WO2007006632A1 - Installation de refroidissement, en particulier installation de climatisation de vehicule automobile - Google Patents

Installation de refroidissement, en particulier installation de climatisation de vehicule automobile Download PDF

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Publication number
WO2007006632A1
WO2007006632A1 PCT/EP2006/063458 EP2006063458W WO2007006632A1 WO 2007006632 A1 WO2007006632 A1 WO 2007006632A1 EP 2006063458 W EP2006063458 W EP 2006063458W WO 2007006632 A1 WO2007006632 A1 WO 2007006632A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
refrigeration system
expansion valve
section
refrigerant
Prior art date
Application number
PCT/EP2006/063458
Other languages
German (de)
English (en)
Inventor
Peter Horstmann
Original Assignee
Robert Bosch Gmbh
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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2007006632A1 publication Critical patent/WO2007006632A1/fr

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/00485—Valves for air-conditioning devices, e.g. thermostatic valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3205—Control means therefor
    • B60H1/3211—Control means therefor for increasing the efficiency of a vehicle refrigeration 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/32—Expansion valves having flow rate limiting means other than the valve member, e.g. having bypass orifices in the valve body
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/325—Expansion valves having two or more valve members
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H2001/3269—Cooling devices output of a control signal
    • B60H2001/3285—Cooling devices output of a control signal related to an expansion unit
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • Refrigeration system in particular motor vehicle air conditioning
  • the invention relates to a refrigeration system, in particular a motor vehicle air conditioning system, with a refrigerant circuit through which a refrigerant flows as a refrigerant, which comprises a compressor, a condenser or gas cooler, an expansion valve with a controllable throttle cross section and an evaporator.
  • Refrigeration systems and in particular motor vehicle air conditioning systems with a refrigerant circuit through which CO2 flows, will become increasingly important in the future, since CO2 can be disposed of without any problem unlike conventional refrigerants, such as fluorinated hydrocarbons.
  • conventional refrigerants such as fluorinated hydrocarbons.
  • a supercritical operation is required.
  • the CO2 is not condensed in the condenser serving as a heat exchanger, but only cooled in a supercritical state, which is why the condenser is also referred to as a gas cooler.
  • the pressure of the refrigerant during heat release can be set independently of the ambient temperature.
  • This expansion valve is used to control the pressure prevailing in the refrigerant circuit high pressure to adjust under the respective operating conditions, such as ambient temperature and temperature in the evaporator, to a value at which the efficiency or the cooling capacity of the refrigeration system is optimal, whereby in a motor vehicle air conditioning Fuel consumption for the operation of the air conditioning can be significantly reduced.
  • the throttle section of the expansion valve In order to allow a desired high-pressure setting, the throttle section of the expansion valve must be adjusted as a function of the respective operating conditions and depending on the selected operating strategy, that is, either optimizing the refrigerating capacity or optimizing the coefficient of performance (COP) to let. If the selected operating strategy is established, there is a dependency between the high pressure prevailing in the refrigerant circuit and a throttle cross section required for optimum operation of the system. This required throttle cross-section is shown in FIG.
  • control task then consists in adjusting the throttle cross-section of the expansion valve pressure-dependent and thereby regulate that he on the points with optimum cooling capacity or optimum efficiency, corresponding to the black squares or black diamonds shown in FIG. 2, for which the curve A shown in FIG. 2 represents a first approximation.
  • expansion valves whose throttle cross section can be adjusted over a range of 0 to 2 mm 2 and are suitable for a CO 2- operated refrigeration system have the disadvantage that they are structurally relatively complex and require a control corresponding to the control, whereby they are relatively high are expensive.
  • the refrigeration system according to the invention with the features mentioned in claim 1 offers the advantage that can be used by the limitation of the adjustment or control range simply constructed, manufactured in high volumes for brake systems of motor vehicles valves, compared to conventional controllable expansion valves for operated with CO 2 - A -
  • Refrigeration systems are significantly cheaper. Although these expansion valves only have a maximum throttle cross-section of about 1 mm 2 or an adjustment or control range between 0 and about 1 mm 2 , this is sufficient under moderate ambient conditions to ensure optimum efficiency and optimum cooling capacity of the refrigeration system to care. Since moderate ambient conditions predominate during most of the annual operating hours of a motor vehicle air conditioning system, a substantial reduction in the fuel consumption of the air conditioning system is made possible and an overall cost-effective mode of operation is ensured. In contrast, higher ambient temperatures, which would require larger throttle cross sections for optimum operation of the air conditioning system, are only of secondary importance with respect to their duration and thus with regard to fuel consumption and can therefore be neglected.
  • valves produced for brake systems of motor vehicles such as a valve available under the name MV1.80 from Robert Bosch GmbH, also have a lower drive power, a lower weight and a smaller installation space than conventional controllable expansion valves for refrigeration systems and, moreover, due to their small throttle cross-section, allow cycling without the production of audible sounds.
  • a fixed throttle having a constant throttle cross section may be connected in parallel with the controllable expansion valve, wherein the total throttle cross section of the fixed throttle and the controllable expansion valve is at most about 1 mm 2 and wherein the throttle cross section Section of the fixed throttle (Orifice) is suitably smaller than the throttle cross-section of the expansion valve.
  • the fixed throttle may be a separate component, but is suitably designed in the form of a bypass bore in a valve block of the variable expansion valve.
  • a parallel to the expansion valve switched overflow valve may be provided which also serves as a pressure limiter and opens when a first predetermined high pressure in the refrigerant circuit is exceeded, for example at 120 bar, and at a second predetermined high pressure, for example at 130 bar , is fully opened with an opening cross section exceeding the throttle cross-section of the expansion valve.
  • the opening pressure of the overflow valve expediently corresponds to the high pressure, in which, with a maximum throttle cross-section of the expansion valve, an optimum efficiency or an optimal cooling capacity is achieved.
  • the expansion valve may have any suitable design, for example as a cone or ball valve with a conical or ball seat for a corresponding valve member, needle valve or as a sliding sleeve valve and be operated as needed as a proportional valve or as a clocked valve, wherein it each of these two modes is electrically controlled.
  • the refrigeration system may expediently comprise an internal heat exchanger, in which the compressed refrigerant flowing out of the condenser or gas cooler to the expansion valve is cooled by heat exchange with the refrigerant flowing from the evaporator to the compressor.
  • controllable expansion valve with a maximum throttle cross section of less than 1 mm 2 can also be used to advantage for controlling a refrigerant mass flow of the second evaporator.
  • Figure 1 is a schematic representation of a flowed through by CO2 refrigerant circuit of a motor vehicle air conditioning system with an expansion element and an internal heat exchanger;
  • FIG. 2 shows a representation of the throttle cross sections of an expansion element of a refrigeration system for maximum efficiency (black squares) or for maximum refrigeration conduction (black diamonds) as a function of high pressure, as well as with approximation curves for the control of a known controllable expansion valve with an adjustment range of the throttle cross section from 0 to 2 mm 2 , a known fixed throttle (orifice) with a throttle cross section of 0.32 mm 2 and an expansion valve according to the invention with a control range from 0 to 1 mm 2 ;
  • Figure 3 is a schematic representation of a first embodiment of the expansion device of Fig. 1;
  • Figure 4 is a schematic representation of a second embodiment of the expansion device of Fig. 1;
  • Figure 5 is a partially sectioned view of a valve block of the embodiment of Figure 4.
  • Figure 6 is a schematic representation of a third embodiment of the expansion device of Fig. 1;
  • FIG. 7 shows a schematic representation of a fourth embodiment of the expansion element from FIG. 1.
  • refrigerant circuit 2 operated with CO2 as a refrigerant motor vehicle air conditioning system 4 consists in a known manner substantially from a compressor 6, an oil separator 8, a gas cooler 10 and a first part 12 of an inner heat exchanger 14, in a high pressure section 16 of the refrigerant circuit 2 are arranged behind the compressor 6 and are flowed through by the compressed refrigerant, an expansion sion member 18 for relaxing and cooling the compressed refrigerant, and designed as a heat exchanger evaporator 20 and a collector 22, which together with a second part 24 of the inner heat exchanger 12 in a low pressure section 26 of the refrigerant circuit 2 between the expansion member 18 and the suction side of the compressor. 6 are arranged.
  • the gaseous refrigerant is compressed to increase its internal energy. Subsequently, the refrigerant is passed through the oil separator 8 to deposit oil residues contained in the refrigerant and to return to the lubrication of the compressor 6 through a return line 28 to this. Thereafter, the compressed refrigerant is cooled in the gas cooler 10 serving as a heat exchanger with supplied ambient air 30, wherein the refrigerant releases a part of its internal heat energy and assumes a supercritical gaseous state.
  • the compressed refrigerant flows countercurrently to the refrigerant flowing through the low-pressure portion 26 through the inner heat exchanger 12, and its temperature is further lowered.
  • the refrigerant is subsequently expanded and cooled down a further time before it subsequently flows through the evaporator 20, which is designed as a heat exchanger, and evaporates therein at least partially.
  • the expansion element 18 comprises an electrically controllable expansion valve 34, as shown in FIGS. 1 and 3, whose throttle cross-section is changed as a function of the high pressure prevailing in the high-pressure section 16 and measured by a sensor (not shown).
  • the expansion valve 34 has a control range of 0 to 1 mm 2 and is formed for example by a valve produced in large numbers for brake systems of motor vehicles with anti-lock braking system (ABS) or electronic stability program (ESP) valve, the company Robert Bosch GmbH the designation MV1.80 is available.
  • ABS anti-lock braking system
  • ESP electronic stability program
  • This valve has at moderate environmental conditions, good control characteristics, and makes it possible to operate the air conditioner ciency below an ambient temperature of about 25 0 C in response to the high pressure at an optimum cooling capacity or optimum WIR, as indicated by the approximate curve C for the control of of the expansion valve 34 shown in Fig. 2.
  • the curve C runs at inlet pressures of more than 118 bar at the entrance of the expansion device 18 horizontally, ie parallel to the straight line B, so that exceeding the allowable operating pressure of the air conditioner 4 must be prevented.
  • FIGS. 4 to 7 show further possible embodiments of the expansion element 18, wherein the expansion element 18 shown in FIGS. 4 and 5 comprises, in addition to the controllable expansion valve 34, a fixed throttle (orifice) 36 connected in parallel thereto.
  • the fixed throttle 36 is an oblique bypass bore 38 between a radial valve inlet bore 40 and an axial valve outlet bore 42 in a valve block 44 formed of the expansion member 18, wherein the cross section of the bypass bore 38, for example, 0.2 mm 2 , while the throttle cross-section of the variable expansion valve 34, depending on the high pressure between 0 and 0.5 mm 2 or between 0 and 0.8 mm 2 is adjustable and because of the small cross-sections is particularly well suited for a clock operation.
  • the controllable expansion valve 34 is an electrically controlled valve, which may be formed as a ball, conical, needle or sliding sleeve valve depending on the selected mode, ie clock or proportional operation, and the existing installation conditions.
  • the expansion element 18 shown in FIG. 6 contains, in addition to the controllable expansion valve 34, an overflow valve 46 which opens, for example, at a pressure of 120 bar and is fully opened at 130 bar, so that in this way the permissible operating pressure of the air conditioning system is exceeded 4 in the horizontal part of the curve C can be prevented.
  • an overflow valve 46 which opens, for example, at a pressure of 120 bar and is fully opened at 130 bar, so that in this way the permissible operating pressure of the air conditioning system is exceeded 4 in the horizontal part of the curve C can be prevented.
  • the expansion element 18 shown in FIG. 7 contains, in addition to the expansion valve 34, a fixed throttle 36 and an overflow valve 46, which are both connected in parallel to the expansion valve 34.
  • the collector 22 downstream of the evaporator 20 serves to collect and store the liquid, that is to say non-vaporized, refrigerant after it has passed through the evaporator 20, in order, if necessary, for example, to reduce the temperature Speed of the compressor 6, back from the collector 22 in the evaporator 20 due.
  • the vaporized in the evaporator 20 gaseous refrigerant is from the compressor 6, wherein it flows through the low pressure section 26 and the second part 24 of the inner heat exchanger 14 and heats up with simultaneous cooling of the refrigerant in the high pressure section 16.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

L'invention concerne une installation de refroidissement, en particulier une installation de climatisation de véhicule automobile (4), comprenant un circuit de réfrigérant (2) qui est traversé par un réfrigérant se présentant sous la forme de CO2, et qui comprend un compresseur (6), un condenseur ou appareil de refroidissement à gaz (10), un organe d'expansion (18) comportant une section transversale d'étranglement, et un évaporateur (20). Cette invention est caractérisée en ce que la zone de régulation maximale de la section transversale d'étranglement est approximativement égale à 1 mm2.
PCT/EP2006/063458 2005-07-12 2006-06-22 Installation de refroidissement, en particulier installation de climatisation de vehicule automobile WO2007006632A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005032458A DE102005032458A1 (de) 2005-07-12 2005-07-12 Kälteanlage, insbesondere Kraftfahrzeug-Klimaanlage
DE102005032458.4 2005-07-12

Publications (1)

Publication Number Publication Date
WO2007006632A1 true WO2007006632A1 (fr) 2007-01-18

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Application Number Title Priority Date Filing Date
PCT/EP2006/063458 WO2007006632A1 (fr) 2005-07-12 2006-06-22 Installation de refroidissement, en particulier installation de climatisation de vehicule automobile

Country Status (3)

Country Link
DE (1) DE102005032458A1 (fr)
HK (1) HK1110282A1 (fr)
WO (1) WO2007006632A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008119768A2 (fr) * 2007-03-29 2008-10-09 Valeo Klimasysteme Gmbh Système de climatisation, en particulier pour un véhicule à moteur
DE102010027601A1 (de) 2010-07-20 2012-01-26 Christoph Peschke Kopplung von Solarkollektoren und Wärmepumpen mit variabler Expansionstemperatur
DE102012224121A1 (de) * 2012-12-21 2014-06-26 Bayerische Motoren Werke Aktiengesellschaft Expansionsventil für einen Kühlkreislauf
CN104101140A (zh) * 2014-08-04 2014-10-15 合肥华凌股份有限公司 冷柜或冰箱及其制冷系统
DE102014213267A1 (de) 2014-07-09 2016-01-14 Volkswagen Aktiengesellschaft Klimatisierungsvorrichtung sowie ein hierfür bestimmtes Absperrorgan
EP3985325A4 (fr) * 2019-06-17 2022-11-16 Mitsubishi Electric Corporation Dispositif à cycle frigorifique

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007063619A1 (de) * 2007-05-31 2008-12-04 Güntner AG & Co. KG Kälteanlage mit als Gaskühler betreibbarem Wärmeübertrager

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19832479A1 (de) * 1998-07-20 2000-01-27 Behr Gmbh & Co Mit CO¶2¶ betreibbare Klimaanlage
JP2001241809A (ja) * 2000-03-02 2001-09-07 Saginomiya Seisakusho Inc 超臨界蒸気圧縮冷凍サイクル装置用高圧制御弁
EP1134467A1 (fr) * 2000-03-16 2001-09-19 Otto Egelhof GmbH & Co. Installation de soupape dans un système de refrigération
US6430950B1 (en) * 1998-11-12 2002-08-13 Behr Gmbh & Co. Expansion element and a valve unit usable therefor
FR2868830A1 (fr) * 2004-04-09 2005-10-14 Valeo Climatisation Sa Dispositif de detente ameliore pour circuit de climatisation

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19832479A1 (de) * 1998-07-20 2000-01-27 Behr Gmbh & Co Mit CO¶2¶ betreibbare Klimaanlage
US6430950B1 (en) * 1998-11-12 2002-08-13 Behr Gmbh & Co. Expansion element and a valve unit usable therefor
JP2001241809A (ja) * 2000-03-02 2001-09-07 Saginomiya Seisakusho Inc 超臨界蒸気圧縮冷凍サイクル装置用高圧制御弁
EP1134467A1 (fr) * 2000-03-16 2001-09-19 Otto Egelhof GmbH & Co. Installation de soupape dans un système de refrigération
FR2868830A1 (fr) * 2004-04-09 2005-10-14 Valeo Climatisation Sa Dispositif de detente ameliore pour circuit de climatisation

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 2000, no. 26 1 July 2002 (2002-07-01) *

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008119768A2 (fr) * 2007-03-29 2008-10-09 Valeo Klimasysteme Gmbh Système de climatisation, en particulier pour un véhicule à moteur
WO2008119768A3 (fr) * 2007-03-29 2009-01-22 Valeo Klimasysteme Gmbh Système de climatisation, en particulier pour un véhicule à moteur
DE102010027601A1 (de) 2010-07-20 2012-01-26 Christoph Peschke Kopplung von Solarkollektoren und Wärmepumpen mit variabler Expansionstemperatur
DE102012224121A1 (de) * 2012-12-21 2014-06-26 Bayerische Motoren Werke Aktiengesellschaft Expansionsventil für einen Kühlkreislauf
DE102014213267A1 (de) 2014-07-09 2016-01-14 Volkswagen Aktiengesellschaft Klimatisierungsvorrichtung sowie ein hierfür bestimmtes Absperrorgan
CN104101140A (zh) * 2014-08-04 2014-10-15 合肥华凌股份有限公司 冷柜或冰箱及其制冷系统
EP3985325A4 (fr) * 2019-06-17 2022-11-16 Mitsubishi Electric Corporation Dispositif à cycle frigorifique
EP4234992A3 (fr) * 2019-06-17 2023-10-04 Mitsubishi Electric Corporation Dispositif à cycle frigorifique

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HK1110282A1 (en) 2008-07-11
DE102005032458A1 (de) 2007-01-25

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