WO2006114983A1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

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Publication number
WO2006114983A1
WO2006114983A1 PCT/JP2006/306686 JP2006306686W WO2006114983A1 WO 2006114983 A1 WO2006114983 A1 WO 2006114983A1 JP 2006306686 W JP2006306686 W JP 2006306686W WO 2006114983 A1 WO2006114983 A1 WO 2006114983A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
hot water
evaporator
heat
heat exchanger
Prior art date
Application number
PCT/JP2006/306686
Other languages
English (en)
Japanese (ja)
Inventor
Masaya Honma
Yuuichi Yakumaru
Kou Komori
Original Assignee
Matsushita Electric Industrial Co., Ltd.
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 Matsushita Electric Industrial Co., Ltd. filed Critical Matsushita Electric Industrial Co., Ltd.
Publication of WO2006114983A1 publication Critical patent/WO2006114983A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H4/00—Fluid heaters characterised by the use of heat pumps
    • F24H4/02—Water heaters
    • F24H4/04—Storage heaters
    • 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
    • B60H1/3228—Cooling devices using compression characterised by refrigerant circuit configurations
    • B60H1/32281—Cooling devices using compression characterised by refrigerant circuit configurations comprising a single secondary circuit, e.g. at evaporator or condenser side
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • 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
    • B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
    • B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
    • B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
    • B60H2001/00961—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising means for defrosting outside heat exchangers
    • 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
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • 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

  • the present invention relates to a refrigeration cycle apparatus that uses hot air as heat source to collect heat with an evaporator.
  • FIG. 8 shows a conventional heat pump device described in Patent Document 1. As shown in FIG.
  • this heat pump device has a compressor 40, a four-way valve 41 as a cooling / heating switching valve, an indoor heat exchanger 42, an indoor decompression device 43, an outdoor decompression device 44, and an outdoor heat exchanger 45 in this order. It is connected so as to be a closed circuit.
  • a hot water supply pressure reducing device 47 is installed at the outlet of the hot water supply heat exchange, and the inlet of the hot water supply heat exchanger 46 is connected to the piping between the discharge side of the compressor 40 and the four-way valve 41 for hot water supply.
  • the outlet of the heat exchanger 46 is connected to a pipe between the indoor decompression device 43 and the outdoor decompression device 44 via a hot water decompression device 47, thereby forming a refrigerant circulation circuit.
  • the circulation pump 48 is activated to perform the defrosting operation using the hot water in the hot water storage tank 49 as a heat source.
  • the circulation pump is operated to circulate the hot water in the hot water storage tank to the heat exchanger near the evaporator, and the evaporator is heated to thereby form the frost formation. Arise I was trying not to let it.
  • Patent Document 1 Japanese Patent Application Laid-Open No. 2004-218944
  • Patent Document 2 Japanese Utility Model Publication No. 55-96370
  • Patent Document 3 Japanese Utility Model Publication No. 55-17126
  • the present invention has been made in view of the above-described problems of the prior art, and is provided with a hot water refrigerant heat exchanger on the inlet side of the evaporator to remove the frost without reducing the heating capacity.
  • An object of the present invention is to provide a refrigeration cycle apparatus capable of performing the above.
  • the present invention provides a compressor that compresses a refrigerant, a radiator that exchanges heat between the refrigerant compressed by the compressor and water, and supplies hot water to a use terminal, and a radiator
  • An expansion mechanism that reduces the pressure of the refrigerant radiated by the refrigerant and an evaporator that evaporates the refrigerant reduced by the expansion mechanism are connected by a refrigerant path, and hot water and refrigerant are connected to the refrigerant path between the expansion mechanism and the evaporator.
  • a hot water refrigerant heat exchanger for heat exchange is provided.
  • the refrigerant in the refrigerant path between the expansion mechanism and the evaporator can be efficiently heated with hot water, so that hot water can be continuously generated, Addition A defrosting operation without reducing the heat capacity can be performed.
  • FIG. 1 is a configuration diagram of a refrigeration cycle apparatus according to a first embodiment of the present invention.
  • FIG. 2 is a configuration diagram of a refrigeration cycle apparatus according to a modification of the first embodiment of the present invention.
  • Fig. 3 is a partial sectional plan view of the hot water refrigerant heat exchanger provided in the refrigeration cycle apparatus of Fig. 1 or Fig. 2.
  • FIG. 4 is a Mollier diagram of the refrigeration cycle according to the first embodiment of the present invention.
  • FIG. 5 is a graph showing the relationship between the refrigerant dryness and the refrigerant heat transfer coefficient according to the first embodiment of the present invention.
  • FIG. 6 is a configuration diagram of a refrigeration cycle apparatus according to a second embodiment of the present invention.
  • FIG. 7 is a block diagram of a modified example of the refrigeration cycle apparatus of FIG.
  • Figure 8 shows the configuration of a conventional heat pump device
  • FIG. 1 is a configuration diagram of a refrigeration cycle apparatus 10 with a hot water tank according to a first embodiment of the present invention, which includes a refrigeration cycle 11, a hot water tank 12, a hot water supply load unit 13 as a use terminal, and a controller 14. It is composed of carbon dioxide as a refrigerant.
  • a compressor 15, a radiator 16, an expansion valve 17, which is an expansion mechanism, a hot water refrigerant heat exchanger 18, and an evaporator 19 are connected through a path through which a refrigerant flows to form a closed cycle.
  • the hot water refrigerant heat exchanger 18 is provided downstream of the expansion valve 17 and upstream of the evaporator 19 in the refrigerant flow.
  • the refrigerant is discharged at a high temperature and high pressure by the compressor 15, and dissipates heat by exchanging heat with the cold water supplied from the hot water storage tank 12 by the radiator 16.
  • the refrigerant heat-exchanged with the cold water is reduced in pressure by the expansion valve 17 and then heated by hot water supplied from the hot water tank 12 by the hot water refrigerant heat exchanger 18 as necessary, and heat from the atmosphere is obtained by the evaporator 19. Take it, vaporize, and return to compressor 15.
  • the refrigerant is heated by the hot water refrigerant heat exchanger 18 when the evaporator 19 needs to be defrosted, and when the evaporator 19 does not need to be defrosted, the hot water refrigerant heat exchange is performed. Do not pour hot water into 18
  • the cold water drawn from the lower part of the hot water storage tank 12 is radiated by the first circulation pump 20 to the radiator.
  • the hot water in the hot water tank 12 is circulated by the first circulation pump 20 by a temperature sensor (not shown) provided in the hot water tank 12 until the set temperature is reached.
  • a temperature sensor not shown
  • cold water and hot water form a temperature stratification, so the temperature of the stored water increases from the lower part of the hot water storage tank 12 toward the upper part.
  • the hot water in the hot water storage tank 12 that has reached the set temperature is supplied from the upper part of the hot water storage tank 12 to the hot water supply load unit 13 such as a bath tank.
  • the lower part of the hot water storage tank 12 is connected to a water supply source 24 via an electromagnetic valve 23, and a level detector (not shown) such as a float switch is provided inside the hot water storage tank 12.
  • a level detector such as a float switch
  • the solenoid valve 23 is controlled to open, and the hot water storage tank 12 is supplied with water.
  • the solenoid valve 23 is closed and the water supply from the water supply source 24 is stopped.
  • the controller 14 includes a microcomputer, and a refrigerant temperature detector 21 such as a thermistor for measuring the refrigerant evaporation temperature at the inlet of the evaporator 19, and hot water stored in the hot water tank 12 is used as a hot water refrigerant heat exchanger.
  • the second circulating pump 22 supplied to 18 and the above-described solenoid valve 23 and the like are connected via a signal line 25.
  • a signal for operating the second circulation pump 22 is output from the refrigerant temperature detector 21 to the controller 14, and the controller 14
  • the second circulation pump 22 is activated in response to the output signal from the hot water, the hot water taken out from the central part of the hot water tank 12 is heated by the hot water refrigerant heat exchanger 18 to heat the refrigerant at the lower part of the hot water tank 12.
  • the refrigeration cycle apparatus 10 shown in FIG. 1 heats cold water stored in the hot water tank 12 at night by using inexpensive late-night power, for example, when the capacity of the hot water tank 12 is relatively large. Is suitable when the hot water stored in the hot water tank 12 covers all of the hot water consumed by the hot water supply load unit 13.
  • FIG. 2 shows a modified example 10A of the refrigeration cycle apparatus 10 shown in FIG. 1, and this refrigeration cycle apparatus 10A has a configuration suitable when the capacity of the hot water tank 12 is relatively small.
  • this refrigeration cycle apparatus 10A has a configuration suitable when the capacity of the hot water tank 12 is relatively small.
  • differences between this refrigeration cycle apparatus 10A and the above-described refrigeration cycle apparatus 10 will be described.
  • the hot water tank 12, the radiator 16, and the first circulation pump 20 are connected in a loop like the refrigeration cycle device 10 of Fig. 1. It is also connected to the water supply 24 via a valve 23.
  • the first circulation pump 20 is connected to the hot water storage tank 12 via a check valve 26 and a three-way valve 27, and the three-way valve 27 is further connected to the hot water supply load unit 13.
  • the pipe between the three-way valve 27 and the hot water supply load unit 13 is connected to the pipe connecting the hot water tank 12 and the second circulation pump 22, and the pipe connecting the radiator 16 and the solenoid valve 23. It is connected via an on-off valve 28.
  • the solenoid valve 23 is controlled to open to store water in the hot water storage tank 12, and the first circulation pump 20 is driven to store cold water stored in the hot water storage tank 12 with a predetermined amount. Heated to temperature.
  • the solenoid valve 23 is controlled to open and water is supplied from the water supply source 24 to the hot water tank 12, but all of the hot water stored in the hot water tank 12 is lost.
  • the hot water is directly supplied from the radiator 16 to the hot water supply load unit 13 by the first circulation pump 20, so that hot water can be used in the hot water supply load unit 13.
  • the hot water from the heat radiator 16 is supplied to the second circulation pump 22 by the first circulation pump 20, and the heat exchange of the hot water refrigerant is further performed. Since the hot water is directly supplied to the hot water tank, the predetermined defrosting can be performed even when the hot water tank 12 becomes empty.
  • the temperature of the hot water used in the hot water supply load unit 13 can be lowered, and the hot water supplied from the hot water tank 12 or the first circulation pump 20 can be used.
  • cold water from the water supply source 24 is also supplied to the hot water supply load unit 13. Can be used.
  • the above-described operation is automatically performed by using a solenoid valve that is preferably composed of an electromagnetic valve whose opening degree can be adjusted as the three-way valve 27 and the on-off valve 28.
  • the hot water refrigerant heat exchange can employ various structures, but the double tube structure shown in Fig. 3 is preferred.
  • the hot water refrigerant heat exchange is constituted by a double pipe,
  • the refrigerant is flown in the pipe on the side and the hot water from the hot water storage tank 12 is allowed to flow in the outer pipe so as to exchange heat between the refrigerant and the hot water.
  • the temperature of the refrigerant having a high heat exchange efficiency between the hot water and the refrigerant tends to be uniform.
  • the heat transfer rate from the hot water to the refrigerant is 100WZm 2 K ⁇ 15, 000WZm 2 K .
  • the Mollier diagram in FIG. 4 shows the case where the refrigerant is carbon dioxide, and the saturation curve 50 shows a line connecting the saturated liquid line and the saturated vapor line.
  • the closed cycle A B C D 51 is a Mollier diagram in the case where the atmospheric temperature is high and the evaporation pressure is high, and it is not necessary to defrost the evaporator.
  • the effects of the refrigeration cycle apparatuses 10, 10A of the first embodiment of the present invention Will be described.
  • the following shows the amount of heat required for defrosting of the evaporator 19 according to the present invention, and the amount of heat generated when defrosting is not performed.
  • an evaporator with a heat exchange amount H of 3.25kW the dry bulb temperature in the atmosphere before passing through the evaporator is 7 ° C, the wet bulb temperature is 6 ° C, and the dry bulb temperature after passing through the evaporator The case where the wet bulb temperature is 2 ° C is explained.
  • the flow rate G (m 3 Zs) of the evaporator is as follows from (Equation 1).
  • V f px GxAx x 3600
  • ⁇ : V 2.066 from the absolute humidity difference (0.00539 kg / kg-0.0045 kg / kg) before and after passing through the evaporator.
  • the amount of heat Q (kjZh) required to melt this amount of frost formation V is (f f 1
  • the refrigeration cycle apparatuses 10 and 10A of the first embodiment of the present invention even when the evaporator 19 is frosted, hot water refrigerant heat exchange is performed while continuing the generation of hot water.
  • the refrigerant can be defrosted by heating in the vessel 18.
  • the amount of heat required for defrosting is 723 kjZh, which is about 1Z3 of the amount of heat 2160 kjZh that does not contribute to hot water generation in the case of the conventional defrosting operation in which the refrigerant flow is reversed.
  • the heat transfer coefficient of heat exchange for circulating the hot water from the hot water tank in the vicinity of the evaporator and heating the evaporator is 5 WZm 2 K to 25 WZm 2 K
  • the hot water refrigerant of the present invention heat exchanger 100WZm 2 K ⁇ 15 since it is 000WZm 2 K, it is much more heat transfer coefficient towards the present invention. Therefore, it is better to use the hot water refrigerant heat exchange 18 of the refrigeration cycle apparatus 10, 10A with the hot water tank of the first embodiment of the present invention than to use the heat exchange that heats the evaporator. Therefore, the amount of heat used for defrosting is small.
  • Figure 5 shows the relationship of the refrigerant heat transfer coefficient to the dryness of the heat exchanger (air conditioning, Proceedings of the Refrigeration Union Lecture, VOL. 37th; PAGE 124). As shown in Fig. 5, heat exchange is performed on the inlet side where the refrigerant heat transfer coefficient is higher on the inlet side of the heat exchanger (refrigerant dryness of 0.2) than on the outlet side (refrigerant dryness of 1). Can obtain a higher amount of heat exchange.
  • the reason why the refrigerant heat transfer rate is higher on the heat exchanger inlet side (refrigerant dryness of 0.2) than on the outlet side (refrigerant dryness of 1) is that the heat exchanger inlet side is Most of them are liquid, but most of the refrigerant is gas at the outlet, and the heat transfer coefficient of liquid refrigerant is several times higher than that of gas refrigerant.
  • the refrigerant is superheated beyond the outlet side.
  • the local heat transfer coefficient decreases rapidly, it is installed on the heat inlet side where the local heat transfer coefficient is kept high on average. It is possible to obtain a higher amount of heat exchange when placed.
  • the amount of heat used for defrosting can be reduced while continuing the generation of hot water.
  • the original amount of hot water used can be increased.
  • a sufficient amount of heat exchange can be secured by providing hot water refrigerant heat exchange on the inlet side of the evaporator.
  • a force indicating a method for detecting and controlling the refrigerant temperature at the inlet of the evaporator 19 is detected and the value is input to the controller 14.
  • the method may be used.
  • the measurement position may be inside the evaporator without being limited to the evaporator inlet.
  • FIG. 6 shows a refrigeration cycle apparatus 30 with a hot water tank according to the second embodiment of the present invention.
  • the refrigeration cycle 31 has the same configuration as the refrigeration cycle 11 of the first embodiment of the present invention except that an indoor heat exchange 32 is provided between the radiator 16 and the expansion valve 17.
  • devices having the same functions are denoted by the same reference numerals as those in the first embodiment of the present invention, and description of the configuration and operation thereof is omitted.
  • the indoor heat exchange is provided in the refrigerant path between the radiator 16 and the expansion valve 17, and heats the room air to heat the room to be heated 33.
  • a blower fan 34 is provided in the vicinity of the indoor heat exchanger 32 in order to promote heat exchange between the indoor heat exchanger 32 and the indoor air.
  • the cooling heat radiated by the radiator 16 which is a heat exchanger for hot water supply is used.
  • the medium is further radiated by indoor heat exchange 32.
  • the heated room 33 can be heated by the indoor heat exchanger 32 while hot water is generated by the radiator 16.
  • the refrigerant temperature detector 21 detects whether frost has been formed, and the refrigerant temperature detector 21 detects a predetermined temperature or lower.
  • the second circulation pump 22 is operated, and the hot water in the hot water storage tank 12 is caused to flow through the hot water refrigerant heat exchanger 18.
  • the evaporator 19 can continue the heat collecting operation without frost formation, and the indoor heat exchanger 32 can continue to heat the heated room 33 while the radiator 16 generates hot water.
  • a conventional refrigeration cycle apparatus that performs heating performs a defrosting operation, and during the defrosting operation, cool air is not sent indoors, so that the blower fan near the indoor heat exchange is stopped, The As described above, since the heating operation is completely stopped during the defrosting operation in the past, the user is uncomfortable, but according to the second embodiment of the present invention, the heating operation is stopped. Hana! ⁇ so don't give the user such a bad feeling.
  • the indoor heat exchanger 32 is provided in series on the downstream side of the radiator 16, but the indoor heat exchanger 32 may be provided in series on the upstream side of the radiator 16. .
  • the heated room 33 can be heated by the indoor heat exchanger 32 while generating hot water by the radiator 16, as described above.
  • the capacity of the upstream equipment heatsink 16 or indoor heat exchange 32
  • the capacity of the downstream equipment room heat exchange or heatsink 16
  • the capacity of the hot water tank 12 is set to be relatively large. For example, hot water is generated at midnight and stored in the hot water tank 12, while heating operation is performed during daytime and nighttime as needed and the hot water is stored. When necessary, hot water stored in the hot water tank 12 may be used.
  • FIG. 1 In the case where it is desired to simultaneously generate hot water and heat in a state where the capabilities of both the radiator 16 and the indoor heat exchanger 32 are sufficiently secured (a state where the heated fluid can be sufficiently heated), FIG. As shown in the figure, the indoor heat exchanger 32 and the radiator 16 may be connected in parallel in the path of the counter-current refrigerant from the compressor 15 to the expansion valve 17. Further, a part of the radiator 16 may be used as the indoor heat exchanger 32.
  • the refrigerant temperature detector 21 is employed as the frost detection means, and the evaporation temperature of the refrigerant measured by the refrigerant temperature detector 21 is equal to or less than a predetermined value. Then, it is determined that the evaporator 19 is frosted and the second circulation pump 22 is operated to heat the refrigerant with the hot water refrigerant heat exchanger 18, but the refrigerant temperature detector 21 is used instead.
  • the following detectors can also be employed as the frost detection means.
  • an expansion valve is used as an expansion mechanism, but an expansion machine using an electric motor as a drive source may be used.
  • the refrigeration cycle apparatus with a hot water tank that is effective in the present invention can reduce the amount of hot water used in the hot water tank for defrosting and increase the amount of original hot water supply. It is useful as a heating device.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

L’invention concerne un échangeur thermique eau tiède/réfrigérant (18) pour échanger la chaleur entre l’eau tiède et le réfrigérant dans un circuit réfrigérant entre un mécanisme d’expansion (17) et un évaporateur (19). Si une détection de température de réfrigérant (21) indique une température, par exemple, inférieure ou égale à 0ºC, une seconde pompe de circulation (22) est actionnée pour provoquer l’écoulement d’eau tiède dans un conteneur d’eau tiède (12) vers l’échangeur thermique eau tiède/réfrigérant (18). Cette opération chauffe le réfrigérant pour augmenter la pression d’évaporation, et la chaleur est recueillie par l’évaporateur (19) tandis que l’évaporateur (19) est décongelé. Même si la pression de vapeur augmente avec le dégivrage, un cycle réfrigérant (11) continue le recueil de chaleur de façon à produire en continu de l’eau tiède.
PCT/JP2006/306686 2005-04-25 2006-03-30 Dispositif à cycle de réfrigération WO2006114983A1 (fr)

Applications Claiming Priority (2)

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JP2005126035A JP2008170015A (ja) 2005-04-25 2005-04-25 貯湯槽付き冷凍サイクル装置
JP2005-126035 2005-04-25

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CN101504210B (zh) * 2009-03-17 2011-07-20 贝莱特空调有限公司 一种六合一风冷热泵机组
EP2458304A3 (fr) * 2010-11-24 2014-06-18 Glen Dimplex Deutschland GmbH Installation de pompe à chaleur comprenant une pompe à chaleur et procédé de fonctionnement d'une telle installation de pompe à chaleur
EP2918921A1 (fr) * 2014-03-12 2015-09-16 Panasonic Intellectual Property Management Co., Ltd. Générateur d'eau chaude
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EP4048958A4 (fr) * 2019-10-25 2023-08-30 M.E.D. Energy Inc. Procédé de transmission d'énergie thermique en utilisant de l'eau et du dioxyde de carbone

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JP2010091129A (ja) * 2008-10-03 2010-04-22 Daikin Ind Ltd 熱交換器および温水システム
JP5816422B2 (ja) * 2010-08-27 2015-11-18 日立アプライアンス株式会社 冷凍装置の排熱利用システム
JP2012207915A (ja) * 2012-07-30 2012-10-25 Daikin Industries Ltd 熱交換器および温水システム
WO2015118580A1 (fr) * 2014-02-10 2015-08-13 三菱電機株式会社 Dispositif d'alimentation en eau chaude d'une pompe à chaleur

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EP2375195A4 (fr) * 2009-01-05 2016-08-24 Mitsubishi Electric Corp Chauffe-eau du type pompe a chaleur
CN101504210B (zh) * 2009-03-17 2011-07-20 贝莱特空调有限公司 一种六合一风冷热泵机组
EP2458304A3 (fr) * 2010-11-24 2014-06-18 Glen Dimplex Deutschland GmbH Installation de pompe à chaleur comprenant une pompe à chaleur et procédé de fonctionnement d'une telle installation de pompe à chaleur
EP2918921A1 (fr) * 2014-03-12 2015-09-16 Panasonic Intellectual Property Management Co., Ltd. Générateur d'eau chaude
EP4048958A4 (fr) * 2019-10-25 2023-08-30 M.E.D. Energy Inc. Procédé de transmission d'énergie thermique en utilisant de l'eau et du dioxyde de carbone

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