US2098462A - Self regulated heat transfer system - Google Patents

Description

Nov. 9, 1937. s p, MlLLER 2,098,462

SELF REGULATED HEAT TRANSFER SYSTEM Filed May 15, 1936 2 sheets-sheet 1 n L n 4I'I--N Il Il k Il II n `v-"Vmr Y :l E: `-J1 .-11 5 11 -f` JZ J2 i Je lili! f i an -I Z ge s Nov. 9, 1937,4

s. P. MILLER 2,098,462 SELFl REGULATED HEAT TRANSFER SYSTEM Filed May 15, 1936 2 sheets-sheet 2 Patented Nov. 9, i937 UNT TTES saar enumeran naar TRANSFER srs'rnrr Samurai 1P; Miller, Chicago, Ill.

Appiication May 15, 1936, Serial No. 79,842

En @amada January 27, 1936 29 Claims.

'Ny invention relates to improvements in self regulated heat transfer systems and has for a particular object the provision of a heat transfer system in which the pressure or degree of 5 vacuum through the entire system may be maintained at a substantially uniform and predetermined point without any human intervention.

This application is a continuation in part of my application for patent on Self regulated heat transfer systems, Serial No. 699,557, first led in the United States Patent Oilce on November'Zi, 1933, and renewed on April 425, 1936, and my application for patent on Heat transfer systems, Serial No. 1,091, flied in the United States Patent l5 Omce on January 10, 1935.

Another object is to provide such a system.

at a very small cost and one which may be employed with known heat Atransfer systems without occasioning expensive changes.

Another object of my invention is to provide a heat transfer system in which the pressure in the secondary steam line may be maintained at a Very low point, even below atmosphere, and yet provide sufficient heat for the transfer system.

The expansion of steam as used in the ordiynary steam heating system of today causes a loss in the amount of steam necessary for the work, due to the fact that being controlled from the near end only, expansion of steam through the entire header and riser system results, which accounts for the greatest amount of the so-called friction in the lines, since expansion causes friction, and expanding steam also creates a noncondensible gas which is lighter than expanded steam andwhich therefore 'goes to the top of radiators. Iljhe dew formed of expanded steam goes to the bottom of the radiators, keeps the thermostatic traps shut on due to the heat content, and therefore the gases are not removable by the ordinary vacuum pump. Expansion causes absorption from the steam to the water, ordinarily calledrefrigeration, therefore requiring more steam to do the same work than when there is less expansion of the steam. Expansion causes large amounts of water'to be condensed in headers and risers, due to this expansion and refrigeration, and this water will not be re-evaporated. In other words, if the steam is kept from expanding in headers and risers, no steam will turn to water, and if it did, due to radiation, it would re-evaporate into steam.

In my invention I stop the larger parts of these losses due to expansion by connecting the headers and risers at the near end and the far end with the control valve diaphragm through a control or biasing means whereby headers, risers, and far end return lines, either one affecting the reducing valve or control means, cause more or less steam to be delivered to the headers because 5 one ounce of variation of the control or biasing means would affect the reducing valve diaphragm to the extent of eight ounces, due to the diameter of the reducing Valve diaphragm which is not less than eight inches. Three Aounces less l0 pressure on the diaphragm than the valve is set for would open the valve wide open. Therefore I would have the. risers and headers all full of steam at not less than one ounce difference from end to end to maintain the equilibrium l5 of the valvesetting. Therefore the entire expansion of the steam in the headers and risers would not exceed one ounce which would not set up much absorption and refrigeration; also it would not drop much or any water in the 20 headers and risers. This also stops the boiling of the water in the return lines because the Water does notl absorb heat from the steam in the quantities it would under expansion of the steam, and the returns will operate so near the pressure in the headers and risers the difference in the boiling points at the diierent pressures between the two would not permit the same.

Regulating Valves are very old in the heating art, and it is well known that they are employed 30 and interposed between a primary steam pressure line and a secondary steam pressure line. The primary steam pressure line ordinarily conducts steam from a boiler or other source'of steam at a considerably higher pressure than is desired to be introduced into the secondary steam pressure -line; the regulating valves just mentioned are designed to effect such a reduction of pressure and maintain in the secondary line a substantially uniform and predetermined pressure regardless of the pressure in the primary line. These regulating Valves are ordinarily provided with a manually operable set wheel by which the operator or engineer sets the valve to maintain a desired pressure in the secondary line. It has been found, however, that regardless of the skill and knowledge employed in making regulating valves and heating systems, pressures at various points throughout lthe heat transfer system vary a considerable degree. This variation is most noticeable, of course, between 'a point close to the beginning of the secondary steam line and the far end of the secondary and risers where condensed steam is collected for reevaporation.' A cause of the variation in pressure and temperature is the friction offered by the steam line to the passage of steam therethrough. As before stated one of my objects is to provide a heat transfer system in which variations in pressure and temperature or degree of vacuum throughout the system are substantially eliminated, and in which the pressure or degree of vacuum may be automatically maintained at a predetermined point.

Some heat transfer systems are commonly known as vacuum systems and are in wide use. Some of these systems employ exhaust steam from a power generating engine to supply heating systems or other heat transfer systems. In the type of system just mentioned the primary steam line from the boiler or other source of steam is provided with a by-pass, one side of which supplies steam to a power generating engine under boiler pressure, and the other side of which supplies steam under the same pressure to a reducing or regulating valve, which in turn communicates with the main secondary steam line. The exhaust steam from the power generating engine is received in a tank also communicating. with the main secondary steam line. A vacuum is preferably maintained in the secondary steam line and exhaust st eam receiving tank in order to increase the eiiiciency of the power generating engine and the .heat transfer system. With my system steam may be delivered from the boiler to the heat transfer system at f as much as ten inches of vacuunrif desired; the

vacuum may be maintained at a constant degree by the automatic opening and closing of the regulating or reducing valve interposed between the primary from the boiler and the main secondary steam line. It can be seen that such a result is highly desirable and increases the efflciency of the power generating engine and heating system as well.

My invention may be understood clearly from rthe following specication and drawings, in

which:

Fig. 1 is a 'somewhat diagrammatic layout of a heat transfer system employing my regulating means;

Fig. 2 is a detail view in section of the pilot valve of a conventional type regulating valve with some of my connections attached thereto;

Fig. 3 is a sectional View of a conventional type of check valve employed for preventing the water, pressure, or vacuum in the condensation chamber from affecting the pressure or vacuum of the heat transfer system;

Fig. 4 is a diagrammatic view of a modified steam heating system embodying the princip1e of my invention; and

` Fig. 5 is a vertical sectional view of the control and reducing valve of said system shown in detail.

Referring particularly to Figs. 1, 2, and 3, a conventional type boiler 5 may be employed to deliver steam to a primary steam line 6 which is connected to the high pressure side of a regulating valve generally indicated at 1. A secondary steam line 8 is connected to the low pressure side of regulating valve 1. Secondary line 8 isconnected at its far end with a pipe 9 which empties into a condensation chamber I0. Branch steam .lines I I conduct steam from secondary line 8 to a multiplicity of steam consuming units or radiators I2, and the ends of branch pipes II arereceived by a condensate manifold pipe I3 which empties into a pipe I4. The pipe I4 empties into condensation chamber I0, and a check valve I5 is arranged in line I4 for the purpose above mentioned. Various return pipes I5 conduct condensed and used steam from the heat consuming units I2 and empty into return manifold I1 which empties into a return line I8 having its lower end communicating with condensation chamber I9. A similar check valve 2li is arranged in return line I8.

The particular type of regulating valve illustrated is typical of the construction employed in regulating valves although various types employ some modification in structure. Referring now to Fig. 2 the regulating valve 1 is under the control of a pilot Valve 2i whose stem 22 extends upwardly through a guide web 23 and into a diaphragm chamber 24. The upper end of the stem 22 abuts against a diaphragm 25. The lower end of the stem 22 extends into a spring housing chamber 26 and is encircled by a coil spring 21. A collar 28 is pinned to the stem, and the compression spring 21 presses upwardly on collar 28 to urge the valve 2| to a closed position on valve seat 29. A spring urged disk 30 seats on the upper face of diaphragm 25 and is provided with a stem guide 3| for the sliding reception of a screw stem 32. A compression spring 33 is arranged on screw stem 32 and seats in a groove 34 on the upper face of disk 30. The upper end of spring 33 seats against a follower 35 which carries a longitudinally threaded bore 36 int-o which stem 32 is turned. A pair of guide lugs 31 on follower 35 seat in appropriate grooves of housing 38 and prevent the rotation of said follower.

A steam line 39 extends from high pressure side of the regulating valve 1 to the valve chamber 40 of pilot valve 2|'. The opening of the pilot valve 2| permits steam from the high pressure side to pass into outlet chamber 4I and thence into steam line 42. The steam line 42 communicates with the lower end of a cylinder 43 shown in Fig. 1 and drives piston 44 upwardly. A main valve stem 45 is connected to piston 44 at one end and a main valve 45 at its opposite end. Valve 46 in closed position seats on main valve seat 41 and prevents the passage of steam from high pressure primary to the lower pres- -valve 2I to be unseated in order to admit steam to outlet chamber 4I for action .upon piston 44.

The novel part of my invention and the part which enables the accomplishment of startling results is the following described system of intercommunicating by-passes. A pipe 49 of relatively small dimensions is arranged to conduct steam from secondary pipe 8 to a T fitting 50. A pipe 5I is connected with one end of T fittingl 50 and has its opposite end communicating with diaphragm chamber 24 heretofore described. A pipe 52 is connected to the other end of T fitting 5Il and has its opposite end communicating with a T fitting 53. A pipe 54 extends between pipe 52 and a T fitting 55 arranged in pipe I8. A pipe 56 is connected at one end with T fitting 53 and at its opposite endwith a T fitting 51 which is arranged in pipe 9.-

il'he operation of my system as described above is as follows: 'I'he hand wheel 48 is turned so as to depress diaphragm 25 and valve 2l a lsumcient distance to permit a desiredy pressure in secondary steam line 8. Steam from the primary 6 passes through pipe 39, pilot valve chamber 40, outlet chamber 4I, pipe 52, and pushes upwardly on piston 44 in cylinder 53. Main valve 551s thus opened and steam passes into the secondary and likewise into cylinder 53. The pressure on.

the upper face of piston de tends to force it downwardly and thus decrease the opening of main valve 46. The steam passing into secondary 5 passes through the various pipes l l, steam consuming units l2, manifold i3, far'end 9, return manifold I'l, return pipe i8, pipe i4, and thence into condensation collecting chambers it! and i9. However, steam also passes from secondary 8 to pipe 49 and to T fitting 5i). Since the tension of coil spring 33 opposes the raising of diaphragm 25 by the steam pressure passing through T tting and pipe 5l to `diaphragm chamber 25, the steam follows the line of least resistance and passes through pipe 52 to T fitting 53. As before stated T fitting 53 by-passes steam from line 52 to pipe I8, which is connected`with return manifold il which collects water of condensation from the various steam consuming units, and to pipe 55 which communicates with T tting 5l arranged in pipe 5; pipe 9 is the far end of secondary line 8. When Steam through pipe 52 reaches T fitting 55 it will again follow the line of least resistance, or enter the pipe having the smallest pressure therein, and will continue to do so until the pressures in pipes yI8 and 9 are equalized. As soon as the pressures in pipes i3 and 5 are suihciently great, the pressure in pipe 52 supplied through pipe 49 will be exerted through pipe 5| and cause the passage of steam into diaphragm chamber 2d, the steam pressure on diaphragm 25 will cause the raising of diaphragm 25 when the pressure becomes suciently great, and when this occur.;` compression spring 2l will urge valve stem 22 upwardly and urge pilot valve 2i toward its seat 29. It should be noted carefully, however, that no closing action on pilot valve 2| will occur until an equalization of pressure and a building up of sumcient pressure have been accomplished as above set out.

Under certain circumstances, particularly moderately sized systems, it is Apossible lto omit pipe 56, and under other circumstances to omit pipe 5d. Under these conditions I have found that satisfactory operation of the control valve will result with pipe 52 connected either ,to pipe 9 or I3 as the particular condition may warrant.

A check valve 58 prevents water of condensation, pressure, or vacuum in the condensation 'chamber from affecting the heating system through return steam line 9; it is similar in construction to check valves l5 and 20. 'I'he construction of these check valves is shown clearly in Fig. 3, and each comprises a housing 59, removable cap plug 59a, check ball 59h, and valve seat 59e. An intake nipple 59d is adapted to be connected to a communicating pipe connection, and a nipple 59e is adapted to be connected to an outlet pipe connection. The rise of liquid on thclower side of check ball 59h will cause it to become unseatcd and permit the liquid to enter the outlet pipe connection. The reverse is not,

true, however, because any pressure on thel top side of check ball 59h could not have any unseating function. The pressure on the communicating side of the valve is usually higher than the pressure on theoutlet side, and this, of course, aids in unseating the check lball when necessary. The presence of excess water in steam lines ,makes it difiicult to maintain a balanced pressure throughout the heat transfer system, and it is desirable 'to employ check valves and condensation collecting chambers in order to remove water from steam lines.

I am aware that exhaust steam has been used at above atmospheric pressure for heating systems, but to my knowledge no one has ever controlled exhaust steam for a heating system at subatmospheric pressure, and especially by means which I have provided. Among the advantages are the ecient and economical heat and reduction of back pressure on the engine generating the exhaust steam. The initial pressure steam maybe reduced from thirty-five pounds to at least nineteen pounds per hour per horsepower at deflnite inches of vacuum. The arrangement which I have provided entirely eliminates all the disadvantages of the necessity of using water for condensation in the cases where exhaust steam is used for heating or process work at above atmospheric pressure.

The'means which I have provided are simple.

I have provided a riserand return and radiator structure ,which is conventional, and I have also valve to admit additional steam as desired.

I have provided means for controlling the ,de`

sired amount of vacuum in the heating system to admit steam from a primary line through a reducing valve and by my system exhaust steam may be used as far as it will go and if there is too much of itat certain times a safety valve may be provided. I f the exhaust steam is not suiiicient, steam is automatically admitted from the primary line.

In my system the diaphragm of the reducing l valve of the primary line may also be Yplaced in multiple series with the entire load. The near and far ends of the secondary line may be placed in series by means of the control or by-pass pipe to allow an equalizing of pressure between the near and far ends of thesecondary line .to be registered on the control or by-pass line. Thus the diaphragm in the reducing valve of the primary line being in communication with the control or by-'pass line the pressure on the diaphragm will vary according to the rate of condensation in the condensing units. When the thermostatic trap v'alve opens, bot

ends 'of the secondary line and one side of the diaphragm are placed in communication with the vacuum pump, allowing the vacuum pump to lower the pressure underneath the diaphragm and throughout the` secondary line, which allows the reducing valve to deliver more steam from the primary line 'to the secondary line. When the heat rises in the control line to-a set number of degrees, the thermostatic trap valve closes, cutting oi the pump from communication with the control or by-passline. Ihave provided a thermostatic trap valve for each 4. radiator so that when the steam reaches the desired temperature the trap will close and it will be impossible to draw further steam through the radiator. The vacuum pump will not only assist in exhausting air and condensation speedily, but will assist in automatically maintaining the desired lvacuum, as will be manifest to those skilled in the art, in view of the following description.

In the modified form shown in Figs. 4 and 5, exhaust steam may be led from a prime mover through an exhaust line 80 to a hot water tank 8| and outlet pipe 82. From pipe 82 the exhaust steam may be led into an exhaust manifold 88 connected with a secondary 84, and the manifold may also communicate with a safety exhaust pipe 88 having a safety valve `88 to furnish an outlet for excess exhaust steam. The secondary 84 leads to aradiator manifold pipe 81 and a far end pipe 88 provided with an adjustable thermostatic trap valve 89. I claim no invention in the trap itself as these traps are old and well known and adapt.

ed to close under various temperatures to prevent the passage of steam. Far end-pipe 88 leads to a condensation pipe and a pump feed pipe 1|, which in turn is adapted to feed condensation to a conventional vacuum pump 12. The vacuum pump 12 in turn is provided with a discharge pipe 13 which leads to a conventional air extractor 14 on the tank 8|, and thereafter leads tothe tank 8| itself. The tank 8| is provided with a hot water discharge pipe which leads to a pump 18 adapted to pump hot water through a hot water discharge pipe 11 leading to a steam boiler.

The radiator manifold pipe 81 is adapted to feed steam into a plurality of radlator'branch pipes 18 and radiators 18. The radiator branch pipe 18 is provided with a thermostatic trap valve 80 which may be similar to the trap valve 89 and which will function in a similar manner. The radiator branch pipes 18 lead to condensation pipe lines 8| which in turn lead to a return manifold line 82 which in turn is connected to condensation pipe line 10.

Each radiator is provided with a thermostat control trap valve 83 which may be similar to the traps 89 and 80and function in a similar manner. The radiators communicate with condensation pipes 84 which in turn communicate with return manifold line 82.. A by-pass pipe 85 leads from far end pipe 88 to the exhaust manifold 83.

A by-pass condensation pipe 88 is provided to communicate with pump feed pipe 1| and by-pass pipe 85, and is provided with an adjustable thermostatic trap valve 81, and the by-pass condensation pipe 88 is also provided with a check valve 88 adapted to prevent condensation and such from backing into thepipe 88 from pipe 1|.

The by-pass pipe 85 communicates at its other end with a diaphragm pipe 89 which leads to the pressure compartment 90 of a diaphragm casing 9| in a live steam valve structure 92 as shown in detail in Fig. 5. In the diaphragm casing 9| there is provided a diaphragm 93 which creates not only the steam pressure compartment 90 but also an atmospheric pressure compartment 94. The diaphragm 93 has connected to it a vertical post 95 which is operatively connected to a balance lever 98 provided with Weights 91 in a man;

ner which will be manifest to those skilled in the art.

VResting on the pcst 95 or operativelyconnected toit is a valve stem 9,8 which is located in and travels in a bore |00 in the usual packing 99 and the :valve structure body. The stem 98 at its upper end is enlarged as at I8| and is provided with a pair of valves |02 seating in a pair of valve seats |08 in the valve structure body 92. The valve structure body 92 is provided with an inner chamber |88 communicating with a live steam -the same vacuum conditions throughout the system when using live steam. direct from boilers instead of exhaust steam. In the operation of my system the reducing valve structure 82 may be set at ten inches of vacuum, and the vacuum pump may be set to maintain a vacuum of twelve inches. This arrangement will allow a temperature of steam in the control or by-pass line 88 to be maintained at the temperature of steam at ten inches of vacuum. Whenv the thermostatic trap valve 81 starts to open at this temperature,

'this will allow the twelve inches of vacuum in the return lines to pass to the control or by-pass line and lower the pressure in the secondary line and underneath one side of the diaphragm of the reducing valve structure 82, causing the valves |82 to admit more steam to the system until the temperature in the control line has reached the set temperature, when the thermostatic trap will be closed, cutting off the vacuum pump from the control or by-pass line 88. The thermostatic trap valve will be balanced to maintain the degrees of heat throughout the heating system at the temperature of steam at which the reducing valve is set.

If the temperature at any individual radiator thermostatic trap valve lowers beyond the set temperature, its trap valve will open and the twelve inches of vacuum will operate to draw the necessary steam into the particular radiator, insuring that each radiator shall have the desired amount of steam, regardless of its condition or distance from the source of steam supply.

It will be apparent that under operating conditions a drop in temperature and pressure in the control line will open trap valve 81 and that this drop may be occasioned by a drop in the manifold 83 or in the far end pipe 68. Also if there is sulcient drop in pipe 88, trap valve 88 may be opened. Thus the control valve 92 may be opened by the actuation of either valve 89 or 81. In practice, valve 89 will ordinarily be a considerable djstance away from valve 81 so that the latter may be more sensitive to temperature changes in manifold 83 than will valve 89. Valve 89 will preferably be lset at the temperature desired to be maintained in manifold 88 and secondary 64 and valve 81 will be set slightly lower. Thus if a sudden drop occurs in the system near secondary 64 and manifold 83, valve 81 will open and the full eect of the vacuum pump 82 will be transmitted to valve 92 and open it wide open, if necessary, to bring up the temperature or degree of vacuum to balance. If, however, a small drop occurs in the region of far end pipe 88, valve 88 will open and unbaiance the control line 85 only an amount necessary to unseat valve 92 and consequently admit only the required amount of steam to restore the system to normal.

It will be apparent that far end pipes 9 and 88 do not necessarily need to be separate pipes but may be combined with the last riser or 18. In these cases the control line 5,2 or 85 would be connected to the last riser or 18 and the system would function exactly as described.

ity

By the operation of the system as described, it will be clear that the entire secondary line will be maintained at the temperature and pressure that the control valve is set at. There will consequently be no expansion of steam in the secondary line and risers except a negligible amount, as the control valve is operated upon the slightest unbalancing of pressure or temperature in the control pipe; and because expansion is prevented in this manner the operation of the system will be greatly improved with resulting increase of'eiciency.

In installations Where the foregoing described systems are in operation, uniform savings of ten per cent. and in many instances of fifteen to thirty per cent. have been realized.

While I have illustrated and described the preferred form of construction for carrying my invention into effect, this is capable of variation and modiiication Without departing from the spirit of lthe invention. I, therefore, do not Wish to be limited to the precise details of construction set forth, but desire to avail myself of such variations and modifications as come within the-scope of the appended claims.

Having thus described my invention, what I claim as new and desire to secure by Letters Patent is:

l. In a heat transfer system having a primary steam line, a secondary steam line, a regulating valve interposed between said primary steam line and said secondary steam line and having a diaphragm actuated pilot valve therefor, said pilot valve being constructed and arranged to close the regulating valve upon an increase in pressure exerted against said diaphragmand return steam means, the combination of a communicating pipe connection from near the beginning of said secondary steam line to one side of said diaphragm, and a by-pass connection between said last mentioned pipe connection and said return steam means arranged to allow passage of steam from the former to the latter.

2. In a heat transfer system having a primary steam line, a secondary steam line, a regulating valve interposed between said primary steam line and said secondary steam line and having a diaphragm actuated pilot valve therefor, said valve being constructed and arranged to close the regulating valve upon an increase of pressure exerted .againstsaid diaphragm, and return steam lines including the far end of said secondary steam line, the combination of a communicating pipe connection from near ther beginning of said secondary steam line and one side of said diaphragm, by-pass connections between said communicating pipe connection and said return steam lines, and bypass connections between said return Steam lines and the far end of said secondary steam line, said by-pass connections being arranged to allow passage of steam'from the communicating pipe connections to said'return steam lines including the far end of said secondary line.

3. In a heat transfer system having a plurality of radiators, asteam supply pipe, and a return pipe therefor, the combination of a control valve in said supply pipe and having'a diaphragm chamber, a diaphragm in said chamber, and means connecting said valve and said diaphragm and adapted to close said valve on an increase in the pressure in said chamber and open said valve on a decrease in the pressure in said chamber, a control pipe connected to said chamber and to said supply pipe, and a return pipe connection to said control pipe having a thermostatic trap valve therein.

4. In a heat transfer system having a plurality of radiators, a steam supply pipe, and a return pipe therefor, the combination of a control valve in said supply pipe and having a diaphragm cham' ber, a diaphragm in said chamber, and means connecting said valve and said diaphragm and adapted to close said valve on an increase in 'the pressure in said chamber and open said valve on a decrease in the pressure in said chamber, a oontrol pipe connected to said chamber and to said supply pipe, a return pipe connection to said control pipe having a thermostatic trap valve therein, and a vacuum pump connected to said returnpipe.y i

5. In a heat transfer system having a plurality of radiators, a steam supply pipe, and a return pipe therefor, the combination of a control valve in said supply pipe and having a diaphragm chamber, a diaphragm in said chamber, and means connecting said valve and said diaphragm and adapted to close said valve on an increase in the pressure in said chamber and open said valve on a decrease in the pressure in said chamber, a control pipe connected to said chamber and to said supply pipe, a return pipe connection to said control pipe having a thermostatic trap valve therein,

a vacuum pump connected to said return pipe, and a thermostatic trap valve in said return pipe.

6. In a Yheat transfer system having a plurality of radiators, a steam supply pipe having a far end, and a return pipe therefor, the combination .of a control valve in said supply pipe and having a diaphragm chamber, a diaphragm in said chamber, and means connecting said valve and said y diaphragm and adapted to close said valve on an increase in the pressure in said chamber and open said valve ori a decrease in the pressure in said chamber, a control pipe connected to said chamber and to said supply pipe, and a far end pipe connection to said control pipe.

7. In a heat transfer system having a plurality of radiators, a steam supply pipe having a far end, and a return pipe therefor, the combination of a control valve in said supply pipe and having a diaphragm chamber, a diaphragm in said chamber, and means connecting said valve and said diaphragm and adapted to close said valve on an increase in the pressure in said chamber and open said valve on a decrease in the pressure in said chamber, and a control pipe connecting said chamber, said supply pipe, said far end pipe, and said return, said control pipe and return-connec-l tion having a thermostatic trap valve therein.

B. In a heat transfer system having a plurality of radiators, a steam supply pipe having a yfar end, and a return pipe therefor, the combination of a control valve in said supply pipeland having a diaphragm chamber, a diaphragm in said chamber, and means connecting said valve and said diaphragm and adapted to close said valve on an increase in the pressure in said chamber and open saidvalve on a decrease in the pressure in said chamber, a control pipe connecting said chamber, said supply pipe, said far end pipe, and said return, said control pipe and return connection having a thermostatic trap valve therein, a vacuum pump connected to said return, and a. thermostatic trap valve connecting said far end and said vacuum pump.

9. In a heat transfer system having a plurality of radiators, a steam supply pipe having a far end, and a return pipe therefor, the combination of a control valve in said supply Ipipe and having a diaphragm chamber, a ,diaphragm in said chamber, and means connecting said valve and said diaphragm and adapted to close said valve on an increase in the pressure in said chamber and openv said valve on a decrease in the'pressure in said chamber, a control pipe connecting said chamber, said supply pipe, said far end pipe, and said return. said control pipe and return connection having a thermostatic trap valve therein, a vacuum pump connected to said return, and an adjustable thermostatic trap valve connecting said far end and said vacuum pump.

10. In a heat transfer system having a plurality of radiators, a steam supply pipe having a far end, and a return pipe therefor, the combination of a control valve in said supply pipe and having a diaphragm chamber, a diaphragm in said chamber, and means connecting said valve and said diaphragm and adapted to close said valve on an increase in the pressure in said chamber and open said valve on a the pressure in said chamber, a control pipe connecting said chamber, said supply pipe, said far end pipe, and said return, a vacuum pump connected to said return, a thermostatic trap valve connecting s'aid far end and said vacuum pump, and a by-pass connection between said control pipe and said vacuum pump having a thermostatic trap valve therein.

l1. In a heat transfer system having a plurality of radiators. a primary supply pipe therefor, a secondary supplypipe therefor having a far end and a return for said radiators, the combination of a control valve having a diaphragm chamber, a diaphragm in said chamber, and means connecting said valve and said diaphragm and adapted to close said valve on an increase in the pressure in said chamber and open said valve on a decrease in the pressure in said chamber, and means to prevent expansion of steam insaid secondary, comprising a control pipe connecting said diaphragm chamber, said secondary supply, and said return, said control pipe and return connection having aA thermostatic trap valve therein.

12. In a heat transfer system having a plurality of radiators, a primary supply pipe therefor, a secondary supply pipe .therefor having a far end and a return for said radiators, the combination of a control valve having a diaphragm chamber, a diaphragm in said chamber, and means connecting said valve and said diaphragm and adapted to close said valve on an increase in the pressure in said chamber and open said valve on a decrease in the pressure in said chamber, and means to prevent expansion of steam in said secondary, comprising a control pipe connecting said diaphragm chamber, said secondary supply, and said far end.

13. In a heat transfer system having a plurality of radiators, a primary supply pipe therefor, a secondary supply pipe therefor havingV a far end and a return for said radiators, the combination of a control valve having a diaphragm chamber, a diaphragm in said chamber, and means connecting said valve and 'said diaphragm and adapted to close said valve on an increase in the pressure in said chamber and open said valve on a decrease in the pressure in said chamber, and means to prevent expansion of steam in said secondary, comprising a control pipe connecting said diaphragm chamber, said secondary supply, said far end, and said return, said control pipe and return connection having a thermostatic trap valve therein.

14. In a heat transfer system having a conventional radiator system provided with a redecrease in turn pipe, a primary live steam supply pipe, a secondary exhaust steam supply pipe, means to admit exhaust steam to said system, means to4 admit live steam to said system, said live steam admitting means comprising a reducing and control valve for controlling said live steam admitting means, 'said valve having a diaphragm chamber, a diaphragm inr said chamber, and means connecting said valve and said diaphragm and adapted to vclose said valve on an increase in the pressure therein and open said .valve on a decrease in the pressure therein, a vacuum pump connected to said return pipe, and a control pipe connecting said diaphragm chamber, said secondary exhaust steam supply pipe, and said return pipe, andhaving a thermostatic trap valve in said control line connection to said return pipe. t

15. In a heat transfer system having a plurality of radiators, a primary supply pipe therefor, a secondary supply pipe therefor having a far end and a return for said radiators, means to prevent expansion of steam in said secondary supply pipe, said means including a control valve between said supply pipes and a control pipe for said valve connected to said secondary pipe and said far end and said return, said means including a valved aperture between said primary and secondary supply pipes, said aperture adapted to be varied inversely in proportion to the average pressure in said secondary supply pipe.

16. In a heat transfer system having a plurality of radiators, a primary supply pipe therefor, a secondary supply pipe therefor having a far end and a return for said radiators, means to prevent expansion of steam in said secondary supply pipe and risers, said means including a control valve between said supply pipes and a control pipe for said valve connected to said secondary pipe and said far end and said return, said means including a valved aperture between said primary and secondary supply pipes, said aperture adapted to be varied inversely in proportion to the average pressure in said secondary supply pipe and risers.

1'7. In a heat Vtransfer system having a plurality of radiators, a primary supply pipe there- `for, a secondary supply pipe therefor having a far end and a return for said radiators, means to maintain uniform steam pressure in said secondary including said far end, said means including a control valve between said supply 'pipes and a control pipe for said valve connected to said secondarypipe and said far end and said return, said means including a valved aperture between said primary and secondary supply pipes,`said aperture adapted to be varied inversely in proportion to the average pressure in said secondary supply pipe including said far end.

18. In a heat transfer system having a plurality of radiators, a primary supply pipe therefor, a secondary supply pipe therefor having a far end and a return for said radiators. means to maintain uniform steam pressure in said'secondary including said far end and risers, said means including a control valve between said supply pipes and a con'trol pipe for said valve conrality of radiators, a primary-supply pipe therefor, a secondary supply pipe therefor having a far end and a return for said radiators, means to maintain .uniform temperature vand pressure in said secondary and risers, said means includ-l ing a control valve `between said supply pipes and a `control pipe for said valve connectedto said secondary pipe and said far end and said return, said means including a valved aperture between said primary and secondary supply pipes, said aperture adapted to be`varied inversely in proportion to theaverage pressure in said secondary .supply pipe and risers.

20. In a heat transfer system having a primary steam line and a secondary steam line having a far end, a. regulating valve interposed between said primary and secondary lines, diaphragm actuated control means for said regulating valve, said control means adapted to close the regulating valve upon increase in pressure exerted against said diaphragm and open said valve upon a decrease in pressure exerted against said diaphragm, and means adapted to subject said control means tothe average pressure in said secondary steam line including said far end.

21. In a heat transfer system having a primary steam line and a secondary steam line having a far end, a regulating valve interposed between said primary and secondary lines, diaphragm actuated control means for said regulating valve, said control means adapted to close the regulating valve upon increase in pressure exerted against said diaphragm and open said valve upon a decrease in pressure exerted against said diaphragm, and means adapted to subject said control means to the average pressure in said secondary steam line.

22. In a heat transfer system having a primary steam line and a secondary steam line having a far end, a regulating valve interposed between said primary and secondary lines, pressure actuated control means for said regulating valve, said control means adapted to close the regulating valve upon increase in pressure and open said valve upon a decrease in pressure, and means adapted to subject said control means to the average pressure in said secondary steam line including said far end. v

23. In a heat transfer system having a primary steam line and a secondary steam line having a far end, a regulating valve interposed between said primary and secondary lines, pressure actuated control means for said regulating valve,

said control meansadapted to close the regulating valve upon increase inl pressure and open said valve upon a decrease in pressure, and means adapted to subject said control means to the average pressure in said secondary steam line.

24. In a heat transfer system having a primary steam line and a secondary steam line having a far end, a regulating valve interposed between said primary and secondary lines, pressure actuated control means for said regulating valve, said control means adapted to close the regulating valve upon increase in pressure and open said valve upon a decrease in pressure, and means adapted to subject said control means to the instantaneous average pressure in said secondary steam line. v

25. In a heat transfer system having a primary steam line and a secondary steam line,a regu-.- lating valve interposed `between said primary and secondary lines, pressure actuated control means for said regulating valve, said control means adapted to maintain said regulating valve partially open,`said open degree being determined by the average pressure in said secondary steam line.

26. In a heat transfer system having a primary steam line and a secondary steam line, a regulating valve interposed between said primary and secondary lines, pressure actuated control means for said regulating valve, said control means Iincluding balanced actuating means, the point of balance thereof being determined by the average pressure in said secondary steamline.

27. In a heating system having a primary steann line and a secondary steam line including afar end, and a return, means to control the admission of steam from said primary to said secondary, said means including an automatically actuatable valve, the actuating means or said valve including a member responsive to changes in the average pressure in said secondary, said far end and said return.

28. In a heat transfer system having a plurality of radiators, a primary supply pipe therefor, a secondary supply pipe therefor, having a near end and a far end, a pressure actuated control valve between said primary and secondary supply pipes,

and an equalizing pressure control pipe connecting said valve actuator with the said near end and far end of said secondary supply pipe.

29. In a heat transfer system having a plurality of radiators, a primary supply pipe therefor, a secondarysupply pipe therefor, having a near end and a far end, a return and vacuum means -for said return, a pressure actuated control valve nection.

' SAMUEL P.

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