|Publication number||US3301002 A|
|Publication date||Jan 31, 1967|
|Filing date||Apr 26, 1965|
|Priority date||Apr 26, 1965|
|Publication number||US 3301002 A, US 3301002A, US-A-3301002, US3301002 A, US3301002A|
|Inventors||Mcgrath William L|
|Original Assignee||Carrier Corp|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (11), Referenced by (61), Classifications (21)|
|External Links: USPTO, USPTO Assignment, Espacenet|
Jan. 31, 1967 w. L. MOGRATH 3,301,002
CONDI TIONI NG APPARATUS Filed April 26, 1965 5 heets-Sheet 1 INVENTOR. WILLIAM L. MC GRATH.
-1 v BYWZY7%W ATTORNEY.
Jan. 31, 1967 w. L. MCGRATH (JUNIJI 'I 1 UN 1 N0 APPARATUS Filed April 26, 1965 3 Sheets-Sheet 2 FIG. 2
mvuvro; WILLIAM L. m: GRA
ATTORNE 1967 I w. L. MCGRATH I ,0 2
CONDITIONING APPARATUS Filed April 26, 1965 3 Sheets-Sheet 5 INVENTOR. WILLIAM L MC GRATH.
United States Patent C) 3,301,002 CONDITIONING APPARATUS William L. McGrath, Syracuse, N.Y., assignor to Carrier Corporation, Syracuse, N .Y., a corporation of Delaware Filed Apr. 26, 1965, Ser. No. 450,833 15 Claims. (Cl. 62175) This invention relates to a refrigeration apparatus. and more particularly, to a refrigeration apparatus adapted to heat water.
Modification of a refrigeration system of the type having an air cooled outdoor heat exchange coil to enable the system to provide hot water during system operation requires some arrangement for maintaining a minimum condensing temperature under all ambient temperature conditions or the addition of supplementary heating means for the water at relatively high cost. The loss in system efiiciency during most operating conditions from the artificially high condensing temperature imposed on the system increases operating cost of the apparatus. In addition, the vagaries in outdoor conditions and in the demands imposed upon the system necessitates. in most modified systems, that standby or supplemental water heating means be available.
It is a principal object of the present invention to provide a new and improved apparatus for conditioning an enclosure and heating water.
It is a further obiect of the present invention to provide an apparatus for heating water which includes a relatively small refrigerant compressor and condenser incorporated into a primary refrigeration system so as to utilize one of the primary refrigeration system heat exchange coils as an evaporator.
It is an object of the present invention to provide a reverse cycle refrigeration system having a sec-nd compressor and heat exchange coil interconnected therewith so as to form a second refrigeration system adapted to heat water.
It is an object of the present invention to provide a refrigeration apparatus utilizing a pair of staged compressors with means for insuring an adequate supply of lubricant for each compressor.
, It is an object of the present invention to provide accessory refrigeration apparatus for an air conditioning system which salvages heat rejected by the air conditioning system for the purpose of heating service water.
This invention relates to conditioning apparatus, the combination comprising first refrigerant circuit means for conditioning a first fluid medium, the first circuit means including a compressor, a first heat exchanger, expansion means, and a second heat exchanger; and second refrigerant circuit means adapted to condition a second fluid medium; the second circuit means including. a second compressor, -a condenser arranged in heat exchange relation with the second fluid medium, and means connecting the second compressor and the condenser with the first refrigeration circuit means so as to operatively incorporate one of the first and second heat exchangers in the second circuit means.
Other objects and advantages of the present invention will be apparent from the ensuing description and drawings in which:
FIGURE 1 is a diagrammatic view showing a refrigeration system according to the present invention;
FIGURE 2 is a diagrammatic view of a modified form of the refrigeration system shown in FIGURE 1; and
FIGURE 3 is a diagrammatic view showing a reverse cycle refrigeration system according to this invention.
Referring particularly to FIGURE 1 of the drawings, the refrigeration system shown thereatincludes compressor 1, heat exchanger 3, condenser coil 2, expansion I valve 4 and evaporator coil 6, suitably interconnected in source of water to be heated. Refrigerant line 17 connects the lower part of vessel 9 with the system liquid line 23.
Coil 32 of heat exchanger 12 is connected by means of line 10 with the downstream side of coil 2. Line 10- in- 'cludes a capillary portion 14 serving to meter liquid refrigerant flow between the coils 2, 32 as will he more an parent hereinafter. A pressure cont-rolling device such as a pressure relief valve may be contemplated in place of capillary 14.
Line 18 connects coil 32 with the discharge'side of a relatively small compressor 19. Compressors 1, 19 are preferably hermetic reciprocating type compressors. Other suitable compressors such as rotary and nonhermetic type compressors may be contemplated.
The suction side of compressor 19 is connected through lines 20, 21 and separator 22 with coil 2 upstream of line 10. .The secondary or parasite refrigeration circuit formed includes compressor 19, coil 32, capillary 14, and coil 2 of the primary refrigeration circuit.
Heat exchanger 12 includes a housing 33 connected to the discharge side of circulating pump 24 by conduit 26. Conduit 30 connects conduit 26 withcoil 16 of heat ex changer 3. Pump 24, when energized, circulateswater to be heated from storage tank 28 or from the outside source through housing 33 via conduits 26, 27. Check valve 25 prevents direct flow of water to storage tank 28 through conduit 29 from the outside source. Heated water is drawn from tank 28 through conduit 31. If
I desired, an auxiliary heating means such as a resistance door fan 8 at a predetermined temperature condition of the water in storage tank 28. The relatively hot gaseous refrigerant discharged from compressor 19 passes through line 18 into coil 32, the thermal interchange between coil 32 and the water circulated thereabout by pump 24 heat ing the water while condensing refrigerant in coil 32.
Condensed refrigerant from coil 32 passes by means of line 10 and capillary 14 to the primary circuit. Capillary 14 serves to expand the refrigerant in line 10. Gaseous refrigerant returns through line 21, separator 22, andv line 20 to the suction side of compressor 19'.
Where the primary refrigeration system is simultaneously operated, a portion of the gaseous refrigerant discharge from compressor 1 is condensed in vessel 9 of heat exchanger 3 by water flowing through coil 16. The warmed water emitted from coil 16 flows through conduits 30, 2-6 to heat exchanger 12 where further heating thereof is effected by the secondary refrigeration system in the manner explained heretofore. Condensed refrigerant accumulated in the bottom of vessel 9 passes through line 17 to the system liquid line 23 where it mixes with refrigerant from condenser coil 2. Gaseous refrigerant in vessel 9 flows through line 15 to coil 2 .where a portion thereof passes through lines 21, 20 to the suction side of compressor 19, the remainder flowing through coil 2, expansion valve 4, and evaporator coil 6 to compressor 1 in the usual manner. By extracting refrigerant from the primary circuit coil 2, applicant is able to effectively desuperheat the refrigerant for use in the secondary refrigeration circuit.
Where the primary refrigeration system is inoperative, the flow of refrigerant through condenser coil 2 between lines 10, 21 is reversed from that occurring during operation of the primary refrigeration system. Condenser coil 2 in this circumstance functions as the evaporator for the secondary circuit.
Heated water is stored in tank 28 until such time as demand therefor is made. Pressure available from the source of Water forces the heated Water from tank 28 upon opening of conduit 31.
Line 60 connects the lower portion of separator 22 with the sump of compressor 19. Line 61, joined to separator 22 at a selected lubricant level and having a capillary portion 62, is connected to the suction side of compressor 1.
Lubricant entrained in the stream of refrigerant flowing through conduits 20, 21 to compressor 19 accumulates in the lower portion of separator 22 from whence it may flow through line 60 to the sump of compressor 19 thereby insuring an adequate supply of lubricant for compressor 19. Should the lubricant level in separator 22 rise above line 61, the lubricant is drawn through line 61 and capillary 62 into the stream of suction gas flowing to compressor 1. The lubricant entrained in the refrigerant gas stream may, during the compression process, deposit in the crankcase of either compressor 1 or compressor 19, or in the lower portion of separator 22 as explained heretofore.
Where only one of the compressors 1, 19 is operated, no substantial transfer of lubricant from one compressor to the other transpires. If desired, the speed of fan 8 may be varied to maintain a predetermined minimum pressure in coil 2, in a manner well-known in the art.
Referring to FIGURE 2 of the drawings wherein like numerals identify like parts, line 21 is arranged to draw refrigerant from the primary refrigeration system upstream of condenser coil 2. To effect the desired desuperheating of the refrigerant prior to the introduction of the refrigerant into compressor 19 and to extract heat at the temperature of coil 2, a portion 28 of line 20 is disposed in housing 33 of heat exchanger 12 in heat exchange relation with the water to be heated. The arrangement of the remaining portions of the system of the FIGURE 2 embodiment and the operation and function thereof is the same as that described heretofore.
Referring particularly to FIGURE 3 of the drawings, an arrangement for heating water by means of a secondary refrigeration circuit which utilizes a portion of a reverse cycle (heat pump) refrigeration circuit is therein shown. The primary refrigeration circuit includes compressor 65, reversing valve 66, indoor coil 67, expansion valves 68, 69, and outdoor coil 70 suitably coupled together. Indoor and outdoor fans 72, 73 are provided.
Where reversing valve 66 is disposed in the position shown in solid line in FIGURE 3 of the drawings, the system, upon energization of compressor 65, cools, the refrigerant discharged from compressor 65 being routed by reversing valve 66 through outdoor coil 70, expansion valve 68 into indoor coil 67, the refrigerant returning through reversing valve 66 to the suction side of compressor '65. During the cooling cycle check valve 74 bypasses refrigerant expansion valve 69.
When reversing valve 66 is disposed in the dotted line position shown in FIGURE 3 of the drawings, refrigerant discharged in compressor 65 is routed by valve 66 through indoor coil 67, expansion valve 69 into outdoor coil 70, the refrigerant returning through valve 66 to the suction side of compressor 65. Check valve 75 bypasses expansion valve 69. The system accordingly heats Heat exchanger 78 includes a coil 88 connected by line 79 with closed refrigerant separating vessel 76. Line 77 connects the upper portion of vessel 76 with discharge line 80 of compressor 65. Line 86 connects the lower portion of vessel 76 with the primary refrigeration system liquid line 98. Relief valve 81 in line 79 permits flow of refrigerant when pressures in coil 88 exceedpressures in discharge line 80' by a predetermined amount.
Line 82 connects coil 88 to the discharge side of a relatively small compressor 83. Lines 84, 85 connect the suction side of compressor 83 through separator 22' with dis charge line 88 of compressor 65. Line 87 joins line 85 with the primary refrigeration circuit liquid line 98. Expansion valve 90 in line 87 regulates communication between lines 87, 85 in response to thermal conditions at the suction side of compressor 83.
Pump 91 having an inlet side connected with a suitable source of water, circulates water through conduit 92, housing 89 of heat exchanger 78, and conduit 94 to storage tank 93. Conduit 97 connects the inlet side of pump 91 with tank 93. Check valve 95 prevents direct flow of Water from the source of water through conduit 97 into tank 93.
Suitable thermostat controlling means (not shown) are provided for energizing compressor 83, pump 91, and outdoor fan 73 at a predetermined temperature condition of the water in storage tank 93. Compressor 83 discharges relatively hot gaseous refrigerant through line 82 into coil 88. The thermal interchange between coil 88 and the water disposed thereabout heats the water while condensing refrigerant in coil 88. Refrigerant from coil 88 flows through valve 81 and line 79 into the vessel 76, gaseous refrigerant in vessel 76 passing through line 77 into the stream of gas discharged from compressor 65. Liquid refrigerant in vessel 76 passes through line 86 to the system liquid line 98. A portion of the gas discharging from compressor 65 passes through line 84, separator 22', and line 85 to compressor 83. Thermal expansion valve 98, responsive to the thermal conditions of the refrigerant in line 85, serves to desuperheat refrigerant flowing through line 85 to the suction side of compressor 83 by mixing controlled amounts of relatively high pressure liquid refrigerant from the primary circuit with the gaseous refrigerant in line 85.
The secondary refrigeration system may be operated to heat Water while the primary refrigeration system is inoperative. Where the primary refrigeration circuit is inoperative, reversing valve 66 is in the cooling cycle position. Gaseous refrigerant in vessel 76 passes through lines 77, 84, separator 22' and line 85 to the suction side of compressor 83. Liquid refrigerant in vessel 76 passes through lines 36, 98, expansion valve 69, outdoor coil 70, reversing valve 66, into lines 84, 85 and the suction side of the compressor 83 as described above.
The lubricant controlling arrangement comprised of separator 22', lubricant lines 60', 61' an capillary 62' is similar in operation to that described in conjunction with FIGURES 1 and 2.
While I have described preferred embodiments of the present invention, it is understood that this invention may be otherwise embodied within the scope of the following claims.
1. In a conditioning apparatus, the combination of first refrigerant circuit means for conditioning a first fluid medium, said first circuit means including a first compressor, a first heat exchanger, expansion means, and a second heat exchanger, and second refrigerant circuit means for conditioning a second fluid medium, said sec ond circuit means including a second compressor, a condenser arranged in heat exchange relation with said second fluid medium, and means connecting said second compressor and said condenser with said first circuit means so as to operatively incorporate one of said first and second heat exchangers in said second circuit means.
2. The apparatus according to claim 1 in which each of said first and second compressors have a lubricant sump, said connecting means including means for separating lubricant entrained in the refrigerant, a lubricant line connecting said lubricant separating means with one of said first and second compressor sumps, and lubricant metering means joining said lubricant separating means to the other of said first and second compressors.
3. The apparatus according to claim 1 in which said first circuit means includes a reversing valve between said first compressor and said first and second heat exchangers, first and second expansion valves operatively disposed between said first and said second heat exchangers, said connecting means including a first conduit connecting the suction side of said second compressor with said first compressor discharge side.
4. The apparatus according to claim 3 including means for controlling conditions of the refrigerant flowing through said first conduit to said second compressor.
5. The apparatus according to claim 4 in which said condition controlling means comprises a second conduit between said first conduit and a point in said first circuit between said first and second expansion valves, and a third expansion valve for regulating flow of refrigerant between said first and second conduits in response to refrigerant conditions at said second compressor suction side.
6. The apparatus according to claim 1 in which said connecting means incorporates at least part of said first heat exchanger in said second refrigerant circuit means.
7. The apparatus according to claim 6 in which said connecting means includes a conduit connecting said second compressor suction side with said first circuit means at a point between said first compressor and said first heat exchanger, a portion of said connecting means conduit being in heat exchange relation with said second fluid medium.
8. The apparatus according to claim 6 in which said connecting means includes a conduit connecting said second compressor suction side with said first circuit means heat exchanger downstream of the connection of said first compressor with said first heat exchanger.
9. The apparatus according to claim 1 including a second condenser in said first refrigerant circuit means between said first compressor and said first heat exchanger, said second condenser being in heat exchange relation with said second fluid medium upstream of said second refrigerant circuit means condenser, said first refrigerant circuit means including a refrigerant liquid line between said second condenser and a point between said first heat exchanger and said expansion means.
10. The apparatus according to claim 1 including a pump adapted when actuated to circulate second fluid medium in heat exchange relation with said condenser so that upon energization of said second compressor said second fluid medium is heated.
11. In combination: a first compressor, a first condenser serially connected to said first compressor discharge side, an evaporator serially connected to said first compressor suction side, and first expansion means serially connecting said condenser with said evaporator to form a closed refrigeration system; a second condenser disposed in heat exchange relation with a source of water to be heated, a second compressor, said second condenser being serially connected with said second compressor discharge, second expansion means connecting said second condenser with said refrigeration system between said condenser and said expansion means, and refrigerant conduit means connecting the suction side of said second compressor with said refrigeration system at a point between said first compressor discharge side and the outlet of said first condenser.
12. The combination according to claim 11 in which each of said first and second compressors have a lubricant storage sump, said conduit means including a lubricant collecting means, a first line connecting said collecting means with said second compressor sump, a second line joined to said collecting means at a selected lubricant level and connected to said first refrigeration system at a point between said first compressor and said evaporator, said second lubricant line including metering means.
13. The combination according to claim 12 in which a part of said conduit means is in heat exchange relation with the water to be heated.
14. The combination according to claim 11 including pump means for circulating water to be heated into heat exchange relation with said second condenser so that upon energization of said second compressor said water is heated.
15. In combination: a first compressor, an outdoor heat exchanger coil, an indoor heat exchanger coil, and a reversing valve effective in a first position to connect said first compressor discharge and suction sides to said outdoor and indoor coils respectively, and a second position to connect said first compressor discharge and suction sides to said indoor and outdoor coils respectively; first and second expansion valves serially connected between said indoor and outdoor coils, a second compressor, a condenser disposed in heat exchange relation with a supply of water and serially connected to said second compressor dis charge side, closed refrigerant separating vessel, pressure regulating means connecting said condenser to said vessel, a first line connecting the upper portion of said vessel with the discharge side of said first compressor, a second line connecting the lower portion of said vessel with a point between said first and second expansion valves, a third line connecting the suction side of said second compressor with the discharge side of said first compressor, and means for controlling the condition of the refrigerant admitted to said second compressor through said third line including a fourth line connected between said first and second expansion valves and a third expansion valve for permitting controlled amounts of refrigerant to flow from said fourth line into said third line in response to thermal conditions of the refrigerant in said first conduit.
References Cited by the Examiner UNITED STATES PATENTS 2,619,326 11/1952 McLenegen 62-238 2,632,306 3/1953 Ruff 62-238 2,739,453 3/ 1956 Webber 62-175 2,751,761 6/1956 Borgerd 62-238 2,841,962 7/ 1958 Richards 62-175 2,893,218 7/1959 Harnish 62-324 2,938,361 5/1960 McNatt 62-510 2,966,043 12/1960 Ross 62-510 3,074,249 1/ 1963 Henderson 62-510 3,077,088 2/ 1963 Japhet 62-510 3,184,926 5/1965 Blake 62r175 WILLIAM J. WYE, Primary Examiner.
|Cited Patent||Filing date||Publication date||Applicant||Title|
|US2619326 *||Nov 29, 1949||Nov 25, 1952||Gen Electric||Fluid heating system, including a heat pump|
|US2632306 *||Jan 5, 1951||Mar 24, 1953||V C Patterson & Associates Inc||Combined water heater and air conditioner of the heat pump type|
|US2739453 *||Apr 17, 1953||Mar 27, 1956||Webber Robert C||Explosion-proof low-high temperature system|
|US2751761 *||Oct 15, 1951||Jun 26, 1956||Whirlpool Seeger Corp||Combination heat pump and water heater|
|US2841962 *||Jan 23, 1957||Jul 8, 1958||H A Phillips||Return apparatus for a two-stage refrigeration system|
|US2893218 *||Feb 21, 1958||Jul 7, 1959||Borg Warner||Air conditioning systems|
|US2938361 *||Sep 13, 1957||May 31, 1960||Borg Warner||Reversible refrigerating system|
|US2966043 *||Aug 17, 1959||Dec 27, 1960||Wayland Phillips||Balanced circulating system for refrigeration|
|US3074249 *||Jun 15, 1960||Jan 22, 1963||Ray M Henderson||Refrigeration system and apparatus having a heating cycle and a cooling cycle|
|US3077088 *||Mar 21, 1962||Feb 12, 1963||Exchanger|
|US3184926 *||Oct 10, 1963||May 25, 1965||Ray Winther Company||Refrigeration system|
|Citing Patent||Filing date||Publication date||Applicant||Title|
|US3922876 *||Nov 21, 1974||Dec 2, 1975||Energy Conservation Unlimited||Energy conservation unit|
|US3976123 *||May 27, 1975||Aug 24, 1976||Davies Thomas D||Refrigeration system for controlled heating using rejected heat of an air conditioner|
|US3989183 *||Dec 4, 1974||Nov 2, 1976||Projectus Industripdukter Ab||Method and apparatus employing a heat pump for heating fluids in different flow circuits|
|US4000626 *||Feb 27, 1975||Jan 4, 1977||Webber Robert C||Liquid convection fluid heat exchanger for refrigeration circuit|
|US4030312 *||Apr 7, 1976||Jun 21, 1977||Shantzer-Wallin Corporation||Heat pumps with solar heat source|
|US4089667 *||Oct 27, 1976||May 16, 1978||Sun-Econ, Inc.||Heat extraction or reclamation apparatus for refrigerating and air conditioning systems|
|US4098092 *||Dec 9, 1976||Jul 4, 1978||Singh Kanwal N||Heating system with water heater recovery|
|US4143642 *||Sep 24, 1976||Mar 13, 1979||Vapor Corporation||High temperature thermal storage system utilizing solar energy units|
|US4179902 *||Jul 21, 1978||Dec 25, 1979||Paul Mueller Company||Hot water system and condensing unit therefor|
|US4194368 *||Oct 4, 1976||Mar 25, 1980||Borg-Warner Corporation||Combination split system air conditioner and compression cycle domestic hot water heating apparatus|
|US4199955 *||May 16, 1978||Apr 29, 1980||Sun-Econ, Inc.||Heat extraction or reclamation apparatus for refrigerating and air conditioning systems|
|US4226606 *||Oct 6, 1978||Oct 7, 1980||Air & Refrigeration Corp.||Waste heat recovery system|
|US4227382 *||Oct 4, 1978||Oct 14, 1980||General Electric Company||Split system air conditioner adapted to receive a water preheater|
|US4248059 *||Oct 26, 1978||Feb 3, 1981||Kenneth Fowler||Reversible-cycle closed-circuit refrigeration systems|
|US4254631 *||Sep 26, 1979||Mar 10, 1981||Carrier Corporation||Method and apparatus for satisfying heating and cooling demands and control therefor|
|US4270363 *||Apr 16, 1979||Jun 2, 1981||Schneider Metal Manufacturing Company||Refrigerating machine including energy conserving heat exchange apparatus|
|US4279574 *||Apr 23, 1979||Jul 21, 1981||Dresser Industries, Inc.||Energy recovery system|
|US4311498 *||Jul 14, 1980||Jan 19, 1982||Borg-Warner Corporation||Desuperheater control system in a refrigeration apparatus|
|US4314456 *||May 5, 1980||Feb 9, 1982||Borg-Warner Corporation||Refrigerant condensing system|
|US4316367 *||Oct 6, 1978||Feb 23, 1982||Yaeger Ronald J||Heat recovery and hot water circulation system|
|US4351159 *||Mar 5, 1981||Sep 28, 1982||General Electric Company||Energy recovery system|
|US4363221 *||Feb 17, 1981||Dec 14, 1982||Singh Kanwal N||Water heating system having a heat pump|
|US4373354 *||Sep 28, 1981||Feb 15, 1983||Trane Cac, Inc.||Combination discharge gas muffler and water heater|
|US4380156 *||Dec 11, 1981||Apr 19, 1983||Atlantic Richfield Company||Multiple source heat pump|
|US4386500 *||Apr 1, 1981||Jun 7, 1983||Boyd Sigafoose||Water heater heat exchange apparatus, kit, and method of installation|
|US4391104 *||Jan 15, 1982||Jul 5, 1983||The Trane Company||Cascade heat pump for heating water and for cooling or heating a comfort zone|
|US4474018 *||May 6, 1982||Oct 2, 1984||Arthur D. Little, Inc.||Heat pump system for production of domestic hot water|
|US4507938 *||Sep 8, 1983||Apr 2, 1985||Mitsubishi Denki Kabushiki Kaisha||System for air-conditioning and hot water supplying|
|US4798240 *||Mar 18, 1985||Jan 17, 1989||Gas Research Institute||Integrated space heating, air conditioning and potable water heating appliance|
|US4813239 *||Dec 19, 1986||Mar 21, 1989||Olson Hans E E||Method for defrosting and device for the implementation of said method|
|US5647225 *||Jun 14, 1995||Jul 15, 1997||Fischer; Harry C.||Multi-mode high efficiency air conditioning system|
|US5802864 *||Apr 1, 1997||Sep 8, 1998||Peregrine Industries, Inc.||Heat transfer system|
|US5901563 *||Dec 4, 1997||May 11, 1999||Peregrine Industries, Inc.||Heat exchanger for heat transfer system|
|US5953934 *||Jan 2, 1998||Sep 21, 1999||Mitsubishi Denki Kabushiki Kaisha||Refrigerant circulating apparatus and method of assembling a refrigerant circuit|
|US6202427 *||Mar 8, 1999||Mar 20, 2001||Yiue Feng Enterprise Co., Ltd.||Refrigerating air-conditioning system for reducing and reusing waste energy|
|US6253564||May 6, 1999||Jul 3, 2001||Peregrine Industries, Inc.||Heat transfer system|
|US8056348||Jun 3, 2005||Nov 15, 2011||Carrier Corporation||Refrigerant charge control in a heat pump system with water heater|
|US8074459||Apr 20, 2006||Dec 13, 2011||Carrier Corporation||Heat pump system having auxiliary water heating and heat exchanger bypass|
|US8079229||Oct 18, 2005||Dec 20, 2011||Carrier Corporation||Economized refrigerant vapor compression system for water heating|
|US8220531||Jun 3, 2005||Jul 17, 2012||Carrier Corporation||Heat pump system with auxiliary water heating|
|US8312734||Sep 26, 2008||Nov 20, 2012||Lewis Donald C||Cascading air-source heat pump|
|US8756943||Jul 12, 2012||Jun 24, 2014||Nordyne Llc||Refrigerant charge management in a heat pump water heater|
|US8789382 *||Jul 29, 2010||Jul 29, 2014||Lg Electronics Inc.||Heat pump including at least two refrigerant injection flow paths into a scroll compressor|
|US9016079 *||Jul 8, 2010||Apr 28, 2015||Heatf A/S||Energy system with a heat pump|
|US9383126||May 15, 2014||Jul 5, 2016||Nortek Global HVAC, LLC||Refrigerant charge management in a heat pump water heater|
|US20070251668 *||Mar 26, 2007||Nov 1, 2007||Mark Smith||High temperature refrigeration cycle method and apparatus|
|US20080190130 *||Feb 27, 2007||Aug 14, 2008||Springer Carrier Ltda||Heat Pump System with Auxiliary Water Heating|
|US20080197206 *||Jun 3, 2005||Aug 21, 2008||Carrier Corporation||Refrigerant System With Water Heating|
|US20080210768 *||May 18, 2006||Sep 4, 2008||Ying You||Heat Pump System and Method For Heating a Fluid|
|US20090013702 *||Jun 3, 2005||Jan 15, 2009||Springer Carrier Ltda||Refrigerant charge control in a heat pump system with water heater|
|US20090049857 *||Apr 20, 2006||Feb 26, 2009||Carrier Corporation||Heat pump system having auxiliary water heating and heat exchanger bypass|
|US20090293515 *||Oct 18, 2005||Dec 3, 2009||Carrier Corporation||Economized refrigerant vapor compression system for water heating|
|US20100038441 *||Aug 31, 2007||Feb 18, 2010||Troels Pedersen||Energy system with a heat pump|
|US20100077788 *||Sep 26, 2008||Apr 1, 2010||Nyle Special Products, Llc||Cascading air-source heat pump|
|US20110113808 *||May 19, 2011||Younghwan Ko||Heat pump|
|US20110120180 *||Jul 30, 2010||May 26, 2011||Sim Won Chin||Heat pump|
|US20120180511 *||Jul 8, 2010||Jul 19, 2012||Colipu A/S||Energy System With A Heat Pump|
|DE3543072A1 *||Dec 5, 1985||Jun 12, 1986||Takahashi Yutaka||Als heizung und/oder als kuehlsystem betreibbare, nach dem prinzip der waermepumpe arbeitende vorrichtung mit integrierter warmwasserbereitung|
|EP0852324A1 *||Dec 31, 1997||Jul 8, 1998||Mitsubishi Denki Kabushiki Kaisha||Refrigerant circulating apparatus and method of assembling a refrigerant circuit|
|WO1982003908A1 *||Apr 27, 1982||Nov 11, 1982||Refrigeration Co Inc Penjerdel||Self-balancing two-stage heat recovery system|
|WO1983004088A1 *||May 5, 1983||Nov 24, 1983||Arthur D. Little, Inc.||Heat pump system for production of domestic hot water|
|U.S. Classification||62/175, 62/185, 62/238.6, 62/201, 62/324.3, 62/510|
|International Classification||F25B29/00, F25B13/00, F25B31/00, F25B1/10, F24F5/00|
|Cooperative Classification||F25B31/002, F25B13/00, F25B29/003, F24F5/00, F25B1/10|
|European Classification||F25B13/00, F25B31/00B, F25B1/10, F24F5/00, F25B29/00B|