EP1701114B1 - Klimaanlage - Google Patents

Klimaanlage Download PDF

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Publication number
EP1701114B1
EP1701114B1 EP05256352A EP05256352A EP1701114B1 EP 1701114 B1 EP1701114 B1 EP 1701114B1 EP 05256352 A EP05256352 A EP 05256352A EP 05256352 A EP05256352 A EP 05256352A EP 1701114 B1 EP1701114 B1 EP 1701114B1
Authority
EP
European Patent Office
Prior art keywords
main compressor
fluid path
opening
air conditioner
heat exchanger
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.)
Expired - Fee Related
Application number
EP05256352A
Other languages
English (en)
French (fr)
Other versions
EP1701114A1 (de
Inventor
Yoon-Been Lee
Song Choi
Baik-Young Chung
Se-Dong 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
Publication of EP1701114A1 publication Critical patent/EP1701114A1/de
Application granted granted Critical
Publication of EP1701114B1 publication Critical patent/EP1701114B1/de
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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.
  • Embodiments relate to an air conditioner reducing a load on a compressor when ambient air temperature is low during heating operation.
  • air conditioners are used 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.
  • 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 embodiments is to provide an air conditioner reducing 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 for 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, and characterized in that the auxiliary compression unit comprises: an auxiliary fluid path having one side connected with the discharge side of the main compressor and the other side connected to the upstream side of the four-way valve; a sub-compressor disposed on the auxiliary fluid path for compressing the refrigerant; an inlet-side opening/closing valve disposed at an inlet side of the auxiliary fluid path for opening or closing the auxiliary fluid path; and an outlet-side opening/closing valve disposed at an outlet side of the auxiliary fluid path
  • 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; a first heat exchanger for connection to the four-way valve; a second heat exchanger having one side for connection with the first heat exchanger and another side for connection with the four-way valve; an expansion valve for being disposed between the first and second exchangers; and an auxiliary compression unit for reducing the load on the main compressor.
  • a first air conditioner 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.
  • 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 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.
  • 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 second air conditioner 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 therefore 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 first and second air conditioners include 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 noise is reduced. In addition, an instrumental part such as a bearing inside the main compressor 11 is less 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)

Claims (8)

  1. Klimagerät, aufweisend:
    einen Hauptverdichter (11) zum Verdichten eines Kühlmittels;
    ein Vier-Wege-Ventil (13), angeordnet auf einer Auslassseite des Hauptverdichters (11) zum Schalten eines Fluidpfades;
    einen Außenraum-Wärmetauscher (15), dessen eine Seite mit dem Vier-Wege-Ventil (13) verbunden ist;
    einen Innenraum-Wärmetauscher (17), dessen eine Seite mit dem Außenraum-Wärmetauscher (15) und dessen andere Seite mit dem Vier-Wege-Ventil (13) verbunden ist;
    ein Ausdehnungsventil (19), angeordnet zwischen dem Außenraum-Wärmetauscher (15) und dem Innenraum-Wärmetauscher (17) und
    eine Hilfsverdichtereinheit (20) zum Reduzieren einer Last am Hautverdichter (11) und dadurch gekennzeichnet, dass die Hilfsverdichtereinheit (20) aufweist:
    einen Hilfs-Fluidpfad (21), dessen eine Seite mit der Auslassseite des Hauptverdichters (11) und dessen anderen Seite mit der stromaufwärts gelegenen Seite des Vier-Wege-Ventils (13) verbunden ist;
    einen Unter-Verdichter (25), angeordnet am Hilfs-Fluidpfad (21) zum Verdichten des Kühlmittels;
    ein einlassseitiges Offnungs-/Schließventil (23), angeordnet an einer Einlassseile des Hilfs-Fluidpfades (21) zum Öffnen oder Schließen des Hilfs-Fluidpfades (21) und
    ein auslassseitiges Öffnungs-/Schließventil (24), angeordnet an einer Auslassseite des Hilfs-Fluidpfades (21) zum Öffnen oder Schließen des Hilfs-Fluidpfades (21).
  2. Klimagerät, wie in Anspruch 1 beschrieben, wobei die HilfsVerdichtereinheit (20) weiterhin aufweist:
    einen Druckausgleichstank (27), angeordnet auf der stromabwärts gelegenen Seite des einlassseitigen Öffnungs-/Schließventils (23) zur vorübergehenden Aufnahme des vom Hauptverdichter (11) verdichteten Kühlmittels.
  3. Klimagerät, wie in Anspruch 2 beschrieben, wobei die HilfsVerdichtereinheit (20) weiterhin aufweist:
    einen Ölrückström-Fluidpfad (28) zum Verbinden des Druckausgleichstanks (27) mit einer Einlassseite des Hauptverdichters (11), sodass das Öl des Druckausgleichstanks (27) zum Hauptverdichter (11) zurückgeführt wird.
  4. Klimagerät, wie in Anspruch 3 beschrieben, wobei der Ölrückström-Fluidpfad (28) aufweist:
    ein Ölrückströmrohr (29), dessen eine Seite mit dem Druckausgleichstank (27) und dessen andere Seite mit der Einlassseite des Hauptverdichters (11) verbunden ist und
    ein Rückströmrohr-Öffnungs-/Schließventil (30) zum Öffnen oder Schließen des Ölrückströmrohrs (29).
  5. Klimagerät, wie in Anspruch 3 beschrieben, wobei der Ölrückström-Fluidpfad (28) eine Kapillarröhre aufweist.
  6. Klimagerät, wie in jedem beliebigen der Ansprüche 1 bis 5 beschrieben, weiterhin aufweisend:
    einen einlassseitigen Drucksensor (12) zum Erfassen des Drucks der Einlassseite des Hauptverdichters (11);
    einen auslassseitigen Drucksensor (14) zum Erfassen des Drucks der Auslassseite des Hauptverdichters (11) und
    eine Steuerungseinheit (31) zum Steuern des Öffnens oder Schließens des einlassseitigen Öffnungs-/Schließventils (23) und des auslassseitigen Öffnungs-/Schließventils (24) durch Empfangen von Signalen des einlassseitigen Drucksensors (12) und des auslassseitigen Drucksensors (14).
  7. Klimagerät, wie in Anspruch 6 beschrieben, wobei die Steuerungseinheit (31) eine Druckdifferenzberechnungseinheit (33) zur Berechnung einer Druckdifferenz zwischen der Einlassseite und der Auslassseite des Hauptverdichters (11) aufweist.
  8. Klimagerät, wie in jedem beliebigen der Ansprüche 1 bis 5 beschrieben, weiterhin aufweisend:
    einen Umgebungsluft-Temperatursensor zur Erfassung von Umgebungslufttemperatur sowie
    eine Steuerungseinheit (31) zum Steuern des Öffnens oder Schließens des einlassseitigen Öffnungs-/Schließventils (23) und des auslassseitigen Öffnungs-/Schließventils (24) durch Empfangen eines Signals des Umgebungsluft-Temperatursensors.
EP05256352A 2004-10-18 2005-10-13 Klimaanlage Expired - Fee Related EP1701114B1 (de)

Applications Claiming Priority (1)

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

Publications (2)

Publication Number Publication Date
EP1701114A1 EP1701114A1 (de) 2006-09-13
EP1701114B1 true EP1701114B1 (de) 2008-04-30

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EP05256352A Expired - Fee Related EP1701114B1 (de) 2004-10-18 2005-10-13 Klimaanlage

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US (1) US20060080990A1 (de)
EP (1) EP1701114B1 (de)
KR (1) KR100575693B1 (de)
CN (1) CN1763459A (de)
DE (1) DE602005006377T2 (de)

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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

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US6276148B1 (en) * 2000-02-16 2001-08-21 David N. Shaw Boosted air source heat pump
KR100484799B1 (ko) * 2002-06-19 2005-04-22 엘지전자 주식회사 두개의 압축기를 채용한 공기조화기의 압축기 동작방법
KR100471453B1 (ko) * 2002-11-22 2005-03-08 엘지전자 주식회사 히트펌프 시스템 및 히트펌프 시스템의 전자 팽창밸브제어방법
JP4321095B2 (ja) * 2003-04-09 2009-08-26 日立アプライアンス株式会社 冷凍サイクル装置
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

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Publication number Publication date
KR100575693B1 (ko) 2006-05-03
EP1701114A1 (de) 2006-09-13
DE602005006377T2 (de) 2009-06-10
CN1763459A (zh) 2006-04-26
DE602005006377D1 (de) 2008-06-12
US20060080990A1 (en) 2006-04-20
KR20060034148A (ko) 2006-04-21

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