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WO2010143373A1 - Système de pompe à chaleur - Google Patents

Système de pompe à chaleur Download PDF

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Publication number
WO2010143373A1
WO2010143373A1 PCT/JP2010/003611 JP2010003611W WO2010143373A1 WO 2010143373 A1 WO2010143373 A1 WO 2010143373A1 JP 2010003611 W JP2010003611 W JP 2010003611W WO 2010143373 A1 WO2010143373 A1 WO 2010143373A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
path
heat
circulation
tank
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.)
Ceased
Application number
PCT/JP2010/003611
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English (en)
Japanese (ja)
Inventor
岡市敦雄
塩谷優
和田賢宣
尾形雄司
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.)
Panasonic Corp
Original Assignee
Panasonic Corp
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 Panasonic Corp filed Critical Panasonic Corp
Publication of WO2010143373A1 publication Critical patent/WO2010143373A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F24D11/00—Central heating systems using heat accumulated in storage masses
    • F24D11/02—Central heating systems using heat accumulated in storage masses using heat pumps
    • F24D11/0214—Central heating systems using heat accumulated in storage masses using heat pumps water heating system
    • 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
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
    • F24D19/1009—Arrangement or mounting of control or safety devices for water heating systems for central heating
    • F24D19/1039—Arrangement or mounting of control or safety devices for water heating systems for central heating the system uses a heat pump
    • 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
    • F24D3/08—Hot-water central heating systems in combination with systems for domestic hot-water supply
    • 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

Definitions

  • the present invention relates to a heat pump system used in, for example, an air conditioner, a heat pump water heater, a heat pump heater, and the like.
  • Patent Document 1 discloses a heat pump system 501 that is a hot water supply apparatus including a heat source unit 503 including a heat pump circuit and a hot water storage unit (tank unit) 502 as shown in FIG.
  • the heat pump system 501 water is used as the heat storage fluid, and when the hot water supplied to the bathtub is cooled, the heat of the hot water in the tank 511 passes through the intermediate heat exchanger 533 and the circulating water circuit 534 which is a heat medium circuit. Through the heating heat dissipating part 538, the hot water in the bathtub is reheated. For this reason, the intermediate heat exchanger 533 generates intermediate temperature water between the low temperature tap water supplied into the tank 511 and the boiled high temperature hot water, and the intermediate temperature water is stored in the tank 511.
  • the radiator outlet temperature of the carbon dioxide heat exchanged with the intermediate warm water by the radiator 521 increases.
  • the heating capacity decreases (refrigerant circulation amount ⁇ (h A ⁇ h B ) ⁇ refrigerant circulation amount ⁇ (h A ⁇ h E ))
  • the COP Coefficient of Performance
  • a heating device that performs floor heating or the like is heated using the circulating water in the circulating water circuit 534. That is, when heating the heating equipment, the circulating water whose temperature has been lowered using the high-temperature water in the tank 511 is heated by the intermediate heat exchanger 533, so that medium-temperature water is similarly generated and COP is lowered. .
  • the evaporator absorbs heat from the outside air and heats the refrigerant, so that the refrigerant passing through the evaporator has a lower temperature than the outside air. Therefore, when the outside air temperature decreases and the refrigerant temperature of the evaporator becomes below freezing point, water vapor freezes on the surface of the evaporator and frosting occurs.
  • a hot gas bypass passage provided with a constant pressure expansion valve 805 that bypasses the condenser 802 and the expansion valve 803 has been provided (see Non-Patent Document 1). ).
  • the heat radiation in the condenser 802 is stopped, and the high-temperature refrigerant compressed by the compressor 801 is guided to the evaporator 804, thereby melting the frost formed on the surface of the evaporator 804. Since the defrosting performed in this way heats the evaporator 804 using the energy of the refrigerant increased by the compression work performed by the compressor 801, the defrosting operation for the defrosting of the evaporator 804 is a heat release. Considering the loss, the evaporator 804 can be heated only with a heating capacity lower than that of the input of the compressor 801.
  • Patent Document 1 it is proposed to perform boiling and defrosting using medium-temperature water accumulated in the tank 511. Specifically, as shown in FIG. 8, at the time of boiling, the medium-temperature water accumulated in the tank 511 is supplied to the auxiliary evaporator 523, and the refrigerant is heated not only by the outside air but also by the medium-temperature water. Accordingly, the intermediate temperature water is cooled, and the low temperature water is returned to the bottom of the tank 511, so that the intermediate temperature water is reduced and the water temperature supplied to the radiator 521 is decreased.
  • the refrigerant circulating through the heat pump circuit is heated by supplying medium temperature water to the auxiliary evaporator 523. That is, the heat of the water in the tank 511 that is efficiently heated by the heat pump circuit is used as a heating source for the refrigerant used for defrosting. Therefore, since the input spent for the defrosting operation can be reduced, the COP of the heat pump system 501 is improved. However, since the refrigerant flows through the entire heat pump circuit, the pressure loss in the piping is large, and a pressure difference is generated between the suction side and the discharge side of the compressor 525.
  • Patent Document 2 discloses that medium-temperature water generated in the heater 912 and stored in the tank 909 is sent to the second evaporator 908 to heat the refrigerant, and the cooled water is supplied to the lower part of the tank 909.
  • a heat pump system 900 is disclosed for return.
  • the medium-temperature water increases during the boiling operation
  • the medium-temperature water and the expanded refrigerant are supplied to the second evaporator 908, and the water cooled by heat exchange with the refrigerant is stored in the tank 909. Return to the bottom. For this reason, low-temperature water is supplied to the radiator 902, and the cycle efficiency of the heat pump circuit 930 is improved.
  • the heating efficiency of the heat pump system 900 in which the input to the compressor 901 is a denominator and the heating amount of water in the tank 909 is a numerator is low.
  • the operation rate of the 1st evaporator 904 falls by utilizing the 2nd evaporator 908, time until it enters into a defrost operation becomes long, and an efficient driving
  • the time until defrosting is extended only warms the water in the tank 909 with the heat of the water stored in the tank 909, and the input to the compressor 901 is increased. And the heating efficiency of the heat pump system 900 using the heating amount of water in the tank 909 as a numerator is significantly reduced.
  • Patent Document 3 discloses a hot water supply apparatus that simultaneously performs heating of the evaporator 1016 with hot water in the tank 1002 and heating of the evaporator 1016 with hot gas during defrosting, as shown in FIGS. 13 and 14A and 14B.
  • a heat pump system 1000 is disclosed. Specifically, in the heat pump system 1000, the evaporator 1016 is provided with a heating unit 1028 that is a flow path constituted by water piping, and at the time of defrosting, the hot water in the tank 1002 is sent to the heating unit 1028.
  • the compressor 1014 is driven and the hot gas bypass valve 1021 is opened.
  • the evaporator 1016 has a low temperature, so that the water falling operation is performed for the purpose of preventing the water in the heating unit 1028 from freezing.
  • the medium temperature water in the tank 1002 is supplied to the water-refrigerant heat exchanger 1004 and the heating unit 1028, so that the boiling operation can be performed while defrosting.
  • the provision of the heating unit 1028 in the evaporator 1016 causes a decrease in the performance of the evaporator 1016 such as an increase in air-side pressure loss of the evaporator 1016 and a decrease in the area of the fin 1035.
  • the net amount of heat that heats the water in the tank 1002 is only the work of the compressor, and the input to the compressor 1014 is Heating efficiency of the heat pump system 1000 using the heating amount of water in the denominator and tank 1002 as a numerator is low.
  • an object of the present invention is to provide a heat pump system capable of a highly efficient defrosting operation while preventing a decrease in heating efficiency.
  • a heat pump system includes a compressor that compresses a refrigerant, a radiator that exchanges heat between the compressed refrigerant and a heat storage fluid, an expansion unit that expands the refrigerant flowing out of the radiator, and the expanded refrigerant
  • a heat pump circuit including an evaporator for evaporating the water, a tank for storing the heat storage fluid, a boiling path for boiling the heat storage fluid, a forward side path for sending the heat storage fluid in the tank to the radiator, and the A heating path including a return side path for returning a heat storage fluid from a radiator to the tank, a portion between the expansion means and the evaporator in the heat pump circuit, and a portion between the evaporator and the compressor are connected.
  • a defrosting path provided with a refrigerant pump, a circulation path for circulating the heat storage fluid in the tank, a refrigerant flowing through the defrosting path, and a heat storage fluid flowing through the circulation path Those comprising a refrigerant heater for heating the refrigerant by performing heat exchange, the.
  • heat can be absorbed by an evaporator without using a refrigerant heater at the time of boiling, so that a reduction in heating efficiency can be prevented.
  • a refrigerant is circulated using the conventional compressor by circulating a refrigerant
  • the refrigerant circulates through the defrosting circuit having a length shorter than that of the heat pump circuit, so that the pressure loss in the pipe is small and the input of the refrigerant pump is further reduced.
  • defrosting is performed using the heat of the heat storage fluid in the tank heated with high efficiency by the heat pump, the input spent for defrosting is significantly reduced compared to the conventional defrosting by hot gas bypass. .
  • defrosting is performed using a refrigerant pipe path provided in a general evaporator, it is not necessary to provide a separate heat storage fluid pipe path in the evaporator, so heat storage can be performed without degrading the performance of the evaporator. Defrosting with fluid can be realized. Therefore, an efficient heat pump system can be provided.
  • the present invention it is possible to reduce the input necessary for defrosting by circulating the refrigerant by the refrigerant pump and using the heat storage fluid heated with high efficiency for defrosting the evaporator.
  • it is not necessary to change the configuration of the evaporator in order to obtain the above effect it is possible to realize a heat pump system in which the performance of the evaporator does not deteriorate.
  • FIG. 1 is a schematic configuration diagram showing a heat pump system according to a first embodiment of the present invention. Explanatory drawing of the boiling operation state in the heat pump system of FIG. Explanatory drawing of the defrost operation state in the heat pump system of FIG. Flowchart of defrosting operation in heat pump system of FIG. The schematic block diagram which shows the heat pump system which concerns on 2nd Embodiment of this invention. Explanatory drawing of the operation state in the heat pump system of FIG. Explanatory drawing of the defrost operation state in the heat pump system of FIG.
  • Configuration diagram of conventional heat pump circuit Configuration diagram of another conventional heat pump system Configuration of yet another conventional heat pump system 14A is a schematic diagram of the evaporator of the heat pump system of FIG. 13, and FIG. 14B is a cross-sectional view taken along line XVI-XVI of FIG. 14A.
  • FIG. 1 shows a schematic configuration of a heat pump system 100 according to the first embodiment of the present invention
  • FIGS. 2 and 3 show a boiling operation state and a defrosting operation state of the heat pump system 100, respectively.
  • a heat pump system 100 includes a heat pump circuit 110 that circulates a refrigerant, a tank 151 that stores a heat storage fluid, a heating path 150 for boiling the heat storage fluid by the heat pump circuit 110, and control of the entire system. And a control device 180 for performing the above. Furthermore, the heat pump system 100 according to the present embodiment is configured to use the heat of the heat storage fluid stored in the tank 151, the heat use path 154 having both ends connected to the tank 151, and the heat medium circuit 157 that circulates the heat medium. And an intermediate heat exchanger 155 provided across these 154 and 157.
  • the heat pump circuit 100 includes a compressor 111 that compresses a refrigerant, a radiator 112 that performs heat exchange between the compressed refrigerant and a heat storage fluid, and an expansion valve that serves as an expansion unit that expands the refrigerant flowing out of the radiator 112. 113, an evaporator 114 that evaporates the refrigerant expanded by the air sent from the fan 115, and a refrigerant pipe that sequentially connects these devices 111 to 114.
  • the evaporator 114 is provided with a refrigerant temperature sensor 125 (corresponding to the evaporation temperature sensor of the present invention) 125 that detects the temperature of the refrigerant flowing through the evaporator 114.
  • the tank 151 has a shape extending in the vertical direction (for example, a cylindrical shape).
  • water is used as the heat storage fluid
  • a water supply pipe 152 is connected to the lower part of the tank 151
  • a hot water supply pipe 153 is connected to the upper part of the tank 151.
  • the upper part of the tank 151 means a portion of about 1/3 to 1/5 of the upper side of the tank 151 in the vertical direction
  • the lower part of the tank 151 means the lower third of the tank 151 in the vertical direction.
  • a portion of about 1 to 5 is referred to, and an intermediate portion of a tank 151 described later refers to a portion between them.
  • the boiling path 150 includes a forward side path 160 that sends water (heat storage fluid) in the tank 151 to the radiator 112 and a return side path 161 that returns water from the radiator 112 to the tank 151.
  • One end of the forward side passage 160 is connected to a lower outlet provided in the lower portion of the tank 151, and the other end is connected to the radiator 112.
  • One end of the return side passage 161 is connected to the heat radiator 112, and the other end is connected to an upper return port provided in the upper part of the tank 151.
  • a boiling pump 162 which is a first heat storage fluid pump is provided on the outgoing side passage 160.
  • the boiling pump 162 can be provided in the return side passage 161.
  • the water inside the boiling path 160 (more precisely, the upstream side of the boiling pump 162 of the boiling path 160) is upstream of the boiling pump 162 in the outgoing path 160.
  • a discharge path 163 having a freeze prevention valve 163a for discharging is provided.
  • One end of the heat utilization path 154 is connected to the upper part of the tank 151, and the other end is connected to the middle part of the tank 151. Further, the heat utilization path 154 is provided with a pump 156 for flowing water from one end to the other end.
  • the heat medium circuit path 157 is provided with a pump 159 for circulating the heat medium along the heat medium circuit 157, and a heat utilization heat exchanger 158 for releasing the heat of the heat storage fluid through the heat medium.
  • a pump 159 for circulating the heat medium along the heat medium circuit 157
  • a heat utilization heat exchanger 158 for releasing the heat of the heat storage fluid through the heat medium.
  • water can be used as the heat medium
  • an example of the heat-use heat exchanger 158 is a heating device.
  • the heat medium circuit 157 may be omitted, and the heat-use heat exchanger 158 may be used instead of the intermediate heat exchanger 155.
  • the heat pump system 100 includes a defrosting path 120 that connects a portion between the expansion valve 113 and the evaporator 114 and a portion between the evaporator 114 and the compressor 111 in the heat pump circuit 110, and boiling.
  • the “medium temperature” means a temperature that is higher than the outside air temperature but is insufficient for using the heat storage fluid at that temperature as it is.
  • the temperature is about 30 to 40 ° C.
  • the refrigerant heater 118 heats the refrigerant by exchanging heat between the refrigerant flowing through the defrosting path 120 and the water flowing through the circulation path 164.
  • a counter-flow heat exchanger in which refrigerant and water flow oppositely is used as the refrigerant heater 118.
  • the defrosting path 120 includes an expansion valve side flow path that connects the refrigerant pipe between the expansion valve 113 and the evaporator 114 and the refrigerant heater 118, a primary flow path of the refrigerant heater 118, the evaporator 114, and the compression It is comprised by the refrigerant
  • the defrost circuit is comprised by the part containing the evaporator 114 between the defrost path 120 and the both ends of the defrost path 120 in the heat pump circuit 110.
  • a refrigerant pump 117 is provided in the defrosting path 120.
  • the refrigerant pump 117 is provided so that the refrigerant flows through the defrosting passage 120 in a direction passing through the evaporator 114 from the compressor 111 side to the expansion valve 113 side.
  • the refrigerant pump 117 is arranged on the upstream side of the refrigerant heater 118 (that is, in the expansion valve side flow path).
  • a gas-liquid separator 116 is provided in the defrosting path 120 on the upstream side of the refrigerant pump 117.
  • the refrigerant pump 117 is connected to the liquid outlet of the gas-liquid separator 116 by piping, and the liquid-phase refrigerant separated by the gas-liquid separator 116 is guided to the refrigerant pump 117.
  • the flow from the refrigerant heater 118 side is allowed downstream of the refrigerant heater 118 (that is, to the compressor side flow path), but the flow from the heat pump circuit 110 side is prohibited.
  • a check valve 119 is provided.
  • the circulation path 164 includes an upper flow path 165 that connects a middle outlet provided in an intermediate portion of the tank 151 and the refrigerant heater 118, a secondary flow path of the refrigerant heater 118, the refrigerant heater 118, and the tank 151.
  • the lower flow path 166 is connected to a lower return port provided at the lower part of the lower flow path.
  • the upper flow path 165 is provided with a circulation pump 167 that is a second heat storage fluid pump.
  • the circulation pump 167 may be provided in the lower flow path 166.
  • the discharge path 168 having the antifreezing valve 168a for discharging the water inside the circulation path 164 (more precisely, the downstream portion of the circulation path 164 from the circulation pump 167) to the lower flow path 166. is provided.
  • the circulation path 164 is provided with a freezing temperature sensor 121 that detects the temperature of water in the circulation path 164.
  • the freezing temperature sensor 121 is disposed in the secondary flow path of the refrigerant heater 121, but the freezing temperature sensor 121 may be disposed in the upper flow path 165 or the lower flow path 166. May be.
  • the above-described anti-freezing valves 163a and 168a are not particularly limited, but are preferably opened when the operation of the heat pump system 100 is stopped for a long time. If the heat pump circuit 110 is not operated for a long time in an area where the outside air temperature is below freezing point, water in the tank 151, the heating path 150 and the circulation path 164 may be frozen. This is because drainage can prevent piping damage due to freezing.
  • solenoid valves are used as the freeze prevention valves 163a and 168a, and a temperature sensor for detecting the temperature of water stored in the lower portion of the tank 151 is provided, and the temperature detected by the temperature sensor is determined.
  • the freeze prevention valves 163a and 168a when it becomes below predetermined temperature close
  • the anti-freezing valves 163a and 168a are automatically opened when the temperature of water in contact with the anti-freezing valves 163a and 168a falls below the predetermined temperature by an automatic mechanism that does not require electric power such as bimetal. It may be configured.
  • the control device 180 is connected to the above-described compressor 111, various pumps, the refrigerant temperature sensor 125, and the freezing temperature sensor 121.
  • the control device 180 controls the compressor 111 and various pumps based on information detected by the sensors 125 and 121 and performs a boiling operation and a defrosting operation.
  • the compressor 111 In the boiling operation state, as shown in FIG. 2, the compressor 111 is driven, and the refrigerant circulates through the heat pump circuit 110.
  • the boiling pump 162 On the other hand, the boiling pump 162 is driven, and the water stored in the lower portion of the tank 151 flows through the boiling path 150.
  • the high-pressure and high-temperature refrigerant compressed by the compressor 111 exchanges heat with water supplied from the outgoing side passage 160 by the radiator 112, and is cooled to near the temperature of the supplied water.
  • the refrigerant cooled by the radiator 112 is expanded and decompressed by the expansion valve 113 to be in a low-temperature and low-pressure gas-liquid two-phase state, and thereafter, heat exchange with the air blown by the evaporator fan 115 is performed by the evaporator 114. It absorbs heat and evaporates.
  • the evaporated refrigerant is again sucked into the compressor 111 and compressed to be pressurized.
  • the water in the boiling path 150 is boiled to near the temperature of the high-temperature refrigerant discharged from the compressor 111 by the radiator 112 and returned to the upper portion of the tank 151 again.
  • the high-temperature water in the tank 151 boiled in this way is supplied from the hot water supply pipe 153 to a necessary place, and water is supplied from the water supply pipe 152 to the tank 151 by the amount used for hot water supply.
  • the high-temperature water in the tank 151 is supplied to the heat utilization path 154 by driving the pump 156, and exchanges heat with the heat medium in the heat medium circuit 157 in the intermediate heat exchanger 155, so that the heat medium in the heat medium circuit 157
  • the intermediate temperature water that has radiated heat is returned to the intermediate portion of the tank 151.
  • the heat medium heated by the intermediate heat exchanger 155 by driving the pump 159 is sent to the heat utilization heat exchanger 158, and the heat of the fluid is reheated in the bath water, indoor heating, snow melting
  • the cooled heat medium is again sent to the intermediate heat exchanger 155 by the pump 159.
  • the control device 180 first detects the temperature Te of the refrigerant flowing through the evaporator 114 with the refrigerant temperature sensor 125 (step S1), and continues the boiling operation until the refrigerant temperature Te becomes equal to or lower than the first set temperature T1 (step S1). NO in S2.
  • the first set temperature T1 may be determined in advance according to, for example, the outside air temperature, or may be calculated every time the engine is started as a value obtained by subtracting a predetermined temperature from the refrigerant temperature Te detected at the time of starting.
  • the control device 180 stops the compressor 111, stops the boiling pump 162, and stops circulation through the heating path 150. Then, the heating operation by the heat pump circuit 110 is stopped (step S3). Next, the control device 180 drives the refrigerant pump 117 to send the liquid-phase refrigerant in the gas-liquid separator 116 to the refrigerant heater 118 and simultaneously drives the circulation pump 167 to start circulation through the circulation path 164. Then, the medium-temperature water accumulated in the tank 151 is sent to the refrigerant heater 118 which is a counter flow type heat exchanger (step S4).
  • the liquid-phase refrigerant is heated to near the temperature of the medium-temperature water to evaporate, and the heated steam is sent to the evaporator 114, whereby the evaporator 114 is defrosted.
  • the refrigerant radiated and condensed by the evaporator 114 returns to the gas-liquid separator 116 again.
  • the water cooled by the refrigerant heater 118 is returned to the tank 151 from the lower return port provided at the lower part of the tank 151 through the return side passage 166.
  • the control device 180 continues the defrosting operation until the temperature Te of the refrigerant flowing through the evaporator 114 detected by the refrigerant temperature sensor 125 becomes equal to or higher than the second set temperature T2 (NO in step S5 and step S6).
  • the defrosting operation is shifted to the boiling operation.
  • the control device 180 stops the refrigerant pump 117 and stops the circulation pump 167 to stop the circulation through the circulation path 164 (step S7).
  • the control device 180 drives the compressor 111 again to operate the heat pump circuit 110, and also drives the boiling pump 162 to start circulation through the boiling path 150 (step S8).
  • the second set temperature T2 may be the same temperature as the first set temperature T1, or may be a temperature higher than the first set temperature T1.
  • the refrigerant pump 117 and the check valve 119 that are stopped do not supply the refrigerant heater 118 with the low-pressure and low-temperature refrigerant before and after passing through the evaporator 114. Still, when the temperature of the water in the circulation path 164 detected by the freezing temperature sensor 121 becomes equal to or lower than a predetermined temperature close to the freezing temperature, the anti-freezing operation in which the circulation pump 167 is driven to flow the medium temperature water to the circulation path 164 is performed. Do.
  • the defrosting operation is performed based on the temperature Te of the refrigerant flowing through the evaporator 114 detected by the refrigerant temperature sensor 125.
  • the defrosting temperature sensor of the present invention is not limited to this, and an evaporator temperature sensor that detects the temperature of the evaporator 114 may be used instead of the refrigerant temperature sensor 125.
  • liquid refrigerant is sent out by the refrigerant pump 117 to cause circulation of the refrigerant that performs defrosting. Therefore, compared with the conventional case where the overheated gas refrigerant is compressed and circulated by the compressor, the circulation of the refrigerant Can significantly reduce the power required. Further, the path through which the refrigerant circulates for defrosting is only the defrosting path 120 and the evaporator 114 in the heat pump circuit 110 and the vicinity thereof, compared to the case where the refrigerant circulates through the entire conventional heat pump circuit.
  • the circulation power can be reduced by reducing the pressure loss, and the defrosting ability can be improved by reducing the heat dissipation loss, so that an efficient defrosting operation can be performed.
  • the heating medium used for defrosting of the evaporator 114 is a refrigerant and uses the refrigerant flow path of the evaporator 114 that is used when the heat pump circuit 110 is operated, a dedicated medium temperature water is passed through the conventional evaporator. Compared with the case where a heating unit that is a flow path is provided, an increase in air-side pressure loss of the evaporator 114 and a decrease in fin area do not occur, so that the performance of the evaporator 114 can be maintained.
  • the refrigerant pump 117 in the defrosting path 120 is stopped when the heat pump circuit 110 is operated, so that a part of the heat used for boiling water in the radiator 112 is obtained from the medium temperature water in the tank 151. Don't be. Therefore, a heat pump system that prevents the amount of water heated in the tank 151 by the heat pump circuit 110 from being lower than it appears in the past, the input to the compressor 111 is the denominator, and the amount of water heated in the tank 151 is a numerator. A decrease in heating efficiency of 100 can be prevented.
  • the refrigerant pump 117 of the defrosting path 120 is provided so that the refrigerant flows through the defrosting path 120 in a direction passing through the evaporator 114 from the compressor 111 side to the expansion valve 113 side.
  • the gas refrigerant flows in from the compressor 111 side of the evaporator 114 (gas refrigerant outlet during the boiling operation) and is condensed by dissipating heat to the frost formed on the surface of the evaporator 114 to melt the frost.
  • the liquid refrigerant flows out from the expansion valve 113 side of the evaporator 114 (liquid refrigerant inlet during the boiling operation).
  • the gas refrigerant side and the liquid refrigerant side can be matched in the boiling operation and the defrosting operation, and the evaporator 114 is made to correspond to the state of the refrigerant passing through the evaporator 114 (the ratio of gas to liquid). It can be configured to have a cross-sectional area. As a result, the pressure loss accompanying the circulation of the refrigerant can be further reduced.
  • a gas-liquid separator 116 is provided on the upstream side of the refrigerant pump 117 in the defrosting path 120, and the liquid-phase refrigerant is guided to the refrigerant pump 117, so that the refrigerant pump 117 can perform stable liquid feeding, and the refrigerant pump The power of 117 can be reduced.
  • the refrigerant heater 118 is a counter-flow heat exchanger in which the refrigerant and the medium temperature water face each other, so that the temperature of the medium temperature water can be lowered to the temperature of the liquid refrigerant flowing into the refrigerant heater 118.
  • the liquid refrigerant can be heated to the temperature of the medium-temperature water flowing into the refrigerant heater 118 and evaporated to generate heated steam.
  • the heat of medium temperature water can be utilized efficiently for defrosting, and the temperature of the water returned to the tank 151 can be lowered.
  • the forward side path 160 of the heating path 150 is connected to the lower outlet provided in the lower part of the tank 151, and the return side path 161 is connected to the upper return opening provided in the upper part of the tank 151,
  • the low-temperature water stored in the lower part of 151 can be guided to the radiator 112, and the hot water heated to a high temperature can be returned to the upper part of the tank 151. Can be held in.
  • the upper flow path 165 of the circulation path 164 is connected to the middle outlet provided in the intermediate portion of the tank 151, and the lower flow path 166 is connected to the lower return port provided in the lower portion of the tank 151, so that the tank 151
  • the intermediate temperature water accumulated in the intermediate portion can be guided to the refrigerant heater 118, and the low temperature water radiated by the refrigerant heater 118 can be returned to the lower portion of the tank 151.
  • the heat pump circuit 110 that does not perform the defrosting operation is provided.
  • the low-pressure, low-temperature refrigerant that has flowed out of the evaporator 114 does not flow into the refrigerant heater 118. For this reason, the temperature of the refrigerant heater 118 does not decrease and water can be prevented from freezing.
  • the freezing temperature sensor 121 for detecting the temperature of the water in the circulation path 164 is provided and the antifreezing operation in which the intermediate temperature water flows before freezing is performed, it is possible to prevent damage to the piping due to water freezing. Further, when the heat pump system 100 is stopped for a long time, the water in the boiling path 150, the circulation path 164 and the tank 151 is discharged by the freeze prevention valves 163a and 168a. It is possible to prevent the temperature of water from being lowered and frozen when there is no energization.
  • the temperature of the water can be lowered even after the power is turned off. It can be detected and drained appropriately.
  • FIG. 5 shows a schematic configuration of a heat pump system 200 according to the second embodiment of the present invention
  • FIGS. 6 and 7 show a boiling operation state and a defrosting operation state of the heat pump system 200, respectively.
  • the heat pump system 200 of the present embodiment has a configuration substantially similar to the heat pump system 100 (see FIG. 1) described in the first embodiment.
  • the same functional parts are denoted by the same reference numerals, and the description thereof is omitted.
  • the difference between the present embodiment and the first embodiment is the configuration of the tank 151, the boiling path 150 and the circulation path 164, and the heat storage fluid stored in the tank 151.
  • the tank 151 includes an inner tank 351 above the inside of the tank 151, a water supply pipe 152 is connected to the lower part of the inner tank 351, and a hot water supply pipe 153 is connected to the upper part of the inner tank 351. Further, in the tank 151, an antifreeze liquid is stored as a heat storage fluid except for the inner tank 351, and the antifreeze liquid is supplied to the boiling path 150 and the circulation path 164. Then, the water in the inner tank 351 is heated by the high-temperature antifreeze liquid returned from the return side path 161 of the boiling path 150 to the upper portion of the tank 151 and discharged from the hot water supply pipe 153.
  • the upper flow path 165 of the circulation path 164 includes a merging section 360 that merges with the forward side path 160 and a branch section 362 that branches from the forward side path 160.
  • a heat storage fluid pump 361 is provided between the junction 360 and the branch 362. That is, the heat storage fluid pump 361 is shared by the boiling path 150 and the circulation path 164.
  • the first on-off valves 363 and 364 are provided in the upstream side portion of the joining portion 360 and the downstream side portion of the branching portion 362 in the outgoing side passage 160 of the boiling passage 150, respectively.
  • Second on-off valves 365 and 366 are provided in a portion upstream of the junction 360 in the upper flow path 165 of the passage 164 and a portion downstream of the branch 362, respectively.
  • the first on-off valves 363 and 364 and the second on-off valves 365 and 366 are controlled by the control device 180 so that the other is closed when one is opened and the other is closed when the other is opened. .
  • the first on-off valves 363 and 364 and the second on-off valves 365 and 366 allow the circulation through the boiling path 150 and prohibit the circulation through the circulation path 164, and the first on-off valves 365 and 366 through the boiling path 150.
  • the switching means of the present invention is configured to switch between the second state in which the circulation is prohibited and the circulation through the circulation path 164 is permitted. Note that the switching means of the present invention does not need to be configured by four on-off valves, and may be configured by, for example, a pair of three-way valves respectively provided at the junction 360 and the branch 362.
  • the functions of the boiling pump 162 and the circulation pump 167 that are necessary in the configuration of the first embodiment are changed to the opening / closing operations of the first on-off valves 363, 364 and the second on-off valves 365, 366.
  • one heat storage fluid pump 361 can be used, and an efficient heat pump system 200 can be configured at low cost.
  • the heat storage fluid is an antifreeze liquid, there is no risk of freezing of the heat storage fluid in the boiling path 150 and the circulation path 164, so that the antifreeze operation or the use of an antifreeze heater can be performed efficiently.
  • the heat pump system 200 can be operated.
  • the inner tank 351 is disposed in the tank 151, the water stored in the inner tank 351 and the antifreezing liquid stored in the tank 151 can be separated. For this reason, even when the heat storage fluid boiled up by the heat pump circuit 110 is made an antifreeze liquid, the water supplied from the water supply pipe 152 can be heated and supplied from the hot water supply pipe to a necessary place.
  • the upper flow path 165 of the circulation path 164 has the merge section 360 and the branch section 362, but the lower flow path 166 of the circulation path 164 has the merge section 360 and the branch section 362.
  • a heat storage fluid pump may be provided between them.
  • the tank 151 is provided with only one intermediate outlet, but a plurality of intermediate outlets may be provided in the vertical direction. That is, the upstream end of the circulation path 164 is branched into a plurality of branches, and a place for taking out the medium-temperature water is selected according to a place where the medium-temperature water is detected by a plurality of temperature sensors provided in the tank. It may be.
  • the medium temperature water flows through the circulation path 164.
  • the water flowing through the circulation path 164 is water at any temperature as long as it is water in the tank 151. Defrosting can be performed using the water boiled up efficiently. This is because some of the water in the lower part of the tank 151 is given heat from the high temperature water or medium temperature water. That is, the upstream end of the circulation path 164 may be connected to the upper part of the tank 151 or may be connected to the lower part of the tank 151.
  • the positions of the refrigerant pump 117 and the check valve 119 in the defrosting path 120 may be switched. Further, without providing the check valve 119, the inflow portion to the refrigerant heater 118 and the outflow portion from the refrigerant heater 118 in the circulation path 164 are formed so as to lift the refrigerant heater 118 upward in the direction of gravity. May be.
  • the gas refrigerant evaporated by the defrosting operation and the gas refrigerant heated by the medium temperature water by the antifreezing operation are maintained in the refrigerant heater 118 and flowed out of the evaporator 114 during the boiling operation. Low temperature and low pressure liquid refrigerant is prevented from flowing into the refrigerant heater 118. Therefore, even in this configuration, water freezing in the refrigerant heater 118 can be prevented.
  • the present invention is useful for heat pump systems used in heat pump water heaters, heat pump heaters, and the like.

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

Abstract

L'invention porte sur un système de pompe à chaleur (100) qui est composé d'un circuit de pompe à chaleur (110) ; d'un réservoir (151) pour stocker un fluide d'accumulation de chaleur ; d'un trajet d'ébullition (150) pour porter à ébullition le fluide d'accumulation de chaleur ; d'un trajet de dégivrage (120) qui relie une partie entre un moyen de détente (113) et un évaporateur (114) à une partie entre l'évaporateur (114) et un compresseur (111), dans le circuit de pompe à chaleur (110), et qui est pourvu d'une pompe de fluide frigorigène (117) ; d'un trajet de circulation (164) pour faire circuler le fluide d'accumulation de chaleur à l'intérieur du réservoir (151), et d'un dispositif de chauffage de fluide frigorigène (118) qui échange de la chaleur entre un fluide frigorigène traversant le trajet de dégivrage (120) et le fluide d'accumulation de chaleur traversant le trajet de circulation (164), de façon à chauffer le fluide frigorigène.
PCT/JP2010/003611 2009-06-11 2010-05-28 Système de pompe à chaleur Ceased WO2010143373A1 (fr)

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JP2009139735A JP2012163219A (ja) 2009-06-11 2009-06-11 ヒートポンプシステム
JP2009-139735 2009-06-11

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WO2010143373A1 true WO2010143373A1 (fr) 2010-12-16

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013172166A1 (fr) * 2012-05-18 2013-11-21 三菱電機株式会社 Dispositif de pompe à chaleur
CN104654686A (zh) * 2015-02-03 2015-05-27 珠海格力电器股份有限公司 空调系统
CN106595118A (zh) * 2016-12-27 2017-04-26 珠海格力电器股份有限公司 风冷冷热水机组
EP3623724A1 (fr) * 2018-09-13 2020-03-18 Rob Hazes Pompe à chaleur avec pré-chauffage / pré-refroidissement de la source de chaleur / froid
CN111102761A (zh) * 2019-12-13 2020-05-05 北京空间飞行器总体设计部 一种基于热泵的泵驱两相流体回路控温系统
EP3696478A1 (fr) * 2019-02-15 2020-08-19 Panasonic Intellectual Property Management Co., Ltd. Système de pompe à chaleur
CN111998581A (zh) * 2020-09-10 2020-11-27 清华大学 自除霜式空气源热量采集装置及其运行方法
WO2023105210A1 (fr) * 2021-12-07 2023-06-15 Mixergy Limited Système de chauffage d'eau et dispositif de commande associé

Families Citing this family (1)

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CN106765742A (zh) * 2016-11-21 2017-05-31 珠海格力电器股份有限公司 具有满液式壳管换热器的空调机组

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JPH10332196A (ja) * 1997-05-30 1998-12-15 Kyocera Corp 給湯装置
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WO2013172166A1 (fr) * 2012-05-18 2013-11-21 三菱電機株式会社 Dispositif de pompe à chaleur
JPWO2013172166A1 (ja) * 2012-05-18 2016-01-12 三菱電機株式会社 ヒートポンプ装置
US10001318B2 (en) 2012-05-18 2018-06-19 Mitsubishi Electric Corporation Heat pump device that draws heat from both the atmosphere and another heat source
CN104654686A (zh) * 2015-02-03 2015-05-27 珠海格力电器股份有限公司 空调系统
CN106595118A (zh) * 2016-12-27 2017-04-26 珠海格力电器股份有限公司 风冷冷热水机组
EP3623724A1 (fr) * 2018-09-13 2020-03-18 Rob Hazes Pompe à chaleur avec pré-chauffage / pré-refroidissement de la source de chaleur / froid
EP3696478A1 (fr) * 2019-02-15 2020-08-19 Panasonic Intellectual Property Management Co., Ltd. Système de pompe à chaleur
CN111102761A (zh) * 2019-12-13 2020-05-05 北京空间飞行器总体设计部 一种基于热泵的泵驱两相流体回路控温系统
CN111102761B (zh) * 2019-12-13 2021-07-13 北京空间飞行器总体设计部 一种基于热泵的泵驱两相流体回路控温系统
CN111998581A (zh) * 2020-09-10 2020-11-27 清华大学 自除霜式空气源热量采集装置及其运行方法
CN111998581B (zh) * 2020-09-10 2024-03-19 清华大学 自除霜式空气源热量采集装置及其运行方法
WO2023105210A1 (fr) * 2021-12-07 2023-06-15 Mixergy Limited Système de chauffage d'eau et dispositif de commande associé

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