. No. 
of degrees 
temp, t" 
be raised. 
Min. 
temp, of 
fire mos. 
7 
6 
35° 
35° 
87° 
— 17° 
89° 
31° 
72° 
2° 
7 
37° 
33° 
81° 
— 11° 
Buffalo, N. Y 
8 
35° 
35° 
83° 
— 13° 
Burlington, Vt 
7 
32° 
38° 
90° 
— 20° 
Chicago, 111 
7 
35° 
35° 
90° 
— 20° 
Charleston, S. C 
8 
52° 
18° 
47° 
+ 23° 
Cincinnati, 0 
7 
42° 
28° 
77° 
— 7° 
Cleveland, 0 
7 
38° 
32° 
83° 
— 13° 
7 
35° 
35° 
90° 
— 20° 
8 
28° 
42° 
108° 
— 38° 
7 
41° 
29° 
88° 
— 18° 
26° 
+ 44° 
6 
37° 
33° 
90° 
— 20° 
6 
42° 
28° 
80° 
— 10° 
5 
39° 
31° 
68° 
2° 
8 
37° 
33° 
95° 
— 25° 
44° 
+ 26° 
7 
40° 
30° 
76° 
- 6“ 
Philadelphia, Pa 
7 
40° 
30° 
75° 
— 5° 
Pittsburgh. Pa 
7 
39° 
31° 
82° 
— 12° 
Portland. Me 
8 
33° 
37° 
82° 
12° 
Portland, Ore 
6 
43° 
27° 
67° 
+ 3° 
San Francisco, Cal 
4 
53° 
17° 
34° 
+ 36° 
St. Louis, Mo 
5 
37° 
33° 
86° 
— 16° 
7 
5 
25° 
45° 
102° 
73° 
— 32° 
Washington, D. C 
40° 
30° 
— 5° 
Wilmington, N. C 
4 
50° 
20° 
55° 
+ 15° ABRAM COX STOVE COMPANY. 
109 
WEIGHTS AND VOLUMES. 
One United States gallon contains 231 cubic inches. 
One United States gallon weighs 8.33 pounds. 
United States gallons multiplied by .13367 equals cubic feet. 
United States gallons multiplied by 231 equals cubic inches. 
Cubic feet multiplied by 7.48 equals United States gallons. 
Cubic inches multiplied by .04329 equals United States gallons. 
One cubic foot of water at 62° weighs 62.321 pounds. 
One cubic inch of water at 62° weighs .03606 pounds. 
A column of water one foot or 12 inches high equals .433 pound pressure per square inch. 
A column of water 2.3093 feet or 27.71 inches high equals one pound pressure per square inch. 
A column of water 33.947 feet high equals 14.7 pounds pressure per square inch, which is 
the pressure of the atmosphere at the level of the sea. 
A column of water 100 feet high produces a pressure on the base of 43.3 pounds per 
square inch. 
One cubic foot of ice at 32° weighs 57.96 pounds. 
Water is at its maximum density at 39.33° Fahr., or 4.107° cent. 
Wrought-iron : One cubic foot = 480 pounds. One square foot 1 inch in thickness = 40 
pounds. Square bar 1 inch by 1 inch 1 foot long = pounds. 3.6 cubic inches = 1 p>ound. 
Weight of wrought-iron X .92= weight of zinc. 
Weight of wrought-iron X .93 = weight of cast-iron. 
Weight of wrought-iron X 1.01 = weight of steel. 
Weight of wrought-iron X 1.15 = weight of copper. 
Weight of wrought-iron X 1.47 = weight of lead. 
Weight of wrought-iron X 1.08 = weight of brass. 
Cubic inches X -26 = pounds of cast-iron. 
Cubic inches X .278 = pounds of wrought-iron. 
Cubic inches X .283 = pounds of cast-steel. 
Cubic inches X .322 = pounds of copper. 
Cubic inches X .410 = pounds of lead. THE NOVELTY CIRCULATOR. 
TABLE XLVI.—COMPARISON OF WEIGHTS AND MEASURES. 
UNITED STATES AND BRITISH IMPERIAL GALLONS. 
Cubic inches in one gallon. 
Weight of one gallon in pounds. 
Gallons in one cubic foot. 
231. 
8.3311 
7.4805 
277.274 
10. 
6.2321 
LIQUID MEASURES. 
United States gallon. 
British imperial gallon. 
French litre. 
Cubic metre. 
1. 
.83 
3.77 
.0038 
1.19 
1. 
4.53 
.0045 
.26 
.22 
1. 
.001 
8.3311 lbs. 
10 lbs. 
2.204 lbs. 
231 cubic incites. 
277.27 cubic inches. 
61 cubic inches. 
LINEAR MEASURES. 
Inches. 
Decimals of inches. 
F eet. 
Metre. 
1 
2.54 centimetres. 
12 
1. 
30.475 
36 
3. 
91.425 
2 5 
6T 
.39 
.0328 
1 centimetre = .01 
3.9376 
.328 
1 decimetre = .1 
39f 
39.376 
3.28 
1 metre = 1 
SQUARE OR SURFACE MEASURES. 
Square inches. 
Decimals of square inches. 
Square feet. 
Square metre. 
1 5 5 
T¥TTff 
.155 
.001076 
1 square centimetre. 
15| 
15.5 
.1076 
1 square decimetre. 
1650 rVjy 
1550 47 
10.76 
1 square metre. 
1 square inch. 
1 square inch. 
.00694 
6.45 square centimetres. 
1 square foot. 
9.3 square decimetres. 
CUBIC OR SOLID MEASURES. 
Cubic inches. 
Decimals of cubic inches. 
Cubic feet. 
Cubic Metre. 
6 1 
Toutr 
.061 
.0000353 
1 cubic centimetre. 
61-21T 
61.05 
.0353 
1 cubic decimetre. 
61061^ 
61051.3 
35.32 
1 cubic metre. 
1 cubic inch. 
1 cubic inch. 
.000578 
16.38 cubic centimetres. 
1 cubic foot. 
28.32 cubic decimetres. 
1 pound avoirdupois 
= 0.45 kilogramme. 
1 kilogramme = 2.204 pounds avoirdupois. General Directions 
THE Circulator and all flow and return pipes which arc not used for heating should be covered. 
The emptying or discharge-valve should be at the lowest point in the system; the outlet from 
it should be open to view and should not be connected to a sewer pipe. 
The end of the overflow pipe from expansion tank should be open to view, and discharge into 
sink or other open receptacle. Where overflow pipe is connected to expansion tank, a tee, open on 
top end of vertical run, should be used instead of an elbow. 
The expansion tank should be placed as high as possible above the Circulator. 
An automatic supply of water to a system by means of a ball cock in expansion tank or other 
device is desirable. 
As few valves as possible should be used on hot-water heating systems, and they should be of 
the gate or angle pattern. 
Direct radiators may have one valve on either flow or return connection according to 
convenience. 
Direct radiators should have an air cock or air valve where the pipes are not arranged to 
prevent air accumulations. 
The flow and return pipes should be arranged so as to prevent air accumulations by being 
directly connected with main air pipe. 
Main flow pipes are preferably inclined up from Circulator to radiators, but they may be 
inclined down toward radiators, dependent on the position of the air outlet pipe. 
Main return pipes are inclined down toward Circulator or emptying or discharge-valve. 
One main flow pipe and one main return pipe with short branches are preferable to numerous 
small flow and return pipes from Circulator to each radiator, as the latter method reduces the tem- 
perature of the water before entering the radiators, introduces an unnecessary number 'of joints, 
occupies much space with pipes, is more costly, and is not needed to assist circulation where a well- 
designed heater is used. 
Indirect radiators should have air pipes in preference to air valves, or the pipes should be 
arranged so that the radiators can free themselves of air through the flow pipes without using air 
pipes, air cocks, or air valves. 
Indirect radiators need no stop valve on either flow or return pipes, as the regulation of the 
heat from them is controlled by the register valve, and dampers in air-mixing flue and cold-air ducts. 
Provision may be made for the application of thermometers on the main flow and return 
pipes near the Circulator by means of' inserted copper or brass caps screwed into the pipes or fittings 112 
THE NOVELTY CIRCULATOR. 
and in which the thermometers may be applied as desired. Fixed thermometers screwed into the 
pipes are not desirable. 
Fittings, tees, elbows, etc., on flow pipes should not have their openings reduced by the use 
of bushings. Reducing fittings may be used, but it is preferable, especially with tees, to make the 
reduction with a nipple and reducing coupling. 
The casings for indirect radiators may be of tin, wood, or galvanized iron. In all cases the 
casing should be made as tight as practicable. Galvanized iron by itself is not as desirable a material 
for a radiator casing as when used in combination with wood or other covering because it 
transmits heat too readily. 
An indirect radiator and casing should be connected to only one warm-air flue or duct. 
A single warm-air flue or duct should not supply registers on different floors. 
Warm-air pipes should be of tin or galvanized iron. 
Warm-air pipes in exposed positions or in external walls should be constructed double or pro- 
tected so that there will be but little loss of temperature to the heated air in its passage to the apart- 
ment to be warmed. 
The cold-air duct to each casing should be fitted with a damper and connected to a by-duct or 
air-mixing duct which should also have a tight-fitting damper. 
These dampers should have levers attached by which they can be adjusted readily and held 
in any desired position. 
Cold-air ducts are made of wood tongued and grooved, and also of galvanized iron; the latter 
material is preferable. These ducts should be made air-tight so that the air from the cellar or base- 
ment in which they are located will not be drawn into them and allowed to pass up into the apart- 
ments warmed. 
The cold-air duct should be connected to an air chamber which should surround the cold-air 
inlet opening. In this chamber there should be a baffle or some device to prevent the velocity of the 
wind affecting the air in the ducts and casings. 
The cold-air opening should be fitted with a damper easily adjusted and accessible; outside 
this damper the cold-air inlet opening should be fitted with a screen of wire mesh. 
A separate ventilating flue should be provided for each apartment in dwellings. 
One or more ventilating flues or shafts should be provided in all buildings that are occupied 
and required to be warmed. 
Ho indirect heating system is complete or satisfactory without proper arrangements for ven- 
tilation. 
Ventilation is the most important part of a well-designed indirect heating apparatus. 
The circulation of air is as much needed as the circulation of water in an indirect beating 
system. 
Ventilation is as necessary to health as heat,