US20060080990A1 - Air conditioner - Google Patents

Air conditioner Download PDF

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Publication number
US20060080990A1
US20060080990A1 US11/249,706 US24970605A US2006080990A1 US 20060080990 A1 US20060080990 A1 US 20060080990A1 US 24970605 A US24970605 A US 24970605A US 2006080990 A1 US2006080990 A1 US 2006080990A1
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US
United States
Prior art keywords
opening
main compressor
air conditioner
fluid path
closing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US11/249,706
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English (en)
Inventor
Yoon Lee
Song Choi
Baik Chung
Se Chang
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
LG Electronics Inc
Original Assignee
LG Electronics Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by LG Electronics Inc filed Critical LG Electronics Inc
Assigned to LG ELECTRONICS INC. reassignment LG ELECTRONICS INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CHANG, SE DONG, CHOI, SONG, CHUNG, BAIK YOUNG, LEE, YOON BEEN
Publication of US20060080990A1 publication Critical patent/US20060080990A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/02—Increasing the heating capacity of a reversible cycle during cold outdoor conditions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor air

Definitions

  • the present invention relates to an air conditioner, and particularly, to an air conditioner reducing a load on a compressor when ambient air temperature is low during heating operation.
  • an air conditioner is for adjusting temperature, humidity, air current and cleanliness of air in order to create a pleasant indoor environment.
  • an integral type air conditioner in which an indoor unit and an outdoor unit are received inside one single case and a separated type air conditioner in which a compressor and a condenser as an indoor unit are separated from an evaporator as an outdoor unit.
  • Some air conditioners can selectively perform their cooling or heating functions by being provided with fluid path switch valves to switch a fluid path of a refrigerant.
  • FIG. 1 is a schematic view illustrating a construction of a conventional air conditioner for both cooling and heating
  • FIG. 2 is a pressure-enthalpy diagram corresponding to ambient air temperature of the air conditioner.
  • a conventional air conditioner for cooling and heating includes: a compressor 101 for compressing a refrigerant; a four-way valve 103 disposed at a discharge side of the compressor 101 so as to switch a fluid path of a refrigerant; an outdoor heat exchanger 105 and an indoor heat exchanger 107 which are connected with the four-way valve 103 and in which the refrigerant undergoes heat exchange; and an expansion valve 109 disposed between the outdoor heat exchanger 105 and the indoor heat exchanger 107 .
  • the four-way valve 103 switches the fluid path such that the refrigerant compressed in the compressor 101 flows to the outdoor heat exchanger 105 .
  • the refrigerant compressed in the compressor 101 undergoes heat exchange and then is condensed in the outdoor heat exchanger 105 .
  • condensed refrigerant is decompressed and expanded in the expansion valve 109 .
  • the refrigerant performs cooling operation, undergoing heat exchange and absorbing latent heat of evaporation in the indoor heat exchanger 107 .
  • the four-way valve 103 switches the fluid path such that the refrigerant compressed in the compressor 101 flows to the indoor heat exchanger 107 .
  • the refrigerant having undergone heat exchange in the indoor heat exchanger 107 and performed heating operation is condensed, and then is decompressed and expanded while passing the expansion valve 109 .
  • the decompressed and expanded refrigerant absorbs latent heat and is evaporated in the outdoor heat exchanger 105 .
  • the pressure-enthalpy diagram is formed in an order of a loop 1 ⁇ >2 ⁇ >3 ⁇ >4 in which a difference between a high-pressure side and a low-pressure side forms a first value ( ⁇ P).
  • the enthalpy diagram is formed in an order of a loop 1′ ⁇ >2′ ⁇ >3 ⁇ >4 in which the difference between the high pressure and the low pressure forms a second value ( ⁇ P′) which is greater than the first value ( ⁇ P).
  • an object of the present invention is to provide an air conditioner reducing a load on a compressor when ambient air temperature is low during heating operation.
  • an air conditioner comprising: a main compressor for compressing a refrigerant; a four-way valve disposed at a discharge side of the main compressor and switching a fluid path; an outdoor heat exchanger having one side connected with the four-way valve; an indoor heat exchanger having one side connected with the outdoor heat exchanger and the other side connected with the four-way valve; an expansion valve disposed between the outdoor heat exchanger and the indoor heat exchanger; and an auxiliary compression unit for reducing the load on the main compressor.
  • FIG. 1 is a schematic view illustrating a construction of a conventional air conditioner for both cooling and heating
  • FIG. 2 is a pressure-enthalpy diagram according to ambient air temperature of the air conditioner of FIG. 1 ;
  • FIG. 3 is a schematic view of an air conditioner according to a first embodiment of the present invention.
  • FIG. 4 is a view illustrating the operation of an auxiliary compression unit of FIG. 3 ;
  • FIG. 5 is a control block diagram of the air conditioner of FIG. 3 ;
  • FIG. 6 is a schematic view of an air conditioner in accordance with a second embodiment of the present invention.
  • FIG. 7 is a view illustrating the operation of an auxiliary compression unit of FIG. 6 ;
  • FIG. 8 is a control block diagram of the air conditioner of FIG. 6 .
  • FIG. 3 is a schematic view of an air conditioner in accordance with the first embodiment of the present invention
  • FIG. 4 is a view showing the operation of an auxiliary compression unit of FIG. 3
  • FIG. 5 is a control block diagram of the air conditioner of FIG. 3 .
  • an air conditioner in accordance with a first embodiment of the present invention includes: a main compressor 11 to compress the refrigerant, a four-way valve 13 , an outdoor heat exchanger 15 , an indoor heat exchanger 17 , an expansion valve 19 and an auxiliary compression unit 20 .
  • the four-way valve 13 is disposed at a discharge side of the main compressor 11 and switches a fluid path of a refrigerant according to its operating mode.
  • the outdoor heat exchanger 15 has one side connected with the four-way valve 13 and the refrigerant undergoes heat exchange.
  • the indoor heat exchanger 17 has one side connected with the outdoor heat exchanger 15 and the other side connected with the four-way valve 13 and the refrigerant undergoes heat exchange.
  • the expansion valve 19 is disposed between the outdoor heat exchanger 15 and the indoor heat exchanger 17 , and the refrigerant is decompressed and expanded while passing through the expansion valve 19 .
  • the auxiliary compression unit 20 is installed between the main compressor 11 and the four-way valve 13 , and decreases a load on the main compressor 11 when a difference between a high-pressure side and a low-pressure side is great because ambient air temperature is low during heating operation.
  • the auxiliary compression unit 20 includes: an auxiliary fluid path 21 , a sub-compressor 25 , an inlet-side opening/closing valve 23 , an outlet-side opening/closing valve 24 , a pressure equalizing tank 27 and an oil return fluid path 28 .
  • One side of the auxiliary fluid path 21 is connected to the discharge side of the main compressor 11 and the other side thereof is connected to the upstream side of the four-way valve 13 .
  • the sub-compressor 25 is disposed on the auxiliary fluid path 21 , and compresses once again the refrigerant having been compressed in the main compressor 11 .
  • the inlet-side opening/closing valve 23 is disposed at an inlet side of the auxiliary fluid path 21 , and opens or closes the auxiliary fluid path 21 .
  • the outlet-side opening/closing valve 24 is disposed at an outlet side of the auxiliary fluid path 21 , and opens or closes the auxiliary fluid path 21 .
  • the pressure equalizing tank 27 is disposed on the downstream side of the inlet-side opening/closing valve 23 , and temporarily receives the refrigerant compressed by the main compressor 11 .
  • the pressure equalizing tank 27 reduces discharge pulsation of the refrigerant being discharged from the main compressor 11 , and a problem resulted from a difference of mass flow per unit time between the main compressor 11 and the sub-compressor 25 .
  • the oil return fluid path 28 responds to excessive oil discharge in the main compressor 11 . To do so, the oil return fluid path 28 includes an oil return pipe 29 and a return pipe opening/closing valve 30 .
  • One side of the oil return fluid path 28 is installed at the lower part of the pressure equalizing tank 27 and the other side thereof is connected to an intake side of the main compressor 11 such that oil of the pressure equalizing tank 27 is returned to the main compressor 11 . Also, to have a convenience in installing oil return fluid path 28 , it is desirable that the oil return fluid path 28 includes a capillary tube.
  • the oil return pipe 29 have one side connected with the lower part of pressure equalizing tank 27 and the other side connected to the intake side of the main compressor 11 .
  • the return pipe opening/closing valve 30 is installed on the oil return pipe 29 , and opens or closes the oil return pipe 29 .
  • the inlet-side opening/closing valve 23 and the outlet-side opening/closing valve 24 can be manually opened or closed by measuring a pressure difference between the intake side and the discharge side of the main compressor 11 .
  • a intake-side pressure sensor 12 , a discharge-side pressure sensor 14 and a control unit 31 are further included, preferably.
  • the intake-side pressure sensor 12 is installed at the intake side of the main compressor 11 and transmits a signal to the control unit 31 by detecting the pressure of the intake side of the main compressor 11 .
  • the discharge-side pressure sensor 14 is installed at the discharge side of the main compressor 11 and transmits a signal to the control unit 31 by detecting the pressure of the discharge side of the main compressor 11 .
  • the control unit 31 is implemented in the form of MICOM having a control program therein or the like, and controls the opening or closing of the inlet-side opening/closing valve 23 and the outlet-side opening/closing valve 24 by receiving signals of the intake-side pressure sensor 12 and the discharge-side pressure sensor 14 .
  • the control unit 31 includes a pressure difference calculating unit 33 for calculating the pressure difference between the intake side and the discharge side of the main compressor 11 , preferably.
  • control unit 31 controls the four-way valve 13 such that the refrigerant compressed in the main compressor 11 flows to the indoor heat exchanger 17 .
  • the refrigerant having flowed to the indoor heat exchanger 17 performs heating operation and then is decompressed and expanded while passing the expansion valve 19 .
  • the refrigerant having passed the expansion valve 19 absorbs latent heat and is evaporated in the outdoor heat exchanger 15 , and is drawn into the main compressor 11 via the four-way valve 13 .
  • the pressure difference calculating unit 33 calculates the pressure difference between the intake side and the discharge side through the signals transmitted from the intake-side pressure sensor 12 and the discharge-side pressure sensor 14 .
  • control unit 31 blocks the auxiliary fluid path 21 by closing the inlet-side opening/closing valve 23 and the outlet-side opening/closing valve 24 such that compression of the refrigerant can be performed only in the main compressor 11 .
  • the overload may be on the main compressor 11 when the compression of the refrigerant is performed only by the main compressor 11 .
  • the control unit 31 opens the inlet-side opening/closing valve 23 and the outlet-side opening/closing valve 24 and operates the sub-compressor 25 such that the refrigerant can flow to the auxiliary fluid path 21 .
  • part of the refrigerant discharged from the main compressor 11 flows along the auxiliary fluid path 21 and is temporarily received in the pressure equalizing tank 27 .
  • the refrigerant received temporarily in the pressure equalizing tank 27 is drawn into the sub-compressor 25 and is condensed, then flows along the auxiliary fluid path 21 and joins together with the refrigerant discharged from the main compressor 11 , and then flows to the indoor heat exchanger 17 via the four-way valve 13 .
  • the refrigerant having performed the heating operation in the indoor heat exchanger 17 is drawn into the main compressor 11 via the expansion valve 19 , the outdoor heat exchanger 15 and the four-way valve 13 , and repeats compression and discharge processes.
  • control unit 31 opens the return pipe opening/closing valve 30 so as to open the oil return pipe 29 .
  • oil inside the pressure equalizing tank 27 flows along the oil return pipe 29 , is drawn into the intake side of the main compressor 11 , and is returned to the inside of the main compressor 11 .
  • FIG. 6 is a schematic view of an air conditioner in accordance with the second embodiment of the present invention
  • FIG. 7 is a view showing the operation of an auxiliary compression unit of FIG. 6
  • FIG. 8 is a control block diagram of the air conditioner of FIG. 6 .
  • the same reference numerals are given to the same parts as those in the aforementioned and illustrated construction for the purpose of simplicity in description for the drawings, and detailed descriptions therefor will be omitted.
  • the auxiliary compression unit 20 is operated when a pressure difference is great after the pressure difference between the intake side and the discharge side of the main compressor 11 is detected.
  • an auxiliary compression unit 20 is operated when ambient air temperature is low after ambient air temperature is detected instead of the pressure difference. As occasion demands, after both the pressure difference and the ambient air temperature are detected, on the basis of such results, the auxiliary compression unit 20 can be operated.
  • the air conditioner in accordance with the second embodiment includes an ambient air temperature sensor 40 instead of the intake-side pressure sensor 12 and the discharge-side pressure sensor 14 of the first embodiment.
  • the air conditioner of the second embodiment has a control unit 31 excluding the pressure difference calculating unit 33 of the first embodiment. The remaining construction except for this is the same and a detailed description therefor will be omitted.
  • the ambient air temperature sensor 50 is installed at one side of the outdoor heat exchanger 15 , and transmits a signal to the control unit 31 by detecting outside temperature.
  • control unit 31 controls a four-way valve 13 such that the refrigerant compressed in a main compressor 11 flows to an indoor heat exchanger 17 .
  • the refrigerant having flowed to the indoor heat exchanger 17 performs the heating operation, and is decompressed and expanded while passing through an expansion valve 19 .
  • the refrigerant having passed the expansion valve 19 absorbs latent heat and is evaporated in the outdoor heat exchanger 15 , and is drawn into the main compressor 11 via the four-way valve 13 .
  • the ambient air temperature sensor 50 detects the outside temperature and transmits a signal to the control unit 31 .
  • control unit 31 blocks an auxiliary fluid path 21 by closing an inlet-side opening/closing valve 23 and an outlet-side opening/closing valve 24 .
  • the control unit 31 opens the inlet-side opening/closing valve 23 and the outlet-side opening/closing valve 24 such that the refrigerant can flow to the auxiliary fluid path 21 , and operates a sub-compressor 25 .
  • part of the refrigerant discharged from the main compressor 11 flows along the auxiliary fluid path 21 and is temporality received in a pressure equalizing tank 27 .
  • the refrigerant temporarily received in the pressure equalizing pipe 27 is drawn into the sub-compressor 25 and is compressed, then flows along the auxiliary fluid path 21 and joins together with the refrigerant discharged form the main compressor 11 , and then flows to the indoor heat exchanger 17 via the four-way valve 13 .
  • the refrigerant having performed the heating operation in the indoor heat exchanger 17 passes the expansion valve 19 , the outdoor heat exchanger 15 , and the four-way valve 13 , then is drawn into the main compressor 11 , and repeats compression and discharge processes.
  • control unit 31 opens a return pipe opening/closing valve 30 so as to open an oil return pipe 29 .
  • the oil inside the pressure equalizing tank 27 flows along the oil return pipe 29 , is drawn into an intake side of the main compressor 11 , and is returned to the inside of the main compressor 11 .
  • the air conditioner in accordance with the embodiments of the present invention includes the auxiliary compression unit 20 reducing the load on the main compressor 11 when ambient air temperature is low during heating operation. Accordingly, since the load on the main compressor 11 decreases, efficiency and reliability of the main compressor 11 are enhanced and noises are reduced. In addition, an instrumental part such as a bearing inside the main compressor 11 is not subject to abrasion and high heat damage to a motor unit is prevented.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)
US11/249,706 2004-10-18 2005-10-14 Air conditioner Abandoned US20060080990A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1020040083299A KR100575693B1 (ko) 2004-10-18 2004-10-18 보조압축회로를 구비한 공기조화기
KR83299/2004 2004-10-18

Publications (1)

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US20060080990A1 true US20060080990A1 (en) 2006-04-20

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ID=36179304

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/249,706 Abandoned US20060080990A1 (en) 2004-10-18 2005-10-14 Air conditioner

Country Status (5)

Country Link
US (1) US20060080990A1 (ko)
EP (1) EP1701114B1 (ko)
KR (1) KR100575693B1 (ko)
CN (1) CN1763459A (ko)
DE (1) DE602005006377T2 (ko)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011089938A1 (ja) * 2010-01-25 2011-07-28 三菱重工業株式会社 空気調和機

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013014543A1 (de) * 2013-09-03 2015-03-05 Stiebel Eltron Gmbh & Co. Kg Wärmepumpenvorrichtung
CN106196531A (zh) * 2016-09-30 2016-12-07 海南唯视雅科工程服务有限公司 一种水冷式空调制冷主机系统

Citations (14)

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US3668883A (en) * 1970-06-12 1972-06-13 John D Ruff Centrifugal heat pump with overload protection
US4268291A (en) * 1979-10-25 1981-05-19 Carrier Corporation Series compressor refrigeration circuit with liquid quench and compressor by-pass
US4292814A (en) * 1979-06-13 1981-10-06 Anton Braun Heat pump
US4306420A (en) * 1979-10-25 1981-12-22 Carrier Corporation Series compressor refrigeration circuit with liquid quench and compressor by-pass
US4362030A (en) * 1981-09-02 1982-12-07 Carrier Corporation Refrigeration circuit
US5029449A (en) * 1990-02-23 1991-07-09 Gas Research Institute Heat pump booster compressor arrangement
US5839886A (en) * 1996-05-10 1998-11-24 Shaw; David N. Series connected primary and booster compressors
US5927088A (en) * 1996-02-27 1999-07-27 Shaw; David N. Boosted air source heat pump
US6276148B1 (en) * 2000-02-16 2001-08-21 David N. Shaw Boosted air source heat pump
US20030233838A1 (en) * 2002-06-19 2003-12-25 Lg Electronics Inc. Air conditioning system with two compressors and method for operating the same
US6817205B1 (en) * 2003-10-24 2004-11-16 Carrier Corporation Dual reversing valves for economized heat pump
US6923016B2 (en) * 2003-04-09 2005-08-02 Sunao Funakoshi Refrigeration cycle apparatus
US6931871B2 (en) * 2003-08-27 2005-08-23 Shaw Engineering Associates, Llc Boosted air source heat pump
US6951116B2 (en) * 2002-11-22 2005-10-04 Lg Electronics Inc. Air conditioner and method for controlling electronic expansion valve of air conditioner

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JPS57168082A (en) 1981-04-10 1982-10-16 Hitachi Ltd Refrigerator
JP2664740B2 (ja) 1988-09-30 1997-10-22 株式会社東芝 空気調和機
JPH08285384A (ja) * 1995-04-14 1996-11-01 Nippondenso Co Ltd 冷凍サイクル
JP4195120B2 (ja) 1998-04-23 2008-12-10 東芝キヤリア株式会社 空気調和機

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3668883A (en) * 1970-06-12 1972-06-13 John D Ruff Centrifugal heat pump with overload protection
US4292814A (en) * 1979-06-13 1981-10-06 Anton Braun Heat pump
US4268291A (en) * 1979-10-25 1981-05-19 Carrier Corporation Series compressor refrigeration circuit with liquid quench and compressor by-pass
US4306420A (en) * 1979-10-25 1981-12-22 Carrier Corporation Series compressor refrigeration circuit with liquid quench and compressor by-pass
US4362030A (en) * 1981-09-02 1982-12-07 Carrier Corporation Refrigeration circuit
US5029449A (en) * 1990-02-23 1991-07-09 Gas Research Institute Heat pump booster compressor arrangement
US5927088A (en) * 1996-02-27 1999-07-27 Shaw; David N. Boosted air source heat pump
US5839886A (en) * 1996-05-10 1998-11-24 Shaw; David N. Series connected primary and booster compressors
US6276148B1 (en) * 2000-02-16 2001-08-21 David N. Shaw Boosted air source heat pump
US20030233838A1 (en) * 2002-06-19 2003-12-25 Lg Electronics Inc. Air conditioning system with two compressors and method for operating the same
US6951116B2 (en) * 2002-11-22 2005-10-04 Lg Electronics Inc. Air conditioner and method for controlling electronic expansion valve of air conditioner
US6923016B2 (en) * 2003-04-09 2005-08-02 Sunao Funakoshi Refrigeration cycle apparatus
US6931871B2 (en) * 2003-08-27 2005-08-23 Shaw Engineering Associates, Llc Boosted air source heat pump
US6817205B1 (en) * 2003-10-24 2004-11-16 Carrier Corporation Dual reversing valves for economized heat pump

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011089938A1 (ja) * 2010-01-25 2011-07-28 三菱重工業株式会社 空気調和機
CN102575884A (zh) * 2010-01-25 2012-07-11 三菱重工业株式会社 空气调节机
US9285148B2 (en) 2010-01-25 2016-03-15 Mitsubishi Heavy Industries, Ltd. Air conditioner using oil return operation based on outdoor air temperature

Also Published As

Publication number Publication date
EP1701114B1 (en) 2008-04-30
KR20060034148A (ko) 2006-04-21
EP1701114A1 (en) 2006-09-13
DE602005006377D1 (de) 2008-06-12
KR100575693B1 (ko) 2006-05-03
DE602005006377T2 (de) 2009-06-10
CN1763459A (zh) 2006-04-26

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