EP3246641A1 - Appareil de dégivrage rapide d'évaporateur dans une pompe à chaleur air-eau - Google Patents

Appareil de dégivrage rapide d'évaporateur dans une pompe à chaleur air-eau Download PDF

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Publication number
EP3246641A1
EP3246641A1 EP17171090.8A EP17171090A EP3246641A1 EP 3246641 A1 EP3246641 A1 EP 3246641A1 EP 17171090 A EP17171090 A EP 17171090A EP 3246641 A1 EP3246641 A1 EP 3246641A1
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EP
European Patent Office
Prior art keywords
heat pump
cooling medium
evaporator
compressor
pump according
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.)
Withdrawn
Application number
EP17171090.8A
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German (de)
English (en)
Inventor
Lars Friberg
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.)
Lars Friberg Evolution AB
Original Assignee
Lars Friberg Evolution AB
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 Lars Friberg Evolution AB filed Critical Lars Friberg Evolution AB
Publication of EP3246641A1 publication Critical patent/EP3246641A1/fr
Withdrawn legal-status Critical Current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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D3/00—Hot-water central heating systems
    • F24D3/18—Hot-water central heating systems using heat pumps
    • 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0403—Refrigeration circuit bypassing means for the condenser
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0415—Refrigeration circuit bypassing means for the receiver
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/24—Storage receiver heat
    • 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
    • F25B2600/2501—Bypass 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves

Definitions

  • the invention relates to reduction of defrosting times in an air-water heat pump by more than 96 percent. In addition the need for shutting off the heat pump compressor during the defrosting operation. Furthermore it is not required that the air flow through the evaporator contributes to defrosting, apart from it preferably should keep a temperature in excess of 0 °C such that it does not counteract the defrosting.
  • the invention also relates to the enablement of broadening the allowed operational range of the heat pump to encompass even extremely low evaporator temperatures and/or extremely low output power, without any risk for damage to the compressor.
  • Fig. 1 illustrates a prior art heat pump.
  • the evaporator 105 in a highly efficient heat pump normally has a temperature significantly below zero degrees Centigrade and often times as low as 20 degrees below zero.
  • the moisture in the air will deposit on the evaporator 105 and form an increasingly thicker and increasingly more heat insulating layer of ice/frost, which leads to the COP (coefficient of performance) of the evaporator 105 being degraded more and more, which in turn has a detrimental effect on the COP of the heat pump. Therefore the evaporator 105 must be regularly defrosted such that its capacity is restored.
  • an outside air heat pump cannot be defrosted via the air flow when there is a freezing temperature outside, but instead the defrosting energy must be supplied in other ways. In such case the heat must be taken from the compressor or by means of auxiliary electricity, which in turn degrades the average COP.
  • the outside air is to be regarded as an unlimited energy resource, and thus the outdoor air machine can always be dimensioned to produce all heating energy required for the house, during the remaining operative time.
  • the exhaust air itself is always warm enough, slightly more than 20 degrees, to enable defrosting of the evaporator 105.
  • defrosting will however require rather a long time if it is to be ascertained that all ice has been removed.
  • no heat energy can be withdrawn for the actual heating up of the house.
  • the exhaust air is often times a limited energy resource that needs to be utilized as far as possible in order to meet the heating demand during cold periods. In this case there is no possibility to increase the heat withdrawal over and above what the power flow in the exhaust air allows.
  • the energy in the exhaust air is to be seen as a "perishable".
  • the present invention is constituted by supplements to the traditional cooling medium circuit in an air-water heat pump, and is defined in claim 1.
  • the heat pump thereby comprises a cooling medium circuit consisting of a compressor 101, a condenser 102, a cooling medium supply 103, an expansion valve 104 and an evaporator 105.
  • a control unit 106 which controls its function is also associated with the circuit.
  • What is characterizing the invention is a by-pass channel 200 by-passing at least the cooling medium supply 103 and the expansion valve 104, and having a by-pass valve 201 provided in the by-pass channel 200.
  • the by-pass channel 200 by-passes also the condenser 102.
  • the invention includes
  • the open by-pass channel according to point 1 passes the compressor power of about 1-2 kW into the evaporator 105 which becomes heated. Above all the coldest parts of the evaporator are heated, where the heaviest frosting can be expected. Thereby the ice will rapidly melt away from the metal in the evaporator, possible loose frost residues will be completely exposed to the outflowing air and will rapidly melt away. In this way a defrosting, which using traditional methods normally will take at least about 10 minutes (20% of the normal time between two defrosting operations) will be effected in less than two minutes (4% of this time).
  • the cooling medium dome 301 will not add any defrosting function by themselves. However, when the pressure in the dome rapidly decreases due to the by-pass channel 200 opening, the cooling medium condensate contents of the dome will flow in huge amounts through the warm condenser 102 where it immediately is supplied with large heat energy amounts from the heat exchanger of condenser 102 (power of about 30 to 40 kW can be expected), rapidly boils and flows over to the cold evaporator 105 where it rapidly condenses and again releases its 30 to 40 kW. These added 30 to 40 kW will melt away all frost in less than ten seconds (0,33% of the normal time between two consecutive defrosting actions). Possibly the meltwater could require an additional ten seconds for leaving the evaporator. All in all a complete defrosting of the condenser 105 in less than 20 seconds ( ⁇ 0,7% of the normal time between two consecutive defrosting actions).
  • the new invention is defined in claim 1.
  • the invention relates to modification of a conventional cooling medium circuit, Fig. 1 , in a heat pump.
  • the modification is defined above in the descriptions relating to Figs 2-6 .
  • the conventional cooling medium circuit comprises a closed loop having, in order, the following components: a compressor 101, a condensor 102, a cooling medium supply 103 (sometimes referred to as a "receiver"), an expansion valve 104 and an evaporator 105.
  • the flow through the cooling medium circuit is controlled by a dedicated machine control unit 106.
  • the modification comprises:
  • Fig. 4 as an example, the heat pump of Fig. 2 is shown supplemented with a cooling medium dome 301 tempered by return water 1122 and coupled to the cooling medium circuit.
  • a cooling medium dome 301 tempered by return water 1122 and coupled to the cooling medium circuit.
  • the connection of the4 dome 301 should always be located on the opposite side of the condenser 102 relative the bypass conduit 202. In this case at the condenser outlet.
  • the cooling medium dome 301 comprises a closed container, coupled to the high pressure side of the cooling medium circuit at the bottom part via an open connection tube.
  • the connection tube must thus be coupled to the cooling medium circuit somewhere between the compressor outlet 101u and the cooling medium supply 103. Additionally the best effect is achieved if the connection is located on the opposite side of the condenser 102 relative the connection of the bypass channel 200.
  • Cooling medium will flow freely through the connection between dome 301 and cooling medium circuit such that all pressure differences between the dome and the circuit will be eliminated immediately. Due to the connection being located in the bottom of the dome, the outflow from the dome will however always consist of cooling medium condensate that might occur, since condensate will collect at the bottom of the dome.
  • the inflow can on the contrary comprise vapour as well as condensate, fully dependent on the current phase of the medium in the connection to the cooling medium circuit.
  • the medium pressure is determined by the conditions in the condenser and correspond to the condensation pressure of the medium at the current condensation temperature. Since the dome 301 is tempered to a temperature that during normal operation always is below the condenser temperature (when the dome 301 is tempered by exhaust air this means that the condenser temperature should not be below the exhaust air temperature, which by any reasonable standard very rarely happens), the pressure inside the dome during normal operation will substantially exceed the condensation pressure of the cooling medium at current temperature, and hence all cooling medium vapour in the dome 301 will condense and allow inflow of further cooling medium. Thereby the dome 301 after a short period of normal operation or in power reduced operation to be completely filled with cooling medium condensate.
  • the medium pressure will be the same as the current very low condensation pressure in the cold evaporator.
  • a small partial amount of the tempered condensate contents in the dome 301 will then rapidly be flash evaporated and drive all of the remaining condensate out into the cooling medium circuit, further on through the hot condenser for rapid heat uptake, evaporation, expansion and further flow through the wide open bypass channel 200 into the cold evaporator 105.
  • the hot steam will rapidly release its heat energy and condense. This energy transfer can be expected to be largest in the coldest parts of the evaporator, i.e. those parts that carry most frost.
  • the frost matter will thereby rapidly thaw from the inside, come off the evaporator material and be blown away by the exhaust air flow and subsequent possible further thawing and to run off as liquid.
  • the total energy contents in the cooling medium vapour from the dome condensate should be at least as large as the energy that is required for thawing the frost material on the evaporator.
  • the "smallest allowable" volume of the dome 301 is thus determined by the volume of condensate that it must be able to house. This volume is in its turn determined by the amount of ice that has to be melted, the heat of melting per liter of the ice and the heat of evaporation of the current cooling medium per liter of condensate.
  • the melting heat of the ice per liter melt water at zero degrees Celsius can be set to 335 kJ.
  • Fig. 7 shows the heat pump of Fig. 6 in normal operation.
  • the bypass valve is maintained fully closed and the function of the machine completely corresponds to that of a traditional machine according to Fig. 1 .
  • the temperature in the condenser 102 thereby exceeds the incoming temperature of the circulating flow and also to even greater extent its return temperature.
  • the pressure in the condenser 102 in turn exceeds the pressure of condensation of the cooling medium at current temperature. Typical values in this state of operation is about 3°C for the temperature difference across the condensor heat exchanger, and about 6kW for the transfer power to the circulating water.
  • the same pressure prevails during normal operation as in the cooling medium and the condenser 102, but substantially lower temperature, far below the temperature of the cooling medium in the dome 301 at current pressure.
  • Any vapour phase of the cooling in the dome will therefore condense and the volume reduction due to the transfer of vapour to condensate is compensated by a corresponding inflow of cooling medium, in liquid and/or gas phase, from the cooling medium circuit. Any gas that has flown in will condense and new cooling medium will flow in etc.
  • the dome 301 is completely filled with cooling medium condensate.
  • Transition to defrosting operation takes place when the bypass valve 201between the high pressure and low pressure sides of the system is opened. Due to the pressure drop that occurs on the high pressure side a vigorous boiling off of existing cooling medium condensate in the warm condenser 102 occurs. Large amounts of evaporated cooling medium and accompanying large amounts of energy are formed in the condenser 102 and flows out via the condenser inlet and bypass conduit 202 to the evaporator 105 where they immediately are condensed and release their energy. See further under Fig. 8 .
  • Fig. 8 shows the heat pump of Fig. 7 I defrosting operation.
  • the bypass valve 201 is held open at maximum, and there is an almost total pressure levelling between evaporator 105 and condenser 102.
  • the condenser pressure becomes much lower than in normal operation and will be very much lower than the evaporation pressure in the condenser 102 and in the communicating cooling medium dome 301.
  • Any and all cooling medium condensate in the condenser 102 will thus be rapidly flash evaporated during heavy energy uptake, whereby the condenser temperature is lowered to a new equilibrium temperature, substantially lower than in normal operation.
  • the temperature reduction in the condenser 102 brings about a large temperature deficit in the cooling medium relative the circulating water.
  • the temperature deficit in turn causes a very heavy heat flow through the condenser heat exchanger from the circulating water and into the cooling medium, where it drives the evaporation process further.
  • a typical value for the heat exchanging capacity of the condenser 102 is 2 kW per degree of temperature difference. At the new equilibrium temperature one can expect a temperature difference across the heat exchanger of fifteen to twenty degrees, which in turn gives a transfer power of about 30 to 40 kW which supplies energy to the evaporation process in the condensor.
  • the vapour formed flows out of the condenser outlet, bringing with it its about 30 to 40 kW of heat power, and further on through the bypass conduit 202 to the evaporator inlet.
  • the compressor 101 circulates all its flow, against a very low counter-pressure, through the evaporator 105 where the input compressor power (in principle only the idle power of the compressor) contributes a little further to the energy supply.
  • the pressure levelling will in a corresponding manner provide a pressure that is much higher than during normal operation and which is far above the condensation pressure at the current evaporator temperature.
  • the cooling medium vapour in the evaporator 105 is condensed and releases its about 30 to 40 kW inside the evaporator 105, the inner temperature of which is very rapidly increased to such an extent that the released heat power can flow further on and out through the evaporator heat exchanger and reach the cold outside of the evaporator 105 where the temperature almost immediately rises to the melting temperature of the water and rapidly causes the frost to begin melting.
  • the evaporator 105 has a neat exchanging capacity of about 2 kW per degree of temperature difference, and hence the released heat power of about 30 to 40 kW causes an equilibrium temperature about 15 to 20 degrees above the 0 degrees prevailing in the melt water on the outside of the evaporator 105.
  • cooling medium condensate 3011 will collect in the evaporator 105 and in any condensate depots during defrosting. This collected amount of condensate will rapidly evaporate on transition to normal operation and will in less than one minute via the compressor return the used defrosting heat to the circulating water.
  • the machine is kept in defrosting operation by the control unit 203 as long as, but only that long, there is any frost remaining on the evaporator 105. Due to the very efficient defrosting, the total time in this state will be extremely short, not more than a few seconds, which is almost neglectable compared to the total time for a corresponding conventional defrosting. Also, the energy consumption and energy loss due to defrosting will be so much lower than what it would have been during traditional exhaust air driven defrosting.
  • the control unit 203 places the machine in defrosting operation at even time intervals in order to keep the accumulated amount of frost on the evaporator 105 on an optimal level.
  • optimal level is to be understood the level that over a complete heating/defrosting cycle yields the highest average heat power production and the highest average COP, in a mutual optimal balance.
  • the control unit 203 also monitors the defrosting process and closes the bypass valve 201 as soon as all frost has been removed from the evaporator 105.
  • Figs. 10 and 11 show the heat pump of Fig.2 and 6 , respectively, in power reduced operation.
  • the bypass valve is controlled by the control unit 203 to let a suitable portion of the hot gas flow from the compressor 101 pass directly to the evaporator inlet.
  • the gas flow and power flow into the condenser 102 will be reduced as will pressure and temperature in the condenser 102.
  • the medium flow into the evaporator inlet will be affected to be as desired and suitable in terms of temperature, pressure and extent of flow.
  • Fig. 12 shows the principle for a particularly highly efficient version of the cooling medium dome.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Defrosting Systems (AREA)
EP17171090.8A 2016-05-17 2017-05-15 Appareil de dégivrage rapide d'évaporateur dans une pompe à chaleur air-eau Withdrawn EP3246641A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
SE1650658A SE542633C2 (sv) 2016-05-17 2016-05-17 Anordning för snabbavfrostning utan kompressorstopp av förångaren i en luft-vatten-värmepump och för att köra värmepumpen vid extremt låga förångartemepraturer och vid extremt lågalaster

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EP3246641A1 true EP3246641A1 (fr) 2017-11-22

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EP17171090.8A Withdrawn EP3246641A1 (fr) 2016-05-17 2017-05-15 Appareil de dégivrage rapide d'évaporateur dans une pompe à chaleur air-eau

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SE (1) SE542633C2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019146070A1 (fr) * 2018-01-26 2019-08-01 三菱電機株式会社 Dispositif à cycle de réfrigération
CN110454944A (zh) * 2019-08-26 2019-11-15 重庆美的通用制冷设备有限公司 空调器的控制方法、装置及空调器
CN112888586A (zh) * 2018-12-21 2021-06-01 大众汽车股份公司 用于运行电动车辆的热泵的方法

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4646539A (en) * 1985-11-06 1987-03-03 Thermo King Corporation Transport refrigeration system with thermal storage sink
JPH07248166A (ja) * 1994-03-14 1995-09-26 Nippondenso Co Ltd 冷凍装置
US20050132729A1 (en) * 2003-12-23 2005-06-23 Manole Dan M. Transcritical vapor compression system and method of operating including refrigerant storage tank and non-variable expansion device
JP2007170758A (ja) * 2005-12-22 2007-07-05 Sanden Corp 冷凍装置
WO2009140370A2 (fr) * 2008-05-14 2009-11-19 Carrier Corporation Gestion de la charge dans des systèmes de réfrigération à compression de vapeur
GB2487975A (en) * 2011-02-11 2012-08-15 Frigesco Ltd Flash defrost system
WO2014092152A1 (fr) * 2012-12-14 2014-06-19 シャープ株式会社 Cycle de réfrigération et climatiseur équipé de celui-ci
WO2014098724A1 (fr) * 2012-12-21 2014-06-26 Fläkt Woods AB Procédé et appareil de dégivrage d'un évaporateur en relation avec une unité de conditionnement d'air

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4646539A (en) * 1985-11-06 1987-03-03 Thermo King Corporation Transport refrigeration system with thermal storage sink
JPH07248166A (ja) * 1994-03-14 1995-09-26 Nippondenso Co Ltd 冷凍装置
US20050132729A1 (en) * 2003-12-23 2005-06-23 Manole Dan M. Transcritical vapor compression system and method of operating including refrigerant storage tank and non-variable expansion device
JP2007170758A (ja) * 2005-12-22 2007-07-05 Sanden Corp 冷凍装置
WO2009140370A2 (fr) * 2008-05-14 2009-11-19 Carrier Corporation Gestion de la charge dans des systèmes de réfrigération à compression de vapeur
GB2487975A (en) * 2011-02-11 2012-08-15 Frigesco Ltd Flash defrost system
WO2014092152A1 (fr) * 2012-12-14 2014-06-19 シャープ株式会社 Cycle de réfrigération et climatiseur équipé de celui-ci
WO2014098724A1 (fr) * 2012-12-21 2014-06-26 Fläkt Woods AB Procédé et appareil de dégivrage d'un évaporateur en relation avec une unité de conditionnement d'air

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019146070A1 (fr) * 2018-01-26 2019-08-01 三菱電機株式会社 Dispositif à cycle de réfrigération
CN112888586A (zh) * 2018-12-21 2021-06-01 大众汽车股份公司 用于运行电动车辆的热泵的方法
CN110454944A (zh) * 2019-08-26 2019-11-15 重庆美的通用制冷设备有限公司 空调器的控制方法、装置及空调器

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SE1650658A1 (sv) 2017-11-18
SE542633C2 (sv) 2020-06-23

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