GB1600760A

GB1600760A - Solar augmented heat pump system with automatic staging reciprocating compressor

Info

Publication number: GB1600760A
Application number: GB24699/78A
Authority: GB
Original assignee: Dunham Bush Inc
Current assignee: Dunham Bush Inc
Priority date: 1977-06-14
Filing date: 1978-05-31
Publication date: 1981-10-21
Also published as: BR7803807A; JPS5416759A; DE2825076A1; CA1070968A; AU3683278A; FR2410233A1; FR2449858A1

Description

(54) SOLAR AUGMENTED HEAT PUMP SYSTEM WITH AUTOMATIC STAGING RECIPROCATING COMPRESSOR (71) We, DUNHAM-BUSH INC., a corporation of the State of Delaware, of 175 South Street, West Hartford, Connecticut, U.S.A., do hereby declare the invention, for which we pray that a patent may be granted to us, and the method by which it is to be performed, to be particularly described in and by the following statement:- This invention relates to air source heat pumps, and more particularly to solar augmented air source heat pump systems employing a multi-cylinder reciprocating compressor.

A reciprocating compressor has long been employed to compress refrigerant vapor in an air source heat pump system with the compressor in series with and between the outdoor and indoor coils which coils trade functions; the outdoor coil constituting the air source evaporator under heating mode and the indoor coil, the condenser; while during cooling mode the indoor coil becomes the system evaporator and the outdoor coil becomes the air source condenser. When the heat pump is operating under heating mode, the system compression ratio increases as the air source heat pump system operates under colder and colder ambient.For instance, assuming that the reciprocating compressor comprises four cylinders and assuming 100% volumetric efficiency under single stage operation would equal four flow units, at 50% volumetric efficiency the single stage operation results is equivalent to two flow units. In higher system compression ratios, the reciprocating compressor volumetric efficiency drops to very low value and 25% volumetric efficiency under max heating conditions are common. For a single stage four cylinder operation, the result is one flow unit at the higher compressor ratios.

Further, it is conventional to improve system efficiency by incorporating a subcooler between the indoor and outdoor coils which functions to subcool the liquid refrigerant downstream of the coil constituting the condenser and prior to feeding the same to the coil acting as an evaporator of the system.

A portion of the high pressure liquid refrigerant is bled from the system and vaporized to further reduce the temperature of that portion of the refrigerant delivered to the coil functioning as the evaporator for the system under that particular mode. The vapor generated in the subcooler is at a pressure which is well above the suction pressure to the reciprocating compressor. The expansion of that refrigerant to the pressure of the refrigerant vapor passing from the downstream side of the coil functioning as the evaporator in the system and entering the inlet or suction side of the compressor, constitutes a system loss reducing the efficiency of the heat pump system.

Solar collectors have been employed as a source of thermal energy to supplement thermal energy input to refrigeration systems, particularly heat pumps.

According to the invention there is provided an air source heat pump system comprising: a first indoor heat exchange coil, a second outdoor heat exchange coil, a multi-cylinder reciprocating compressor, first conduit means carrying refrigerant, said first conduit means including a reversing valve and connecting said coils and said compressor in a primary closed series loop, said reversing valve functioning to cause said indoor and outdoor coils to operate alternately as evaporator and condenser, characterised by:: a third heat exchange coil, said first conduit means further including means for connecting said third heat exchange coil across said outdoor coil, control valve means within said conduit means for selectively controlling refrigerant flow through said primary closed loop to said second and third heat exchange coils, solar energy heat supply means for supplying thermal energy to said third heat exchange coil, means for sensing the temperature of the ambient air passing over said outdoor coil, and control means for operating said control valve means in response to said temperature sensing means; whereby, thermal energy input to said heat pump system during heating mode may be supplied selectively by said second heat exchange coil acting as an air source evaporator or said third heat exchanger coil via said solar energy supply means.

The solar energy heat supply means can comprise a storage tank, a heat sink fluid being within said storage tank, means for selectively circulating said stored heat sink fluid to the third heat exchange coil for thermal absorption by the primary loop refrigerant with said third heat exchange coil acting as solar evaporator, and means for supplying solar energy supplied heat to said storage tank for heating the heat sink fluid to increase the temperature of the same.

The heat sink fluid of the storage tank may comprise glycol or other fluids, and the system may be provided with a pump and solenoid valve means within the closed loop connecting the storage tank to the solar assist evaporator coil for controlling circulation of the glycol therebetween.

Preferably, the reciprocating compressor comprises a plurality of cylinders and the system further comprises means for automatically controlling primary loop refrigerant circulation to and from the compressor for operating the compressor in single stage with all cylinders in parallel or for placing, in response to ambient temperature drop below a predetermined value under system heating mode, at least one cylinder under high side multi-stage compressor operation. The system may further include means for jointly or alternatively operating the outdoor coil and the solar evaporator coil as evaporators for the heat pump system under heating mode.

The system preferably includes a subcooler for sub-cooling condensed refrigerant within the primary loop under at least system heating mode and means for selectively returning vaporized refrigerant to the low stage or high stage cylinders of the compressor.

The invention will now be further described with reference to the accompanying drawings in which: Figure 1 is a hydraulic schematic circuit diagram of a preferred embodiment of a solar augmented air source heat pump system formed according to the invention with automatic staging reciprocating compressor; Figure 2 is the schematic diagram of Figure 1 with the heat pump system of Figure 1 in single stage compressor, solar evaporator heating mode; Figure 3 is the schematic diagram of Figure 1 with the heat pump system in high ambient air source evaporator heating mode; Figure 4 is the schematic diagram of Figure 1 with the heat pump system in low ambient air source evaporator, staged compressor and subcooling operation, heating mode, and Figure 5 is the schematic diagram of Figure 1 with the heat pump system in air source condenser, cooling mode.

Referring to the drawings, principal components comprise a four cylinder multi-stage reciprocating compressor indicated generally at 10, a first heat exchanger 12 constituting the indoor coil, a second heat exchanger 14 constituting the outdoor coil, a third heat exchanger 16 constituting the solar augmented evaporator or chiller, a heat sink storage tank 18, a solar collector 20 for supplying thermal energy to the heat sink fluid 22 such as glycol within the storage tank, a four way reversing valve 24 and a primary loop subcooler 21. Conduit means connects the four way reversing valve 24, the reciprocating compressor 10, the indoor coil 12, and the outdoor coil 14 in a series, closed primary loop refrigeration circuit.

In that respect, the reciprocating compressor 10 comprises a left cylinder head 26 and a right cylinder head 28. The left cylinder head 26 includes manifold means 23 and 25 defining a low side 30 and a high side 32 for the first cylinder 34 and a low side 31 and a high side 33 for a second cylinder 36. The right cylinder head 28 comprises a low side 38 and a high side 40 for the compresor's third cylinder 42 and fourth cylinder 44, by way of manifold means 45. Compressor inlets for the left cylinder head 26 are provided at 46, 48 and 50, while a single inlet is provided for both cylinders 42 and 44 of the right cylinder head 28 as at 52. A common outlet 54 for both cylinders 42 and 44 is provided for the right cylinder head 28 on the high side 38, while for the compressor left cylinder head 26, two high side outlets are provided: at 56 for cylinder 36, and at 58 for cylinder 34.

The primary refrigeration loop incorporating compressor 10, indoor coil 12 and outdoor coil 14 includes conduit 60 between four way reversing valve 24 and the indoor coil 12, conduit 62 between the indoor coil 12 and the outdoor coil 14, and conduit 64 from the outdoor coil 14 to the opposite side of the four way reversing valve 24. Conduit 66 connects the four way reversing valve 24 to left cylinder head inlets 46 and 48 by way of branch lines or conduits 68 and 70, and employs conduit 67 which terminates at inlet 52 for the right cylinder head 28. Outlet manifold 72 acts to interconnect the high sides 32 and 38 of the left cylinder head cylinder 34 and right cylinder head cylinders 42 and 44 to the four way reversing valve 24 through line or conduit 74 which extends between the manifold 72 and the four way reversing valve 24.Line 74 incorporates a check valve 76 permitting flow from manifold 72 to the four way reversing valve 24 but preventing reverse flow. The high side of the right cylinder head 28 is connected to the manifold by way of line or conduit 78 which connects to the outlet 54 of the compressor right cylinder 28 on the high side 38. A conduit 80 connects the manifold 72 to the outlet 58 on the high side 32 of the left cylinder head cylinder 34. In addition, a line or conduit 82 connects outlet 56 of the left cylinder head for cylinder 36 to the four way reversing valve 24, by intersecting line 74 at point 84 downstream of the check valve 76.

A further line or conduit 85 connects the manifold 72 to the low side inlet 50 of the compressor left cylinder head 26 feeding cylinder 36. This line includes a solenoid operated control valve 86. Within conduit or branch line 70, there is provided a check valve 88 which permits flow from the four way valve 24 to the inlet 48 for compressor cylinder 36 but prevents reverse flow therein.

The subcooler 21 in the illustrated embodiment is connected within line 62 intermediate of the indoor and outdoor coils. A branch line or conduit 90 carries a solenoid operated control valve 92 for controlling the bleed of high pressure liquid refrigerant from the primary loop which vaporizes by expansion through a thermal expansion valve 94 or its equivalent, also within line 90, to subcool that portion of the liquid refrigerant within that portion of line 62 within subcooler 26, with the vaporized refrigerant returning to the compressor by way of vapor return line or conduit 96. Conduit 96 intersects conduit 84 at point 98.

The primary refrigerant loop includes solenoid operated control valve 108 within line 62 and solenoid operated control valve 107 within conduit or line 65 to control primary refrigerant flow so as to direct that flow either through the outdoor coil 14 or the solar evaporator coil or chiller 16. The outdoor col 14 is provided with a fan or blower 110 driven by fan motor 110a. The indoor coil is provided with fan or blower 112 driven by motor 112a. These are appropriately energized for operation to force ambient air and indoor air over the coils respectively in conventional fashion.

The solar assist air source heat pump system of the present invention employs the solar collectors 20 as an alternate source of heat by solar impingement as at 114, the solar collectors 20 being connected to the storage tank by way of a closed loop conduit 116 including coil 118 immersed within the glycol or heat sink medium 22. In turn, the glycol circulates between the solar assist chiller or evaporator 16 by way of conduit means 120. Fluids, therefore, perform the heat transfer of heat randomly from the solar collector to the storage tank heat sink medium 22 and upon demand from that medium to the chiller 16. Conduit means 120 incorporates solenoid operated control valve 124 and pump 122 for forced circulation of the glycol 22.

In order to effect the automatic control of the solar augmented air source heat pump system of the present invention, the solenoid operated control valve 124 is connected to a control panel 126 by line 128, while the pump 122 is connected by line 130 to the same control panel. The control panel 126 is energized through lines 132 from an electrical source (not shown).Providing input signals to the control panel 126 to effect control of the four way reversing valve 24 and solenoid control valves 86, 92, 107, 108 and 124 and pump 122 are: thermobulb or temperature sensor 134 mounted within the storage tank 18 and immersed within the heat sink fluid 22, thermobulb or temperature sensor 136 within the air stream of ambient air passing over the surface of the second heat exchanger or outdoor coil 14 and thermobulb or temperature sensor 138 positioned in the path of the indoor air which moves over the indoor coil 12. Alternatively, thermobulb 138 may be placed in the room or other environment being treated by indoor coil 12. The control or power signals emanate from control panel 126 and pass to the various valves including four way reversing valve 24.

Thermobulb 134 is connected to the control panel 126 by line 140, thermobulb 136 to the control panel 126 by line 142 and thermobulb 138 to the control panel 126 by line 144.

Further, line 150 connects the solenoid operated control valve 108 to the same control panel and companion valve 107 is connected thereto by line 147. Line 148 connects the solenoid operated control valve 86 to that panel, and line 152 connects the solenoid operated control valve 92 to said control panel. Fan motor 11 0a is connected to the source via control panel 126 by line 156, and the electric motor 112a, driving fan 112, is connected to the control panel 126 by way of line 158.

Since the system comprises a reversible refrigeration system, the indoor coil 12 and the outdoor coil 14 must operate as evaporator and condenser coils alternately and respectively when the system is under cooling and heating modes. Expansion means must be provided on the inlet sides of those coils when acting as evaporators, as well as chiller 16, to effect expansion of the high pressure liquid refrigerant within the coils for the purpose of absorbing heat.For simplicity, the expansion devices ae not shown, and likewise, while the subcooler 21 is illustrated as being associated with the indoor coil and functioning only when the indoor coil acts as a condenser, appropriately the subcooler may be incorporated within the system such that it will function to subcool liquid refrigerant delivered to the indoor coil 12 under cooling mode with that coil functioning as an evaporator rather than a condenser.The control panel 126 is of conventional design and functions to compare the temperature of the liquid medium 22 stored within the storage tank 18 and the temperature of the ambient air as provided by signals from temperature sensors 134 and 136 respectively for in turn controlling the condition of solenoid operated control valves 107 and 108 for controlling the flow of primary loop refrigerant through outdoor coil 14 and solar assist chiller or evaporator 16. In the illustrated embodiment of the invention, the control panel 126 comprises conventional circuitry including relays and the like for actuating selectively the reversing valve 24 and the solenoid operated control valves 86, 92, 107 and 108 in response to signals emanating from the temperature sensors 134, 136 and 138 and transmitted to that panel.

The operation of the improved air source heat pump system of the present invention may be seen under various modes by reference to Figures 2-5.

Turning first to Figure 2, the system is shown under a heating mode, wherein the indoor coil 12 is functioning as a condenser, the outdoor coil 14 is not in operation, fan 110 is turned off, solar evaporator or chiller 16 is functioning as the evaporator coil absorbing heat from the heat sink storage medium 22 as received from the solar collectors 20 and the compressor 10 is acting as a single stage compressor. The operation is automatically controlled.Thermobulb 138 associated with the room or other controlled environment, senses the temperature of the air passing over the indoor coil 12, denotes the necessity to heat the environment and initiates a control signal from the control panel 126 to the four way reversing valve 24 by way of control line 154 to keep the control valve in position such that conduits or lines 64 and 66 are connected together, such that low pressure refrigerant vapor discharging from the solar assist evaporator 16 is directed to inlets 46 and 48 of the left cylinder head 26 cylinders 34 and 36, and by way of inlet 52 at the low side of the right cylinder head 28 for both cylinders 42 and 44.The four way reversing valve 24 further makes a connection between lines 60 and 74 such that compressed refrigerant vapor or gas under single stage compression is provided to the indoor coil 12 acting as the condenser for the primary loop, the refrigerant being compressed by the individual cylinders 34, 36, 42 and 44 and discharging in parallel by way of outlets 54. 56 and 58 and passing by way of manifold 72 for outlets 54 and 58 through line 74 with outlet 52 discharging compressed refrigerant vapor into line 82 leading to line 74 downstream of the check valve 76.

Further, the control panel senses the temperature of the ambient air adjacent the outdoor coil 14 by way of temperature sensor 136 and senses the temperature of the heat sink media 22 within the storage tank 18 by means of temperature sensor 134, and signals are sent via lines 142 and 140 respectively to the comparator of control panel 126.

Under the mode of Figure 2, the temperature of the heat sink media such as glycol 22 within the storage tank 18 is warmer than the ambient passing over the outdoor coil 14 by a predetermined amount, and a control signal is sent via line 147 from control panel 126 to the solenoid operated control valve 107 within line 65. The solenoid operated control valves of the illustrated embodiment are of the normally closed type and open when energized, therefore, valve 107 is energized while valve 108 is not. The refrigerant within the primary loop is prevented from flowing through line 64 and the outdoor coil 14 and is bypassed to the solar evaporator or chiller 16.

At the same time, pump 122 and solenoid operated valve 124 are energized so that the glycol is circulated in a closed loop including tank 18 and solar evaporator 16; current emanating from the control panel 126 and passing to elements 122 and 124 via lines 130 and 128 respectively. Further, since the ambient temperature is relatively high, there is not necessity for operating the reciprocating compressor 10 in multi-stage mode, and therefore, the control panel 126 does not energize solenoid operated control valves 86 and 92, and the system subcooler is not operated. The heat load of indoor coil 12 is adequately supplied in this mode by chiller 16.

Turning next to Figure 3, the heat pump system is still operating under the heating mode, and at relatively high ambient temperature. However, the temperature of the glycol 22 within storage tank 18 has dropped below the predetermined differential between that temperature and the temperature of the ambient air passing over the outdoor coil 14 as sensed by temperature sensor 136.

Temperature sensor 138 associated with the indoor coil 12 is still calling for heat, and therefore the indoor coil must function as a condenser, thus the four way reversing valve 24 remains under under the same condition of the operation as in Figure 2. The control panel 126 terminates the energization of the solenoid operated control valve 107 which then automatically closes and the control panel energizes the solenoid operated control valve 108 placing the outdoor coil 14 in the primary loop in place of the solar evaporator 16. At the same time, current passes via line 156 from panel 126 to the fan motor 110a energizing that motor, causing forced air circulation over outdoor coil 14. At the same time, pump 122 and solenoid operated valve 124 are de-energized, terminating circulation of glycol from the storage tank 18 to the solar evaporator 16.Heat, however, is continuously absorbed by the solar collectors 20 as shown by radiation 114, assuming proper solar conditions, and the temperature of the glycol is raised. Thus, even though there is no solar energy applied to the heat pump system, solar energy is being stored within tank 18 and the temperature of the glycol is increasing. While not shown, the system can be operated such that the solar evaporator may act in addition to and in parallel with the air source evaporator 14. Both solenoid operated control valves 107 and 108 are energized to permit primary loop refrigerant to flow through lines 64 and 65 simultaneously, picking up heat both from the storage tank 18 and from the ambient air passing over the outdoor coil 14.

As the ambient temperature drops, and assuming that there is no solar energy augment because of the low temperature of the glycol 22 within the storage tank 18, and further assuming that the environment being conditioned is calling for additional heat by way of temperature sensor 138, the automatically controlled air source heat pump system of the present invention reaches a predetermined but typical volumetric efficiency switchover point which may be 25%, as mentioned previously. At that point, the system automatically shifts to the mode of operation illustrated in Figure 4. The control panel 126 energizes the solenoid operated control valves 86, 92 and 108 upon energization of control valve 86, line 84 opens from manifold 72 to the inlet 50 on the low side of the left cylinder head 26 for cylinder 36 of compressor 10.Further, the control panel 126 acts to energize the solenoid operated control valve 92 with the subcooler in operation, the vaporized refrigerant from the return line 96 passes to line 84 leading from the manifold 72 to inlet 50 on the low side of cylinder 36 of the left cylinder head 26 of compressor 10. Under this mode of operation, cylinders 34, 42 and 44 are operating to provide the first stage of compression for the refrigerant, while cylinder 36 acts to compress the first stage of refrigerant vapor discharge in a second stage of compression.

Assuming 25% volumetric efficiency, with the compressor staged there will be three low side cylir:ilers operating at a volumetric efficiency of approximately 75% resulting in 2.25 flow units in comparison to one flow unit. Thus, the compressor operates at 2.25 times the volume of flow that it would have with all cylinders operating single stage at a 12 to 1 compression ratio, greatly improving system efficiency in this mode under such low ambient conditions.

Check valve 76 closes to prevent the high pressure second stage discharge flow from line 82 to reverse in line 74 towards manifold 72 from point 84 where line 82 meets line 74 upstream of the four way reversing valve 24.

The four way reversing valve 24 remains in the condition of Figures 2 and 3 as the system is still under heating mode. The second stage discharge by way of outlet 56 through line 82 passes to the four way reversing valve 24 and thence to line 60 leading to the indoor coil 12 which is still acting as the system condenser.

Further, the subcooler efficiently discharges its refrigerant vapor which is at a higher pressure than the pressure of the return vapor from the air source evaporator or outdoor coil 14 to compressor inlets 46, 48 and 52. The present invention advantageously meets the necessity of maintaining load reversal on the wrist pins of the reciprocating compressor pistons and connecting rod assembly, since cylinder 36 vents the crank case. The compressor crank case and resulting wrist pins are subjected to low side pressure, which is no problem under single stage operation, but when the compressor 10 is automatically staged, the crank case on the low side for cylinder 36 will be subjected to intermediate pressure (first stage discharge pressure from line 85) and the wrist pins and cylinders 34, 42 and 44 will still undergo proper reversals of loading.The cylinder 36 will also operate with proper wrist pin loading reversal in that cylinder 36 suction pressure will be applied at the wrist pin of cylinder 36. This permits the compressor 10 to be manufactured without expensive, complex and unreliable needle type wrist pin bearings.

It should be noted additionally, that under this mode of operation, the branch line 70 no longer feeds the low pressure refrigerant vapor from the discharge side of the outdoor coil 14 to the low side of cylinder 36, since vapor enters the low side of cylinder 36 by way of inlet 50 and is at a higher pressure than the vapor within line 70. The check valve 88 prevents reverse flow from the low side (first stage discharge) of cylinder 36 into the line 66.

The single, reliable and efficient heat pump system as illustrated, with automatic staging, provides a fundamental advantage over prior art heat pump systems. Automatic staging allows the subcooling loop to be incorporated automatically when it is most needed, and the subcooler automatically feeds the return vaporized refrigerant to the second stage low side of cylinder 36 by way of inlet 50.

Turning next to Figure 5, the heat pump system is illustrated under a cooling mode where the outdoor coil 14 functions as an air source condenser. The room or other environment being conditioned by indoor coil 12 now calls for cooling of that environment and upon receipt of that signal by the control panel 126 through line 144 from temperature sensor 138, the control panel 126 directs the four way reversing valve 24 to shift to the condition shown in Figure 5 by current application to line 154. Typically, the four way reversing valve 24 may be a spring biased solenoid operated valve such that deenergization of the valve causes lines 64 and 66 to be connected and lines 74 and 60, while upon energization, Figure 5, lines 74 and 64 are in fluid communication and lines 66 and 60 are in fluid communication, as shown.

This functions to direct the high pressure refrigerant at the discharge side of the compressor to the outdoor coil 14 which functions as an air source condenser, the vapor condensing to a liquid for passage to the indoor coil 12 which functions as an evaporator coil for the environment or area to be conditioned. As shown, the compressor 10 is operating with all four cylinders in parallel in single stage similar to the operation of Figure 3 except in that case the system was operating under high ambient heating mode with heat exchanger 14 forming the air source evaporator. Under cooling mode conditions, solenoid valves 107, 86, 92 and 124 are off and solenoid valve 108 is on.However, in an alternate circuit arrangement, the subcooler 21 may be employed for subcooling the liquid refrigerant emanating from outdoor coil 14 and feeding indoor coil 12 for absorbing heat from the environment being conditioned.

From the above, it may be seen that the solar augmented heat pump system of the present invention involves a control system which permits the reciprocating compressor to automatically stage itself on demand.

While the reciprocating compressor 10 is illustrated as having four cylinders which operate in parallel in single stage and when double staged only one of the four cylinders acts to compress the vapor in the second stage, it is obvious that more than four cylinders may be employed, or where four cylinders ae employed, two may operate as first stage cylinders and the other two as second stage cylinders.

Further, under the staged mode of compressor operation, it is possible that the solar assist evaporator 16 may have it discharge along with that of the subcooler 21 fed into the intermediate pressure point of the staged compressor, that is, the intake of the second stage cylinders. It is to be noted that the terms high and low side denote high and low pressure conditions for the vapor at the compressor.

WHAT WE CLAIM IS: ! An air source heat pump system com pnslng: a first indoor heat exchange coil 12, a second outdoor heat exchange coil 14, a multi-cylinder reciprocating compressor 10, first conduit means carrying refrigerant, said first conduit means including a reversing valve 24 and connecting said coils 12, 14 and said compressor 10 in a primary closed series loop, said reversing valve 24 functioning to cause said indoor 12 and outdoor 14 coils to operate alternately as evaporator and condenser, characterized by:: a third heat exchange coil 16, said first conduit means further including means for connecting said third heat exchange coil 16 across said outdoor coil 14, control valve means 107, 108 within said conduit means for selectively controlling refrigerant flow through said primary closed loop to said second 14 and third 16 heat exchange coils, solar energy heat supply means 18, 120 for supplying thermal energy to said third heat exchange coil 16, means 136 for sensing the temperature of the ambient air passing over said outdoor coil 14, and control means 126 for operating said control valve means 107, 108 in response to said temperature sensing means;; whereby, thermal energy input to said heat pump system during heating mode may be supplied selectively by said second heat exchange coil acting as an air source evaporator or said third heat exchanger coil via said solar energy supply means.

2. The heat pump system as claimed in claim 1, wherein said solar energy heat supply means comprises a storage tank 18, a heat sink fluid 22 being within said storage tank, means for selectively circulating said stored heat sink fluid to said third heat exchange coil 16 for thermal absorption by the primary loop refrigerant with said third heat exchange coil 16 acting as solar evaporator, and means 20, 116 for supplying solar energy supplied heat to said storage tank 18 for heating said heat sink fluid 22 to increase the temperature of the same.

3. The heat pump system as claimed in claim 2, wherein said solar energy heat supply means for heating of said heat sink fluid comprises a solar collector 20, a fourth heat exchange coil 118 within said storage tank, and in thermal contact with said heat sink fluid 22, and second conduit means 116 for connecting said storage tank 22 and

**WARNING** end of DESC field may overlap start of CLMS **.

Claims

**WARNING** start of CLMS field may overlap end of DESC **.

second stage low side of cylinder 36 by way of inlet 50.

Turning next to Figure 5, the heat pump system is illustrated under a cooling mode where the outdoor coil 14 functions as an air source condenser. The room or other environment being conditioned by indoor coil 12 now calls for cooling of that environment and upon receipt of that signal by the control panel 126 through line 144 from temperature sensor 138, the control panel 126 directs the four way reversing valve 24 to shift to the condition shown in Figure 5 by current application to line 154. Typically, the four way reversing valve 24 may be a spring biased solenoid operated valve such that deenergization of the valve causes lines 64 and 66 to be connected and lines 74 and 60, while upon energization, Figure 5, lines 74 and 64 are in fluid communication and lines 66 and 60 are in fluid communication, as shown.

This functions to direct the high pressure refrigerant at the discharge side of the compressor to the outdoor coil 14 which functions as an air source condenser, the vapor condensing to a liquid for passage to the indoor coil 12 which functions as an evaporator coil for the environment or area to be conditioned. As shown, the compressor 10 is operating with all four cylinders in parallel in single stage similar to the operation of Figure 3 except in that case the system was operating under high ambient heating mode with heat exchanger 14 forming the air source evaporator. Under cooling mode conditions, solenoid valves 107, 86, 92 and 124 are off and solenoid valve 108 is on.However, in an alternate circuit arrangement, the subcooler 21 may be employed for subcooling the liquid refrigerant emanating from outdoor coil 14 and feeding indoor coil 12 for absorbing heat from the environment being conditioned.

From the above, it may be seen that the solar augmented heat pump system of the present invention involves a control system which permits the reciprocating compressor to automatically stage itself on demand.

While the reciprocating compressor 10 is illustrated as having four cylinders which operate in parallel in single stage and when double staged only one of the four cylinders acts to compress the vapor in the second stage, it is obvious that more than four cylinders may be employed, or where four cylinders ae employed, two may operate as first stage cylinders and the other two as second stage cylinders.

Further, under the staged mode of compressor operation, it is possible that the solar assist evaporator 16 may have it discharge along with that of the subcooler 21 fed into the intermediate pressure point of the staged compressor, that is, the intake of the second stage cylinders. It is to be noted that the terms high and low side denote high and low pressure conditions for the vapor at the compressor.

WHAT WE CLAIM IS: ! An air source heat pump system com pnslng: a first indoor heat exchange coil 12, a second outdoor heat exchange coil 14, a multi-cylinder reciprocating compressor 10, first conduit means carrying refrigerant, said first conduit means including a reversing valve 24 and connecting said coils 12, 14 and said compressor 10 in a primary closed series loop, said reversing valve 24 functioning to cause said indoor 12 and outdoor 14 coils to operate alternately as evaporator and condenser, characterized by:: a third heat exchange coil 16, said first conduit means further including means for connecting said third heat exchange coil 16 across said outdoor coil 14, control valve means 107, 108 within said conduit means for selectively controlling refrigerant flow through said primary closed loop to said second 14 and third 16 heat exchange coils, solar energy heat supply means 18, 120 for supplying thermal energy to said third heat exchange coil 16, means 136 for sensing the temperature of the ambient air passing over said outdoor coil 14, and control means 126 for operating said control valve means 107, 108 in response to said temperature sensing means;; whereby, thermal energy input to said heat pump system during heating mode may be supplied selectively by said second heat exchange coil acting as an air source evaporator or said third heat exchanger coil via said solar energy supply means.
2. The heat pump system as claimed in claim 1, wherein said solar energy heat supply means comprises a storage tank 18, a heat sink fluid 22 being within said storage tank, means for selectively circulating said stored heat sink fluid to said third heat exchange coil 16 for thermal absorption by the primary loop refrigerant with said third heat exchange coil 16 acting as solar evaporator, and means 20, 116 for supplying solar energy supplied heat to said storage tank 18 for heating said heat sink fluid 22 to increase the temperature of the same.
3. The heat pump system as claimed in claim 2, wherein said solar energy heat supply means for heating of said heat sink fluid comprises a solar collector 20, a fourth heat exchange coil 118 within said storage tank, and in thermal contact with said heat sink fluid 22, and second conduit means 116 for connecting said storage tank 22 and

carrying a circulating heat exchange fluid therein such that solar energy impinging on said collector 20 is transmitted to said storage tank coil 118 for heating said heat sink fluid 22.
4. The heat pump system as claimed in claim 2, wherein said heat sink fluid 22 comprises glycol and said means for circulating said glycol between said storage tank 18 and said third heat exchange coil 16 comprises third conduit means 120 for communsaid storage tank 18 to said third heat exchange coil 16, a solenoid operated control valve 124 within said third conduit means 120 and pump means 122 within said third conduit means 120 and intermediate of said storage tank 18 and said third heat exchange coil 16 for circulating said glycol therebetween.
5. The heat pump system as claimed in claim 3, wherein said heat sink fluid 22 comprises glycol and said means for circulating said glycol between said storage tanok 18 and said third heat exchange coil 16 comprises third conduit means 120 for communicating said storage tank 18 to said third heat exchange coil 16, a solenoid operated control valve 124 within said third conduit means 120 and pump means 122 within said third conduit means 120 and intermediate of said storage tank 18 and said third heat exchange coil 16 for circulating said glycol therebetween.
6. The heat pump system as claimed in claim 1, wherein said reciprocating compressor comprises a plurality of cylinders 34, 36, 42, 44, and said system control means comprises means 126, 86 responsive to said ambient air temperature sensing means 136 for automatically staging said compressor cylinders at low ambient temperature to increase refrigerant flow rate through said compressor.
7. The heat pump system as claimed in claim 4, wherein said reciprocating compressor comprises a plurality of cylinders, 34, 36, 42, 44, and said system control means comprises means 126, 86 responsive to said ambient air temperature sensing means 136 for automatically staging said compressor cylinders at low ambient temperature to increase refrigerant flow rate through said compressor.
8. The heat pump system as claimed in claim 5, wherein said reciprocating compressor comprises a plurality of cylinders, 34, 36, 42, 44, and said system control means comprises means 126, 86 responsive to said ambient air temperature sensing means 136 for automatically staging said compressor cylinders at low ambient temperature to increase refrigerant flow rate through said compressor.
9. The heat pump system as claimed in claim 6, wherein said compressor 10 comprises a first 26 and a second 28 cylinder head, each cylinder head comprising two cylinders 34, 36 and 42, 44, said first cylinder head 26 including first manifold means 23, 25 separating said cylinders 34, 36 and defining low 30, 31 and high 32, 33 pressure sides for respective cylinders 34, 36 said second cylinder head 28 comprising second manifold means 45 defining commonly, low 40 and high 38 pressure sides for both cylinders 42, 44 said first cylinder head 26 including a first inlet 46 to the low pressure side 30 of one cylinder 34 and a second inlet 48 to the low pressure side 31 of the other cylinder 36, and said second cylinder head 28 comprising a third inlet 52 common to the low pressure 40 side of both cylinders 42, 44 said first cylinder head 26 comprising first and second outlets 58, 56 respectively for the individual cylinders, said second cylinder head 28 comprising a third outlet 54 common to both cylinders 42, 44, a fourth inlet 50 for the other 36 of the cylinders of said first cylinder head 26 and wherein said first conduit means comprising means defining an outlet manifold 72 connected to the outlet 58 of said first cylinder head cylinder 34 having a single inlet 46, and to the outlet 54 of said second cylinder head common to both cylinders, conduit means 74 for connecting said outlet manifold 72 to said reversing valve 24 and parallel with the outlet 56 of said first cylinder head cylinder 36 having dual low side inlets, means for connecting said outlet manifold 72 to said second inlet 50 for said other cylinder 36 of said first cylinder head 26, second control valve means 86 within said conduit means 84 connecting said outlet manifold to said second inlet 50 of said other 36 cylinder of said first cylinder head 26, a first check valve 76 within said conduit 74 leading from said outlet manifold 72 to said reversing valve 24 and a second check valve 88 within said conduit means 70 leading from said reversing valve 24 to said first inlet 48 to said other cylinder 36 of said first cylinder head 26, such that upon energization of said second control valve means 86, said one 34 cylinder of said first cylinder head and both cylinders 42, 44 of said second cylinder head 28 operate in first stage compression and said other cylinder 36 of said first cylinder head 26 operates in second stage with said second check valve isolating said compressor first and second stages.
10. The heat pump system as claimed in claim 7, wherein said compressor 10 comprises a first 26 and a second 28 cylinder head, each cylinder head comprising two cylinders 34, 36 and 42, 44 said first cylinder head 26 including first manifold means 23, 25 separating said cylinders 34, 36 and defining low 30, 31 and high 32, 33 pressure sides for respective cylinders 34, 36 said second cylinder head 28 comprising second manifold means 48 defining commonly, low 40 and high 38 pressure sides for both cylinders 42, 44 said first cylinder head 26 including a first inlet 46 to the low pressure side 30 of one cylinder 34 and a second inlet 48 to the low pressure side 31 of the other cylinder 36, and said second cylinder head 28 comprising a third inlet 52 common to the low pressure 40 side of both cylinders 42, 44 said first cylinder head 26 comprising first and second outlets 58, 56 respectively for the individual cylinders, said second cylinder head 28 comprising a third outlet 54 common to both cylinders 42, 44, a fourth inlet 50 for the other 36 of the cylinders of said first cylinder head 26 and wherein said first conduit means comprising means defining an outlet manifold 72 connected to the outlet 58 of said first cylinder head cylinder 34 having a single inlet 46, and to the outlet 54 of said second cylinder head common to both cylinders, conduit means 74 for connecting said outlet manifold 72 to said reversing valve 24 and parallel with the outlet 56 of said first cylinder head cylinder 36 having dual low side inlets, means for connecting said outlet manifold 72 to said second inlet 50 for said other cylinder 36 of said cylinder head 26, second control valve means 86 within said conduit means 84 connecting said outlet manifold to said inlet 50 of said other 36 cylinder of said first cylinder head 26, a first check valve 76 within said conduit 74 leading from said outlet manifold 72 to said reversing valve 24 and a second check valve 88 within said conduit means 70 leading from said reversing valve 24 to said first inlet 48 to said other cylinder 36 of said first cylinder head 26, such that upon energization of said second control valve means 86, said one 34 cylinder of said first cylinder head and both cylinders 42, 44 of said second cylinder head 28 operate in first stage compression and said other cylinder 36 of said first cylinder head 26 operates in second stage with said second check valve isolating said compressor first and second stages.
11. The heat pump system as claimed in claim 9, wherein said system further comprises a subcooler 21 operatively connected with said first conduit means between said indoor and outdoor coils and said subcooler includes a return line connecting to said first conduit means between said outlet manifold 72 and said fourth inlet 50 for said other cylinder 36 of said first cylinder head 26 downstream of said second control valve means 86 such that during multi-stage compression the refrigerant vapor from said subcooler 21 at intermediate pressure is directed commonly with the first stage discharge to the fourth inlet 50 at the low side of said other cylinder 36 constituting the second stage of said reciprocating compressor.
12. The heat pump system as claim in claim 10, wherein said system further comprises a subcooler 21 operatively connected within said first conduit means between said indoor and outdoor coils and said subcooler includes a return line connecting to said first conduit means between said outlet manifold 72 and said fourth inlet 50 for said other cylinder 36 of said first cylinder head 26 downstream of said second control valve means 86 such that during multi-stage compression the refrigerant vapor from said subcooler 21 at intermediate pressure is directed commonly with the first stage discharge to the fourth inlet 50 at the low side of said other cylinder 36 constituting the second stage of said reciprocating compressor.
13. An air source heat pump system substantially as hereinbefore described with reference to the accompanying drawings.