US3077087A - Outdoor heat - Google Patents

Description

Feb. 12, 1963 Filed Aug. 16,

R. E. JA PHET SELF-POWERED FORCE FEED HEAT PUMP CDLD MIX'I'URE GAS lL LIQUD 2 Sheets-Sheet l FIG.|

COOLI N G' CYC LE LlQuln WATER IN losF. WATER 00T IloR 4 SEPARATQR RECEIVER (la a.)

MIXED G-AS s LIQUID LIQUID 90 FSIG-.To 35 PSI 6.

FIC-n2.

HEATING CYCLE RICHARDEJAPHET 1N V EN TOR.

Rl-:ElvER (ma) United States Patent @dice 3,077,087 SELF-PWERED FORCE FEED HEAT PUMP Richard E. laphet, Coytesville, NJ., assigner to Worthington Corporation, Harrison, NJ., a corporation of Delaware Filed Aug. 16, 1961, Ser. No. 131,915 6 Claims. (Cl. 62-324) This invention relates generally to heat pumps and more particularly to a force feed type heat pump system which employs the inherent thermodynamic characteristics of the high to low side pressure differential as the motive power for the force feed circulation of the low pressure side cycle.

In my copending U.S. application Serial No. 107,181, iiled May 2, 1961, a new and improved heat pump system was described, characterized by the fact that the compressor functioned in a condensing or high pressure side cycle and a pump functioned in an evaporating or low pressure side cycle, which cycles were relatively independent but coacted by means of a common accumulator or the like separating means.

In the force feed heat pump system shown in my copending application it was inherent in the structure shown that the pump would ybe operated by a conventional means such as an electric motor or other independent prime mover.

it is known, however, as shown in Patents 2,156,096, 2,519,010, 2,737,031 and 2,986,898 that in conventional refrigerant cycles motive power can be obtained from the pressure drop of the refrigerant liuid as it passes from the condensing cycle to the evaporating cycle of the refrigerant arrangement.

This broad principle is particularly applicable to the heat pump system shown and described in my copending application U.S. Serial No. 107,181. The addition of this principle to such heat pump system has two main advantages.

(a) It simplifies the system in that the use of the relirigerant fluid to operate the lluid operated driver permits the driver to act as an expansion device thus eliminating either the low pressure tloat valve, iioat valve mechanism or the high pressure float valve metering device as is required in the system shown in the copending application.

(b) lt eliminates the conventional prime mover for at least the important heating and cooling cycles, which in turn increases the efficiency of the system by the power consumption factor of such conventional prime mover.

Thus, the present invention covers an improved heat pump having a cooling and a heating cycle wherein cornpression means functions in a condensing or high pressure side cycle and pump means functions in an evaporating or low pressure side cycle, which cycles are relatively independent but coact through a common separating means and wherein the high pressure refrigerant from the high pressure side cycle is at all times delivered for expansion to a suitable iluid operated driver having its outlet connected to said separating means which driver provides the motive power for the pumping means operating in the low pressure side cycle.

Accordingly, it is an object of the present invention to provide a force feed type heat pump system which is relatively simple and employs the inherent thermodynamic characteristics of the refrigerant iluid as it changes pressure and phase.

It is another object of the present invention to provide a heat pump system wherein the conventional prime mover such as an electric motor will be eliminated from the system and the driving means of the pump will be operated by the refrigerant of the system itself.

Further objects and advantages of the invention will 3,077,637 Patented Feb. 12, 1953 become evident from the following description with reference to the accompanying drawings in which:

FIGURE 1 is a diagrammatic sketch of the invention showing a cooling cycle including an outdoor heat exchanger in heat exchange communication with atmospheric air.

FIGURE 2 is a diagrammatic sketch of the invention showing a heating cycle including an outdoor heat exchanger in heat exchange relation with atmospheric air.

FIGURE 3 is a diagrammatic sketch showing a system in accordance with the invention having an auxiliary pump to provide an intermediate cooling cycle.

FIGURE 4 is a diagrammatic sketch showing the invention with the uid operated driver and pump disposed outside of the separating means.

FIGURES 1 and 2 illustrate diagrammatically arrangements of the same elements in the form of a heat pump in accordance with the present invention. They are distinguished in that the refrigerant temperature, pressure and flow path between the elements differ for the respective cooling and heating cycles.

While in the heat pump system illustrated one heat exchanger is shown in heat exchange relation with atmospheric air, it will be understood that such heat exchanger could be associated with other heat sink or heat source media as will be understood by those skilled in the art and that the corresponding heat exchanger best for the medium serving as the heat sink or heat source will be utilized.

Furthermore, while the system shows a. second heat exchanger in heat exchange relation with circulating water to be heated or cooled, it will be understood that heat exchange can be with other liquid media or with air or other gaseous media without departing from the scope of the present invention.

General Arrangement of the Hear Pump Referring to FIGURES l and 2 where the same parts will have the same character numerals, a compressor is shown at 1 having a discharge outlet 2. connected to a discharge line 3 disposed to receive hot compressed gaseous refrigerant from the compressor. The discharge line 3 is connected to three conduits 4i., S and 6 each having a respective solenoid operated valve '7, 8 and 9 which can be manually or automatically controlled to provide that direction of iiow in the system which will produce the desired cooling, heating or defrost cycles. Only the cooling and heating cycles will be described in the present application because the defrost cycle is fully described in my above identified copending application and therefore does not require further comment herein.

Conduit 4 communicates with an inlet header 10 of a first heat exchanger 11 which will be called for the purpose of the present disclosure the outdoor heat exchanger because it is disposed and located so that atmospheric air can be passed thereover as by a fan 12 to permit good heat exchange relation to occur between the coils 13 of the heat exchanger and the air. Heat exchangers for this purpose are well known and are easily purchasable on the open market.

As indicated above this heat exchanger may for all purposes also be one which is adapted for heat exchange relation with other types of heat sink and heat source media.

The outlet header A1e of the first or outdoor heat exchanger communicates to connecting line 15 and common conduit 16 directly with the inlet 17 which is connected to an automatically operable lluid driver and pump arrangement generally designated 18 mounted by any suitable means in a separating means or accumulator 19 which driver and pump arrangement is operable by expansion of the high pressure liquid refrigerant delivered through the inlet line 17 and serves for pumping 10W pressure liquid refrigerant from the Separating means 19 through the low side cycle of the heat pump system as is more fully described hereinafter.

The uid driver may be either the expansion turbine type depicted diagrammatically in FIGURES 1 and 2 of the drawings, a sliding vane type or other suitable driver adapted to be operated by expansion of refrigerant huid. Similarly the pump may be either the centrifugal type shown in FIGURES 1 and 2, a positive displacement type or other suitable pump for delivering the liquid t the low pressure side cycle.

Such devices and pumps are purchasable on the open market, hence, it will be understood by those skilled in the art that any combination of driver and pump for accomplishing the desired result may be used without departing from the scope of the present invention.

Furthermore, even though in the illustrated form of the invention the combined driver and pump are shown mounted in the separating means d?, it is believed that those skilled in the art will understand that this is a matter of practical expediency because it eliminates the necessity for seals and the driver and pump arrangement can be mounted outside of the separating means as is shown in FIGURE 4 but in this latter arrangement in order to obtain the same advantage relative the seal problem the combination unit will have to be hermetic.

Separating means 19 will also be sized sufficiently large both to accommodate the combined fluid driver and pump arrangement 18 and to permit a proper separation 0f the gaseous and liquid refrigerant which is delivered to the accumulator and shall be constructed to act as a high pressure receiver for storing the entire charge of the refrigerant as may be necessary during shutdown or repair periods. The receiver 19a is also provided for overflow and storage.

The combined fluid operated driver and pump arrangement 1S as shown in FIGURES l and 2 includes an integral casing 2t? forming a pump 21 at one end and a duid operated driver 22 at the other end.

The casing 2t? includes a common shaft 23 which extends through the casing from a pumping chamber 2d for the pump 2. to a rotor chamber 2,5 for the fluid operated driver 22 where the respective ends of the shaft receive a pump impeller 26 and a rotor 27.

The rotor is driven by high pressure liquid refrigerant delivered through the nozzle 255 which communicates with the end of the inlet line 17 remote from the end connected to the common line 16.

The rotor chamber' 25 is shown as having a discharge outlet 29 which discharges directly to the separator or accumulator i9. It is believed that those skilled in the art will understand that when high pressure liquid refrigerant expands through the nozzle 28 and expends energy to drive the rotor 27 that the pressure and temperature of the liquid refrigerant will drop and as a result a partial phase change will occur on the discharge outlet side of the rotor 27 so that a mixed gaseous and liquid phase of refrigerant will be discharged from the discharge outlet 29 into the separator 19 Where by reason of the sizing of the separator will separate into the respective liquid and gaseous phases by the eifect of gravity and difference in mass as indicated by the liquid level line therein.

As a result, if the combined fluid operated driver and pump arrangement 18 is so disposed that at least the pump 21 is submerged in the refrigerant liquid, then when the impeller 26 which is connected by common shaft 23 to the rotor Z7 rotates liquid refrigerant can be drawn in through the suction inlet 30 O-f the pumping chamber and discharged through the discharge outlet 31 for the pumping chamber to deliver refrigerant liquid at low pressure to the outlet connecting line 32 which extends through the wall of the separator 19 to deliver low pressure refrigerant liquid to the low side cycle as is more fully described hereinafter.

The gaseous refrigerant in separator 19 will be drawn of through suction line 33 to the suction inlet 34 for the compressor 1 when the compressor is in operation so that the slugging of liquid is always avoided during the operation of the compressor.

Conduit 6 in turn communicates with the inlet header 40 of a second heat exchanger 41 which is termed for the purposes of the kpresent description as the indoor heat exchanger because it will be disposed at an enclosed point such that either a liquid or a gas may be circulated through the coils 42 to provide means for transferring heat or abstracting heat depending on the cycle in operation at the time that refrigerant is flowing through the coils. This is accomplished in the present form of the invention by passing liquid through the cooling fluid inlet 43 and removing it by outlet 44 to the point where the liquid can be utilized. Heat exchangers for this purpose are Well known in the air conditioning and refrigeration art and are easily purchasable 0n the open market, hence are not more fully described herein.

The outlet header 45 for the second or indoor heat exchanger 41 is also connected through return line 46 to the common line 16 and FIGURES l and 2 show that the conduits 15 and 46 are provided with check valves as at 47 and 48 respectively so that the flow of refrigerant fluid through the outdoor and indoor heat exchangers will be unidirectional at all times which condition of 0peration is a specific characteristic of the present invention regardless of the particular cycle of operation.

FIGURES l and 2 also show that lines 15 and 46 cornmunicate through lines 49 and 50 respectively directly to a common collecting line Srl and depending on the operating cycle which signals the automatic or manual setting for control valves 52 and 53 for the respective lines 49 and S0, refrigerant gas and liquid from one or the other of the heat exchangers 11 or 41 can bypass the common conduit 16 and be passed directly to the separator or accumulator 19.

The operation of valves 7, Y8, 9, 52l and 53 may be manual or automatic and any suitable type of conventional solenoid or the like type pneumatically or electrically operated controls.

Pumping Cycle In order to provide the positive or force feeding circulation of refrigerant liquid to the respective indoor and outdoor heat exchangers in the heating or cooling cycle hereinafter described where the heat exchanger is not receiving hot compressed gaseous refrigerant, the pump 21 delivers low pressure refrigerant liquid through outlet line 32 connected to the conduits 55 and 56 which are in turn connected to the conduits 4 and 6 leading to the heat exchangers 11 and Ail. Conduits 55 and 56 are provided with their respective check valves 57 and 5S which check valves act to direct the flow of refrigerant liquid depending on the setting of the control valves 7 and 9.

It is readily .apparent that the operation of the check valves S7 `and 5S will be similar to that of the check valves 47 and 4S which depend on the setting of the control valves 52 and 53.

In both the case of the check valves 57 yand 5S and check valves 47 and 48 the pressure of the refrigerant will pressurize one or the other of the check valves so that the ow will occur through that check valve which does not have pressure acting against its discharge side.

The valves 52 #and `53 also permit the inclusion of the defrosting cycle which is accomplished through the defrosting conduit 5 connected to the common discharge line 3 from the compressor `and to a point downstream of the solenoid operated valve 7 and the check valve 57, which defrosting cycle is fully described in my copending application and hence is not referred to further herein `as it forms no part of the present invention.

Also described in my copending application is an oil recovery arrangement which includes a valve 60. This system is also not described in the present application as it forms no part of the present invention.

Cooling Cycle Cooling of ya liquid or gaseous medium in heat exchange relation with the indoor heat exchanger 41 can be obtained by operating the heat pump in the following manner:

First, the compressor 1 and the fan 12 are placed into operation. Valves 7, 53 and 60 will be open and all other valves will be closed. Hot compressed gaseous refr-igerant from the compressor 1 will now pass through the discharge outlet 2 and common discharge line 3 to the conduit 4 connected to the inlet header 10 of the outdoor heat exchanger 11. ln the outdoor heat exchanger 11 the hot compressed gaseous refrigerant will b-e condensed to provide a hot liquid refrigerant which will collect in the outlet header 14 of the outdoor heat exchanger 11.

The hot liquid refrigerant passes from the outlet header 14 through lines 1S and 16 to the yinlet line 17 which communicates with the nozzle in the rotor chamber 25. The hot liquid refrigerant expands through the nozzle and provides the motive power for rotating the rotor 27 and is discharged through the discharge outlet 29 as ya mixture of relatively cold gas and liquid refrigerant into the separator or accumulator 19 where t-he gaseous liquid refrigerant by reason of the sizing of the separator separates so that a gas layer occupies the upper portion of the accumulator and a liquid layer occupies the lower portion of the accumulator as indicated by the liquid level line in FIGURE 1.

Suction line 33 of the compressor is connected to the upper portion of the accumulator which holds the gaseous refrigerant. Therefore, only gas passes through the suction line 33 and the suction inlet 34 of the compressor Where it is once again recompressed to repeat .the condensing or high side cycle above described.

Since the fluid operated driver and pump operate automatically Whenever the rotor is energized under the action of the expanding hot refrigerant liquid the relatively cold liquid refrigerant in the accumulator 19 will be pumped with positive pressure to the indoor heat exchanger 41. Thus pump 21 receives liquid through the suction inlet 30 into the pump chamber 24 and discharges the refrigerant liquid through line 32 to the connecting conduits 55 and 56. Due to the fact that hot compressed gaseous re frigerant is passing through conduit 4 the check valve 57 is prevented from opening and liquid refrigerant from the pump 21 must be delivered through conduit 56 and check valve 58 to the conduit 6 connected to the inlet header 4d of the indoor heat exchanger 41.

At the indoor heat exchanger the liquid refrigerant is passed therethrough into heat exchange relation with fluid to tbe cooled which is delivered through line 43 and removed by line 44 so that part of the cold liquid refrigerant is evaporated as it cools the uid being passed through the indoor heat exchanger. This -cooled iiuid media `as it leaves line 44 may be passed to any suitable point of use.

It is believed clear to tho-se skilled in the air conditioning and refrigeration `art that air or other gaseous media could also be cooled by passing it in heat exchange relation with a suitable type indoor heat exchanger without departing from the scope of this invention.

The refrigerant collected in the outlet header 45 of the heat exchanger 41 will be part gas and part liquid because the pump supplies a greater quantity of liquid than is required for the capacity of the heat exchanger. This is advantageous because the inner surfaces of the tu-bes of the heat exchanger will under these conditions be continually wetted `thereby increasing the efficiency `of the heat exchanger.

This mixture of gaseous and liquid refrigerant will be passed from the outlet header 45 through lines 46 and 50 and control valve 53 to line 51 into the separator or accumulator 19 where it joins with alike mixture as gas and 6 liquid from the discharge outlet 29 of the :duid driver 22 Where it is separated by gravity as indicated by the liquid level line shown.

This pump circulation cycle will operate continuously to provide the desired cooling as long as the compressor continues to operate with the valve set for the cooling cycle as above described.

Heating Cycle In the heating cycle shown in FIGURE 2 the compressor 1 and the fan 12 are first placed into operation, all valves are closed except control valves 9, 52 and 60.

With this arrangement of the control valves hot compressed gaseous refrigerant Will be discharged from the compressor through discharge outlet 2 and discharge line 3 to the conduit 6 and will be passed by conduit 6 to the inlet header 40 of the indoor heat exchanger 41 where it gives up heat to the medium to be heated as, for example, water brought into the heat exchanger 41 through the inlet 43 and discharged to the desired point of use through outlet 44 in its heated condition. lt is understood that heat exchange could be made with other liquid media or air or other gaseous media without departing from the scope of this invention and that where air or a gas media is used that the type heat exchanger required for this rnedia will also be used as is well known in the heat pump art.

The release of heat to the media to be heated causes the gas to condense to provide hot liquid refrigerant, which hot liquid refrigerant passes through the outlet header 45 of the heat exchanger 41 through line 46 and check valve 48 to the common line 16 leading into the inlet line 17 of the combined fluid operated driver and pump device 13.

The hot refrigerant liquid expands and releases its energy to place the rotor 27 into operation so that relatively cool gas and liquid refrigerant will be passed from the discharge outlet 22 to the separator or accumulator 19 where by reason of the size of the accumulator the refrigerant mixture separates as by gravity to provide a gaseous layer and a liquid layer of the refrigerant in intimate contact with each other as indicated by the liquid level line in FIGURE 2.

Since the suction line 33 communicates with the gaseous portion of the refrigerant in the separator 19 the compressor will draw gaseous refrigerant through the suction inlet line 33 and suction inlet 34 into the compressor where it will be recompressed and passed through the cycle above described.

In addition to the heat of compression heat is also drawn from the heat source in Contact with the outdoor heat exhanger 11 by force feeding cold refrigerant liquid to this outdoor heat exchanger by means of the pump circulation cycle.

Thus, pump 21 operating automatically whenever the rotor 27 of the fluid operated driver 22 is energized will receive liquid refrigerant from the separator 19 through its suction inlet 30 where it passes through the pump chamber 24 and is discharged through line 32 to the connecting conduits 5S and 56.

Due to the fact that hot compressed gaseous refrigerant is passing through conduit 6 the check valve 58 in the line 56 is prevented from opening and liquid refrigerant from pump 21 must be delivered to conduit 55 and check valve 57 to the conduit 4 connected to the inlet header 10 of the outdoor heat exchanger 11.

As this cold liquid refrigerant passes through coil 13 of the outdoor heat exchanger 11 the liquid refrigerant which will always be colder than the heat source will pick up heat from the heat source and then from the outlet header 14 of the outdor heat exchanger 11, will be passed through line 15 and line 49 and control valve S2 to the collecting line 51 which delivers the mixture of gas and liquid refrigerant to the separating means 19 where it separates into gas and liquid layers similar to the separation of the mixture discharged from outlet 29 as indicated by the liquid 'level line and as above described recirculated through lines 32 and 33 for the compressor and suction inlet for the pump respectively to repeat the cycle above described.

The construction thus described of the present invention While operating substantially similar to that of the construction described in my copending application Serial No. 107,181 differs in that it utilizes thc inherent thermodynamic characteristics of the high to low side pressure differential as 'the motive force for the force feed circulation of the low pressure side cycle which system is not only simpler in construction but further has a materially increased efficiency thereover by the power consumption factor of the conventional prime mover required in such systems.

Intermediate Cycle It is apparent that the motive force for the pump 21 depends on the continuous operation of the compressor 1. However, the present invention can be easily adapted to provide an intermediate cooling cycle identical with that described in my copending application Serial No. 107,181 if the system is modified as shown in FIGURE 3 of the drawings.

In FIGURE 3 identical parts have been given identical numbers and the operation is identical with that above described for the respective cooling and heating cycles.

However, by adding an auxiliary pump as at 7d operated by any conventional form of prime mover 71 if the suction inlet of the pump is connected to the separator 19 and the discharge outlet is connected to line 55 it is believed clear that iluid can be delivered independently through the respective conduits by this auxiliary pump when the compressor is not in operation.

Thus, for the intermediate cooling cycle where cooling is effected by a mixing process, the heat content of two portions of the refrigerant is changed by circulation. One portion discharges heat to the heat sink and the other absorbs heat from the media to be cooled, the respective portions then being mixed together for recirculation through the system once again by means of the separator 19.

This operating cycle is designed for very limited conditions where some but not a large quantity of cooling is required and the circulation can of course 'oe either in parallel as shown in FIGURE 3 or the drawings or in series as is indicated in my copending application Serial No. 107,181.

Thus by reference to FIGURE 3 which shows a parallel arrangement we find that in this cycle only the pump 7d and the fan 12 will be in operation. The compressor will not be in operation. in addition valves '7, S, 3- and 60 will be closed and valves 52 and 53 will be open.

In operation pump 7d draws refrigerant liquid from the separator 19 and discharges the liquid under pressure through lines 55 and 56 simultaneously into conduits 4 and 6 respectively which in turn direct the liquid refrigerant to the inlet header 10 for the heat exchanger l1 and the inlet header di) for the heat exchanger 41.

Refrigerant liquid in heat exchanger' 11 will pass through the coils 13 and on contacting heat exchange relation with air passed thereacross by the fan 12 and thus will be cooled. The cool refrigerant collects in the outlet header 14 and is passed via lines l5 and dit and collecting line 51 to the separator 19.

Similarly liquid refrigerant in heat exchanger 41 will pass through its coils in non-contacting heat exchange relation with the media be it liquid or gas or other fluid to be cooled as, for example, water which is introduced through inlet 43 and discharged through outlet i4 of the heat exchanger 41 which cooi liquid can be utilized for cooling at any suitable point.

The heat exchange relation in heat exchanger d1 delivers a mixture of gas and liquid refrigerant to the outlet header of the heat exchanger l1 which mixture flows via lines 46 and 50 and control valve 53 to the collecting line 51 which communicates with the separator 19 where it mixes with the cool liquid refrigerant returning from the heat exchanger 11. Mixture of the two provides a refrigerant having an ambient temperature which will once again permit it to absorb heat from the media to be cooled by repetition of the full cycle above described.

Where the intermediate cooling cycle is accomplished by series ow the system must be modied as shown in FIGURE 6 of my copending application Serial No. 107,181 and since it has been fully described therein it is not deemed necessary to repeat the description of the series cycle for the purposes of the present invention.

Modified Form of the Invention FGURE 4 shows a modified form of the invention and differs from the form of the invention shown in FIG- URES l and 2, only to the extent that the combined fluid operated driver and pump arrangement is disposed exteriorly of the separator.

ln FiGURE 4 identical parts have been given identical numbers and the operation of these parts is substantially identical with those above described for the cycles of the invention shown in FIGURES 1 and 2..

By reference to FIGURE 4 line 16 is connected to the inlet port 17 for the automatically operable iluid driver and pump arrangement designated 18.

The combined fluid operated driver and pump arrangement 18 as shown in FIGURE 3 is a hermetic unit and thus includes an integral casing 20 forming a pump 21 at one end and the fluid operated driver 22 at the other end.

The casing 20 has a comm-on shaft 23' which extends `from the pumping chamber 24' of the pump Z1' to the rotor chamber 25 for the fluid operated driver 22 where the respective ends of the shaft receive a pump impeller 26 and a rotor 27.

Therotor is driven by high pressure liquid refrigerant, identical with the form of the invention shown in FIG- URES l and 2, which is delivered through the nozzle 28' connecting with the inlet port 17' remote from the end connected to common line 16.

The rotor chamber 25 is shown as having a discharge line 29a connected to the return line 51 so that mixed gaseous and liquid refrigerant is released to the separator or accumulator@ for separation into layers as indicated by the liquid level line and for recirculation.

The pump Z1 is provided with a suction inlet 30' which connects suction line 3%@ to the lower section of the separator 19, and will when rotated with .the rotation of rotor 27 discharge refrigerant liquid from the pumping chamber 2d through discharge outlet 31' for the pumping chamber and outlet line 32 connected in turn to conduits 55 and 56. y

Operation of this form of the invention will be identical with that above described lfor the cooling and heating cycles of FIGURES 1 and 2. This `form of the invention differs only to the extent that the driver and pump 18' are external of the separator 19, hence fluid discharge from the driver must pass through the lines 29a and 51 for discharge directly into the separator and the pump must direct fluid to the suction inlet Bil via the line 30a connected to the lowermost portion of the separator 19.

it will be understood that this invention is not to be limited to the specific construction or arrangement of parts shown but that they may be widely modified within the scope of the invention defined by the claims.

What is claimed is:

y1. ln a heat pump, a'plurality of heat exchange means, separating means for storing and separating gaseous and liquid refrigerant, a iiuid operated driver having an inlet and an outlet wherein the outlet is disposed in operative relation to said separating means for delivering fluid thereto, means connecting the downstream side of each heat exchange means to `the inlet of said fluid operated aoc/zoe? driver, a compression means, said compressi-on means having its suction connected to said separating means and its discharge being connected to deliver hot compressed gaseous refrigerant interchangeably and selectively to the upstream side of at least one of said heat exchange means, and a pump circulation cycle having its suction connected to said separating means to receive cold liquid refrigerant therefrom and to force feed an excess of liquid refrigerant to the upstream side of at least one other of said heat exchange means not receiving hot compressed gaseous refrigerant from said compression means, said pump means connected to and operated by said iiuid operated driver.

2. ln a heat pump, a lirst heat exchange means and a second heat exchange means each having inlet means and outlet means, at least one compressing means, at least one pumping means, means to interchangeably and selectively connect the compression means and the pumping means to the respective inlet means for the first and second heat exchange means, a common separating means for storing and separating gaseous and liquid refrigerant, a uid operated device having an inlet and an outlet, means connecting the respective outlet means from said iirst and second heat exchange means to the inlet for said fluid operated device to expand refrigerant therethrough for driving said fluid operated device, said separating means in communication with the outlet of said fluid operated devce to receive expanded refrigerant therefrom, said compression means having its suction connected to said common separating means to receive gaseous refrigerant therefrom and to pass hot compressed gaseous refrigerant to that heat exchange means selectively connected to the discharge of the compression means, and said pumping means having its suction connected to said common separating means to receive cold liquid refrigerant therefrom and to pass any excess of liquid refrigerant under pressure to that heat exchange means selectively connected to the discharge lof the pumping means, and said liuid operated device operatively connected to said pump to provide the motive power for driving said pump.

3. In a heat pump having a heating and a cooling cycle, a high pressure side cycle including, compression means and at least one heat exchanger, a low pressure side cycle including pump means and at least one other heat exchange means, means interchangeably and selectively connecting the compression means discharge to the upstream side of said first-mentioned heat exchange means and to the upstream side of said second heat exchange means for delivering hot compressed gaseous refrigerant thereto, means interchangeably and selectively connecting the pump means to the upstream side of said first-mentioned heat exchange means and to the upstream side of said second heat exchange means for delivering cold liquid refrigerant from said pump means to the respective heat exchange means, a common separating means for storing and sepaarting gaseous and liquid refrigerant, a Huid operated device having an inlet and an outlet, means connecting the downstream side of said first heat exchange means and said second heat exchange means to the inlet of said liuid operated device delivering hot liquid refrigerant at high pressure to said inlet for expansion in the liuid operated device, said fluid operated device having its outlet connected to deliver mixed low pressure gaseous and liquid refrigerant to the separating means, lsaid compression means having its suction inlet connected to said common separating means and its discharge outlet connected to said means for interchangeably and selectively del-ivering hot compressed gaseous refrigerant .to the upstream side of the respective first and second heat exchange means, and said pump means having its suction connected to said common separating means and its discharge connected to said means for delivering cold liquid refrigerant to said first and second heat exchange means and at al1 times to deliver an excess of liquid refrigerant to the respective heat exchange means connected thereto for the particular cycle of operation, and said pump means connected to and operated by said fluid operated device.

4. In the heat pump as claimed in claim 3 wherein the liuid operated device is disposed in said separating means.

5. In the heat pump as claimed in claim 3 wherein the tiuid operated device and pump are combined in a single operating unit, and said combined fluid operated driver and pump are mounted in said separating means.

6. In a heat pump as claimed in claim 3 including an auxiliary pumping means, a conventional driver for operating said auxiliary pumping means, said pumping means having an inlet and an outlet, and said pumping means disposed to permit the inlet to receive liuid from said separating means and to discharge said refrigerant iuid .to the upstream side of said respective heat exchangers, and said auxiliary pumping means disposed to operate independently and without the compressor to selectively deliver relatively cold liquid refrigerant from the separating means to the respective heat exchangers yfor providing an intermediate cooling cycle when the same is required.

References Cited in the tile of this patent UNITED STATES PATENTS 2,394,109 Sanchez Feb. 5, 1946 2,494,120 Ferro Jan. 10, 1950 2,576,663 Atchison Nov. 27, 1951 2,724,240 Sloan Nov. 22, 1955

Claims (1)

1. IN A HEAT PUMP, A PLURALITY OF HEAT EXCHANGE MEANS, SEPARATING MEANS FOR STORING AND SEPARATING GASEOUS AND LIQUID REFRIGERANT, A FLUID OPERATED DRIVER HAVING AN INLET AND AN OUTLET WHEREIN THE OUTLET IS DISPOSED IN OPERATIVE RELATION TO SAID SEPARATING MEANS FOR DELIVERING FLUID THERETO, MEANS CONNECTING THE DOWNSTREAM SIDE OF EACH HEAT EXCHANGE MEANS TO THE INLET OF SAID FLUID OPERATED DRIVER, A COMPRESSION MEANS, SAID COMPRESSION MEANS HAVING ITS SUCTION CONNECTED TO SAID SEPARATING MEANS AND ITS DISCHARGE BEING CONNECTED TO DELIVER HOT COMPRESSED GASEOUS REFRIGERANT INTERCHANGEABLY AND SELECTIVELY TO THE UPSTREAM SIDE OF AT LEAST ONE OF SAID HEAT EXCHANGE MEANS, AND A PUMP CIRCULATION CYCLE HAVING ITS SUCTION CONNECTED TO SAID SEPARATING MEANS TO RECEIVE COLD LIQUID REFRIGERANT THEREFROM AND TO FORCE FEED AN EXCESS OF LIQUID REFRIGERANT TO THE UPSTREAM SIDE OF AT LEAST ONE OTHER OF SAID HEAT EXCHANGE MEANS NOT RECEIVING HOT COMPRESSED GASEOUS REFRIGERANT FROM SAID COMPRESSION MEANS, SAID PUMP MEANS CONNECTED TO AND OPERATED BY SAID FLUID OPERATED DRIVER.

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