WO2015136595A1 - ヒートポンプ装置 - Google Patents
ヒートポンプ装置 Download PDFInfo
- Publication number
- WO2015136595A1 WO2015136595A1 PCT/JP2014/056149 JP2014056149W WO2015136595A1 WO 2015136595 A1 WO2015136595 A1 WO 2015136595A1 JP 2014056149 W JP2014056149 W JP 2014056149W WO 2015136595 A1 WO2015136595 A1 WO 2015136595A1
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- WIPO (PCT)
- Prior art keywords
- refrigerant
- heat
- temperature
- heat exchanger
- pressure
- Prior art date
Links
- 238000010438 heat treatment Methods 0.000 claims abstract description 116
- 238000007906 compression Methods 0.000 claims abstract description 89
- 230000006835 compression Effects 0.000 claims abstract description 88
- 239000012530 fluid Substances 0.000 claims abstract description 13
- 238000007599 discharging Methods 0.000 claims abstract description 5
- 239000003507 refrigerant Substances 0.000 claims description 274
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 259
- 239000002826 coolant Substances 0.000 claims description 16
- 238000001704 evaporation Methods 0.000 claims description 14
- 230000008020 evaporation Effects 0.000 claims description 13
- 239000007788 liquid Substances 0.000 description 18
- 238000010586 diagram Methods 0.000 description 13
- 238000009833 condensation Methods 0.000 description 12
- 230000005494 condensation Effects 0.000 description 12
- 239000010721 machine oil Substances 0.000 description 10
- 238000000034 method Methods 0.000 description 9
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 8
- 238000012546 transfer Methods 0.000 description 5
- 229910002092 carbon dioxide Inorganic materials 0.000 description 4
- 239000001569 carbon dioxide Substances 0.000 description 4
- 101150091111 ACAN gene Proteins 0.000 description 3
- 238000001514 detection method Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000012545 processing Methods 0.000 description 3
- 229920006395 saturated elastomer Polymers 0.000 description 3
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical compound CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 238000009423 ventilation Methods 0.000 description 2
- CDOOAUSHHFGWSA-OWOJBTEDSA-N (e)-1,3,3,3-tetrafluoroprop-1-ene Chemical compound F\C=C\C(F)(F)F CDOOAUSHHFGWSA-OWOJBTEDSA-N 0.000 description 1
- FXRLMCRCYDHQFW-UHFFFAOYSA-N 2,3,3,3-tetrafluoropropene Chemical compound FC(=C)C(F)(F)F FXRLMCRCYDHQFW-UHFFFAOYSA-N 0.000 description 1
- 206010037660 Pyrexia Diseases 0.000 description 1
- 230000002528 anti-freeze Effects 0.000 description 1
- 239000012267 brine Substances 0.000 description 1
- 230000014509 gene expression Effects 0.000 description 1
- 239000003673 groundwater Substances 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000005338 heat storage Methods 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 230000000704 physical effect Effects 0.000 description 1
- 239000001294 propane Substances 0.000 description 1
- QQONPFPTGQHPMA-UHFFFAOYSA-N propylene Natural products CC=C QQONPFPTGQHPMA-UHFFFAOYSA-N 0.000 description 1
- 125000004805 propylene group Chemical group [H]C([H])([H])C([H])([*:1])C([H])([H])[*:2] 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- HPALAKNZSZLMCH-UHFFFAOYSA-M sodium;chloride;hydrate Chemical compound O.[Na+].[Cl-] HPALAKNZSZLMCH-UHFFFAOYSA-M 0.000 description 1
- 238000013517 stratification Methods 0.000 description 1
- 239000013526 supercooled liquid Substances 0.000 description 1
Images
Classifications
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- 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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
-
- 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
- F24D17/00—Domestic hot-water supply systems
- F24D17/02—Domestic hot-water supply systems using heat pumps
-
- 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
- F24D19/1051—Arrangement or mounting of control or safety devices for water heating systems for domestic hot water
- F24D19/1054—Arrangement or mounting of control or safety devices for water heating systems for domestic hot water the system uses a heat pump
-
- 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
- F24H15/00—Control of fluid heaters
- F24H15/20—Control of fluid heaters characterised by control inputs
- F24H15/212—Temperature of the water
- F24H15/219—Temperature of the water after heating
-
- 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
- F24H15/00—Control of fluid heaters
- F24H15/20—Control of fluid heaters characterised by control inputs
- F24H15/227—Temperature of the refrigerant in heat pump cycles
-
- 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
- F24H15/00—Control of fluid heaters
- F24H15/20—Control of fluid heaters characterised by control inputs
- F24H15/242—Pressure
-
- 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
- F24H15/00—Control of fluid heaters
- F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
- F24H15/335—Control of pumps, e.g. on-off control
-
- 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
- F24H15/00—Control of fluid heaters
- F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
- F24H15/375—Control of heat pumps
- F24H15/38—Control of compressors of heat pumps
-
- 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
- F24H15/00—Control of fluid heaters
- F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
- F24H15/375—Control of heat pumps
- F24H15/385—Control of expansion valves of heat pumps
-
- 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
- F24H15/00—Control of fluid heaters
- F24H15/40—Control of fluid heaters characterised by the type of controllers
- F24H15/414—Control of fluid heaters characterised by the type of controllers using electronic processing, e.g. computer-based
- F24H15/421—Control of fluid heaters characterised by the type of controllers using electronic processing, e.g. computer-based using pre-stored data
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/006—Cooling of compressor or motor
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- 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
- F25B40/00—Subcoolers, desuperheaters or superheaters
-
- 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
- F24D2200/00—Heat sources or energy sources
- F24D2200/12—Heat pump
- F24D2200/123—Compression type heat pumps
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- 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
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- 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
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- 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
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
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- 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
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
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- 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
- F25B2700/2116—Temperatures of a condenser
- F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser
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- 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
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
Definitions
- the present invention relates to a heat pump device that heats a target fluid.
- Patent Document 1 discloses the following hot water supply cycle apparatus.
- the hot water supply cycle apparatus includes a compressor, a gas cooler, an expansion valve, an evaporator, and the like.
- the compressor has a compression element and an electric element in a sealed container.
- the compressor includes a suction pipe that directly guides the low-pressure refrigerant to the compression element, a discharge pipe that discharges the high-pressure refrigerant compressed by the compression element to the outside of the sealed container without releasing it into the sealed container, and heat discharged from the discharge pipe.
- Refrigerant reintroduction pipe for reintroducing the refrigerant after replacement into the sealed container
- refrigerant redischarge pipe for discharging the refrigerant after being introduced into the sealed container from the refrigerant reintroduction pipe and passing through the electric element to the outside of the sealed container With.
- the temperature of water in the water pipe is increased by the refrigerant in the refrigerant pipe by exchanging heat between the water pipe through which hot water is circulated and the refrigerant pipe through which the compressed refrigerant is circulated.
- the high-temperature side refrigerant pipe connected to the discharge pipe exchanges heat with the outlet side of the water pipe of the gas cooler
- the low-temperature side refrigerant pipe connected to the refrigerant re-discharge pipe exchanges heat with the inlet side of the water pipe of the gas cooler.
- the following Patent Document 2 discloses the following heat pump water heater.
- the heat pump water heater has a heat pump cycle in which a compressor, a water refrigerant heat exchanger, an expansion valve, and an evaporator are connected in an annular shape.
- the heat pump water heater has a hot water storage operation mode and a hot water operation mode. In the hot water filling operation mode, the heat pump cycle is operated, the water supplied from the hot water storage tank and the water flowing out of the water refrigerant heat exchanger of the heat pump cycle are mixed by the hot water mixing valve, and the mixed water is mixed. Supply to the bathtub and make the hot water temperature lower than the hot water storage operation mode.
- the refrigerant mixed with the refrigerating machine oil evaporates, so that the refrigerating machine oil is foamed and the refrigerating machine oil is combined with the refrigerant. It flows out from the discharge pipe. As a result, the refrigerating machine oil in the sealed container may be insufficient.
- the present invention has been made to solve the above-described problems, and an object of the present invention is to provide a heat pump device capable of suppressing liquid refrigerant from accumulating inside a sealed container during low heating operation.
- the heat pump device of the present invention includes a sealed container, a compression element provided inside the sealed container, and a first low-pressure refrigerant sucked from the outside of the sealed container that is led to the compression element without being discharged into the internal space of the sealed container.
- a compressor having a second suction passage that discharges the refrigerant to the inner space of the sealed container without compression, and a second discharge passage that discharges the high-pressure refrigerant in the inner space of the sealed container to the outside of the sealed container without being compressed.
- the high-pressure refrigerant that has passed through the second heat exchanger The total amount of heating of the expansion part to be a low-pressure refrigerant, the evaporator that evaporates the low-pressure refrigerant that has passed through the expansion part, the high heating operation, and the first heat exchanger and the second heat exchanger is the high heating operation.
- a control means for performing a low heating operation that is smaller than the control means, and the control means controls the refrigerant state in the second suction passage to be in an overheated gas state during the low heating operation.
- the heat pump device of the present invention it is possible to suppress liquid refrigerant from accumulating inside the sealed container during low heating operation.
- FIG. 1 is a configuration diagram illustrating a heat pump apparatus according to Embodiment 1 of the present invention.
- the heat pump device 1 according to the first embodiment includes a heat pump unit 2 that heats water, a hot water storage tank 10, and a control device 50.
- the hot water storage tank 10 stores water by forming a temperature stratification in which the upper side is hot and the lower side is low.
- the lower part of the hot water storage tank 10 and the inlet 12 of the heat pump unit 2 are connected via an inlet pipe 11.
- a pump 13 is installed in the middle of the inlet pipe 11.
- One end of the upper pipe 14 is connected to the upper part of the hot water storage tank 10.
- the other end of the upper pipe 14 branches into two and is connected to the first inlet of the hot water mixing valve 15 and the first inlet of the bath mixing valve 16, respectively.
- the outlet 17 of the heat pump unit 2 is connected to a position in the middle of the upper pipe 14 via the outlet pipe 18. Details of the heat pump unit 2 will be described later.
- the target fluid to be heated is water
- the target fluid in the present invention may be a fluid other than water, such as brine or antifreeze.
- a water supply pipe 19 for supplying water from a water source such as a water supply is connected to the lower part of the hot water storage tank 10.
- a pressure reducing valve 20 for reducing the water source pressure to a predetermined pressure is installed in the middle of the water supply pipe 19.
- a water supply pipe 21 branches from a water supply pipe 19 between the hot water storage tank 10 and the pressure reducing valve 20.
- the downstream side of the water supply pipe 21 branches in two and is connected to the second inlet of the hot water mixing valve 15 and the second inlet of the bath mixing valve 16, respectively.
- the outlet of the hot water supply mixing valve 15 is connected to a hot water tap 23 via a hot water supply pipe 22.
- a hot water supply flow rate detection means 24 and a hot water supply temperature sensor 25 are installed in the hot water supply pipe 22.
- the outlet of the bath mixing valve 16 is connected to a bathtub 27 via a bath pipe 26.
- An open / close valve 28 and a bath temperature sensor 29 are installed in the bath pipe 26.
- a heat pump outlet temperature sensor 30 that detects a heat pump outlet temperature, which is a temperature of water exiting the heat pump unit 2, is installed in the outlet pipe 18 in the vicinity of the outlet 17 of the heat pump unit 2.
- the heat pump outlet temperature sensor 30 may be provided in a pipe (water channel 48 described later) inside the heat pump unit 2. In the following description, the temperature of water entering the heat pump unit 2 is referred to as “heat pump inlet temperature”.
- the control device 50 is a control means configured by, for example, a microcomputer.
- the control device 50 includes a ROM (Read Only Memory), a RAM (Random Access Memory), a storage unit including a nonvolatile memory, an arithmetic processing unit (CPU) that executes arithmetic processing based on a program stored in the storage unit, An input / output port for inputting / outputting external signals to / from the arithmetic processing unit, a timer for measuring time, and the like are provided.
- the control device 50 is electrically connected to various actuators and sensors included in the heat pump device 1.
- the control device 50 is connected to the operation unit 60 so as to communicate with each other.
- the user can set the hot water supply temperature, the amount of bath water, the bath temperature, etc., or can make a timer reservation for the bath hot water time by operating the operation unit 60.
- the control device 50 controls the operation of the heat pump device 1 by controlling the operation of each actuator according to the program stored in the storage unit based on the information detected by each sensor, the instruction information from the operation unit 60, and the like. .
- the hot water storage operation is an operation for increasing the amount of hot water stored and the amount of heat stored in the hot water storage tank 10.
- the control device 50 operates the heat pump unit 2 and the pump 13.
- the low temperature water led out from the lower part of the hot water storage tank 10 by the pump 13 is sent to the heat pump unit 2 through the inlet pipe 11 and heated by the heat pump unit 2 to become high temperature water.
- This high-temperature water flows into the upper part of the hot water storage tank 10 through the outlet pipe 18 and the upper pipe 14.
- hot water is accumulated in the hot water storage tank 10 from above.
- the control device 50 controls the heat pump outlet temperature detected by the heat pump outlet temperature sensor 30 to be, for example, about 65 ° C. to 90 ° C.
- the heat pump outlet temperature is lowered by controlling the pump 13 so that the flow rate of the water flowing through the heat pump unit 2 is increased.
- the heat pump outlet temperature rises by controlling the pump 13 so that the flow rate of the water flowing through the heat pump unit 2 becomes low.
- the control device 50 controls the heat pump unit 2 so as to perform the high heating operation.
- the high heating operation of the heat pump unit 2 is an operation for setting the heating capacity of the heat pump unit 2 to a predetermined rated capacity.
- the hot water supply operation is an operation for supplying hot water to the hot water tap 23.
- the hot water supply pipe 19 flows into the lower part of the hot water storage tank 10 due to the water source pressure, so that the high-temperature water in the upper part of the hot water storage tank 10 flows out to the upper pipe 14.
- the hot water supply mixing valve 15 the low temperature water supplied from the water supply pipe 21 and the high temperature water supplied from the hot water storage tank 10 through the upper pipe 14 are mixed. This mixed water is discharged to the outside from the hot water tap 23 through the hot water supply pipe 22.
- the control device 50 sets the hot water supply temperature detected by the hot water supply temperature sensor 25 in the operation section 60 in advance by the user.
- the mixing ratio of the hot water supply mixing valve 15 is controlled so as to be a value.
- the hot water filling operation is an operation in which hot water is accumulated in the bathtub 27.
- the control device 50 operates the heat pump unit 2 and the pump 13 to open the on-off valve 28.
- water from the water supply pipe 19 flows into the lower part of the hot water storage tank 10 due to the water source pressure, the high-temperature water at the upper part of the hot water storage tank 10 flows out to the upper pipe 14.
- the low temperature water led out from the lower part of the hot water storage tank 10 by the pump 13 is sent to the heat pump unit 2 through the inlet pipe 11 and heated by the heat pump unit 2.
- the water heated by the heat pump unit 2 passes through the outlet pipe 18 and flows into the upper pipe 14.
- the high temperature water supplied from the hot water storage tank 10 and the water heated by the heat pump unit 2 merge through the upper pipe 14 and are supplied to the bath mixing valve 16.
- the bath mixing valve 16 low temperature water supplied from the water supply pipe 21 and hot water supplied through the upper pipe 14 are mixed.
- This mixed water passes through the bath pipe 26, passes through the on-off valve 28, and is discharged into the bathtub 27.
- the control device 50 controls the mixing ratio of the bath mixing valve 16 so that the hot water supply temperature detected by the bath temperature sensor 29 becomes the bathtub temperature set value set in advance by the user using the operation unit 60. .
- hot water is supplied to the bathtub 27 by using not only high-temperature water stored in the hot water storage tank 10 but also water heated by the heat pump unit 2.
- the control device 50 controls the heat pump outlet temperature detected by the heat pump outlet temperature sensor 30 to be lower than the bathtub temperature set value.
- the control device 50 controls the heat pump unit 2 to perform the low heating operation.
- the low heating operation of the heat pump unit 2 is an operation that lowers the heating capacity of the heat pump unit 2 compared to the high heating operation.
- the hot water filling capacity is heat energy per unit time required when a bathtub is filled at a target bath temperature under the conditions of a predetermined bath capacity, feed water temperature, and hot water flow rate.
- the bath capacity is 180 L
- the feed water temperature is 9 ° C.
- the target bath temperature is 45 ° C.
- the hot water flow rate is 10 L / min to 20 L / min
- the standard hot water filling capacity is 25 kW to 50 kW.
- the rated heating capacity of the heat pump unit 2 is, for example, about 4.5 kW to 9 kW. Only the heating capacity of the heat pump unit 2 cannot satisfy the standard hot water filling capacity. In order to satisfy the standard hot water filling capacity, it is necessary to use hot water stored in the hot water storage tank 10.
- the heat pump unit 2 has a characteristic that COP (Coefficient of Performance) becomes higher as the heating capacity is lowered. Moreover, the heat pump unit 2 has a characteristic that COP increases as the heat pump outlet temperature decreases. For this reason, the COP for the low heating operation is higher than the COP for the high heating operation.
- the COP of the low heating operation is C1
- the COP of the high heating operation is C2
- the hot water COP which is a substantial COP of the hot water operation is C3
- the heating capacity of the low heating operation of the heat pump unit 2 with respect to the hot water filling capacity When the ratio is Rhp, the hot water filling COP is expressed by the following equation.
- C3 C1 ⁇ Rhp + C2 ⁇ (1 ⁇ Rhp) (1)
- the hot water filling operation of the first embodiment the low water heating operation is performed and the water heated by the heat pump unit 2 is used as an auxiliary to make the hot water filling COP higher than the COP of the high heating operation. be able to.
- FIG. 2 is a configuration diagram showing the heat pump unit 2 provided in the heat pump device 1 according to the first embodiment of the present invention.
- the heat pump unit 2 includes a refrigerant circuit in which a compressor 3, a first heat exchanger 4, a second heat exchanger 5, an expansion valve 6, and an evaporator 7 are connected by a refrigerant pipe. Is provided.
- the first heat exchanger 4 and the second heat exchanger 5 are heat exchangers that heat water with the heat of the refrigerant.
- the evaporator 7 is composed of an air refrigerant heat exchanger that performs heat exchange between air and refrigerant.
- the heat pump unit 2 further includes a blower 8 that blows air to the evaporator 7 and a high-low pressure heat exchanger 9 that performs heat exchange between the high-pressure refrigerant and the low-pressure refrigerant.
- carbon dioxide is used as the refrigerant.
- the evaporator 7 in this invention is not restricted to what heat-exchanges air and a refrigerant
- the compressor 3 includes a sealed container 31, a compression element 32 and an electric element 33 provided inside the sealed container 31, a first suction passage 34, a first discharge passage 35, a second suction passage 36, And two discharge passages 37.
- a compression element 32 is disposed below the electric element 33. Inside the sealed container 31, an internal space 38 between the compression element 32 and the electric element 33 and an internal space 39 above the electric element 33 are provided.
- the first suction passage 34 does not discharge the low-pressure refrigerant sucked into the compressor 3 into the internal spaces 38 and 39 of the sealed container 31, and guides the low-pressure refrigerant directly to the compression element 32.
- the compression element 32 compresses the low-pressure refrigerant into a high-pressure refrigerant.
- the compression element 32 is driven by the electric element 33.
- the electric element 33 is an electric motor having a stator 33a and a rotor 33b.
- the compression element 32 discharges the compressed high-pressure refrigerant to the first discharge passage 35.
- the first discharge passage 35 does not discharge the high-pressure refrigerant to the internal spaces 38 and 39 of the sealed container 31, but directly discharges the high-pressure refrigerant to the outside of the sealed container 31.
- the high-pressure refrigerant discharged from the first discharge passage 35 passes through the refrigerant flow path 40 and flows into the first heat exchanger 4.
- the high-pressure refrigerant cooled with water in the first heat exchanger 4 passes through the refrigerant passage 41 and the second suction passage 36 and is re-inhaled into the compressor 3.
- the outlet of the second suction passage 36 is located in the internal space 38 between the electric element 33 and the compression element 32.
- the second suction passage 36 does not compress the high-pressure refrigerant re-inhaled by the compressor 3 and discharges the high-pressure refrigerant to the internal space 38 between the electric element 33 and the compression element 32.
- the inlet of the second discharge passage 37 is located in the internal space 39 above the electric element 33.
- the high-pressure refrigerant discharged from the outlet of the second suction passage 36 to the internal space 38 between the electric element 33 and the compression element 32 passes through a gap between the rotor 33b and the stator 33a of the electric element 33 and the like. It reaches the internal space 39 above the element 33.
- the electric element 33 having a high temperature is cooled by the high-pressure refrigerant, and the high-pressure refrigerant is heated by the heat of the electric element 33.
- the second discharge passage 37 does not compress the high-pressure refrigerant in the internal space 39 above the electric element 33 and discharges the high-pressure refrigerant to the outside of the sealed container 31.
- the high-pressure refrigerant discharged from the second discharge passage 37 flows into the second heat exchanger 5 through the refrigerant flow path 42.
- the high-pressure refrigerant cooled with water in the second heat exchanger 5 passes through the refrigerant flow path 43 and reaches the expansion valve 6.
- the expansion valve 6 is an expansion part that expands the high-pressure refrigerant to make it a low-pressure refrigerant.
- the low-pressure refrigerant expanded by the expansion valve 6 flows into the evaporator 7 through the refrigerant flow path 44. In the evaporator 7, the low-pressure refrigerant is heated and evaporated by exchanging heat with the outside air guided by the blower 8.
- the low-pressure refrigerant that has passed through the evaporator 7 reaches the first suction passage 34 of the compressor 3 through the refrigerant flow path 45 and is sucked into the compressor 3.
- the high-low pressure heat exchanger 9 exchanges heat between the high-pressure refrigerant in the refrigerant channel 43 and the low-pressure refrigerant in the refrigerant channel 45.
- the pressure of the refrigerant discharged from the compression element 32 is referred to as “compression element discharge pressure”, and the pressure of the refrigerant sucked into the compression element 32 is referred to as “compression element suction pressure”.
- the refrigerant temperature is referred to as “compression element discharge temperature”, and the refrigerant temperature drawn into the compression element 32 is referred to as “compression element suction temperature”.
- the pressure of the high-pressure refrigerant discharged from the first discharge passage 35 is equal to the compression element discharge pressure.
- the pressure of the high-pressure refrigerant discharged from the first discharge passage 35 decreases due to the pressure loss that reaches the second suction passage 36 via the first heat exchanger 4. For this reason, the pressure of the high-pressure refrigerant in the internal space 38 of the sealed container 31 is slightly lower than the pressure of the high-pressure refrigerant discharged from the first discharge passage 35, that is, the compression element discharge pressure.
- the heat pump unit 2 includes a water flow path 46 that guides water flowing from the inlet 12 to the second heat exchanger 5, a water flow path 47 that guides water that has passed through the second heat exchanger 5 to the first heat exchanger 4, A water flow path 48 that guides the water that has passed through the heat exchanger 4 to the outlet 17 is further provided.
- water flowing from the inlet 12 flows into the second heat exchanger 5 through the water flow path 46 and is heated by the heat of the refrigerant in the second heat exchanger 5.
- the water heated in the second heat exchanger 5 flows into the first heat exchanger 4 and is further heated by the heat of the refrigerant in the first heat exchanger 4.
- the water further heated in the first heat exchanger 4 reaches the outlet 17 through the water channel 48 and flows to the outlet pipe 18.
- the first discharge passage 35 or the refrigerant passage 40 is provided with a discharge temperature sensor 51 for detecting the compression element discharge temperature.
- a refrigerant temperature sensor 52 that detects the refrigerant temperature of the second suction passage 36 is provided in the second suction passage 36 or the refrigerant flow path 41.
- FIG. 3 is a pressure-enthalpy diagram of the high heating operation.
- a to H in FIG. 3 correspond to A to H in FIG.
- the refrigerant is compressed by the compression element 32 to a pressure exceeding the critical pressure (A ⁇ B).
- the high-pressure refrigerant in the supercritical state is cooled by the first heat exchanger 4 (B ⁇ C).
- the state of the high-pressure refrigerant sucked into the internal space 38 of the sealed container 31 from the second suction passage 36 is C in FIG.
- This high-pressure refrigerant is heated by the heat of the electric element 33 while reaching the internal space 39 (C ⁇ D).
- the state of the high-pressure refrigerant discharged from the second discharge passage 37 is D in FIG.
- This high-pressure refrigerant is cooled by the second heat exchanger 5 (D ⁇ E). Thereafter, the high-pressure refrigerant is further cooled by the high-low pressure heat exchanger 9 (E ⁇ F).
- the high-pressure refrigerant that has passed through the high-low pressure heat exchanger 9 is decompressed by the expansion valve 6 and becomes low-pressure refrigerant (F ⁇ G).
- This low-pressure refrigerant evaporates in the evaporator 7 (G ⁇ H).
- the low-pressure refrigerant evaporated in the evaporator 7 is heated in the high-low pressure heat exchanger 9 (H ⁇ A).
- the heat pump outlet temperature of 65 ° C. to 90 ° C. in such a high heating operation is sufficiently higher than the critical temperature of carbon dioxide as a refrigerant.
- the compression element discharge pressure and the pressure of the refrigerant inside the first heat exchanger 4, the sealed container 31, and the second heat exchanger 5 are pressures exceeding the critical pressure.
- FIG. 4 is a diagram illustrating an example of temperature changes of the refrigerant and water in the first heat exchanger 4 and the second heat exchanger 5 in the high heating operation.
- B to E in FIG. 4 correspond to B to E in FIGS.
- the horizontal axis of FIG. 4 represents the position in the 1st heat exchanger 4 and the 2nd heat exchanger 5 by ratio of flow path length. That is, the horizontal axis of FIG. 4 represents the ratio of the water flow path length from the water inlet of the second heat exchanger 5 when the total length of the water flow paths of the first heat exchanger 4 and the second heat exchanger 5 is 1.
- coolant flow path of the 1st heat exchanger 4 and the 2nd heat exchanger 5 is set to 1 is represented.
- the temperature of water entering the second heat exchanger 5, that is, the heat pump inlet temperature is about 9 ° C.
- the temperature of water exiting the first heat exchanger 4, ie, the heat pump outlet temperature is about 65 ° C.
- the temperature of the refrigerant entering the first heat exchanger 4, that is, the compression element discharge temperature is about 85 ° C.
- FIG. 5 is a flowchart showing the control operation of the control device 50 in the high heating operation.
- the control device 50 controls each actuator as follows.
- the control device 50 controls the compressor 3 so that the heating capacity of the heat pump unit 2 becomes the rated capacity (step S1).
- the heating capacity is the total amount of water heating per hour for the first heat exchanger 4 and the second heat exchanger 5.
- the control device 50 can control the heating capacity by controlling the capacity of the compressor 3.
- the control device 50 can control the capacity of the compressor 3 by controlling the driving speed, driving frequency, and the like of the compressor 3.
- the control device 50 controls the water flow rate by the pump 13 so that the heat pump outlet temperature detected by the heat pump outlet temperature sensor 30 becomes a predetermined heating temperature set value in the range of 65 ° C. to 90 ° C. .
- the control apparatus 50 controls the ventilation volume of the air blower 8 according to required evaporation capability.
- the evaporation capacity is the amount of heat absorbed by the refrigerant from the air in the evapor
- the control device 50 controls the refrigerant flow rate with the expansion valve 6 so that the compression element discharge temperature matches the target value.
- the compression element discharge temperature can be detected by a discharge temperature sensor 51 provided at B in FIGS. 2 and 6.
- the control device 50 stores a table that defines the relationship between parameters such as the heat pump outlet temperature, the outside air temperature, the heating capacity, and the target value of the compression element discharge temperature.
- the target value of the compression element discharge temperature is determined so as to obtain the maximum COP according to parameters such as the heat pump outlet temperature, the outside air temperature, and the heating capacity.
- the control device 50 determines a target value of the compression element discharge temperature based on parameters such as the heat pump outlet temperature, the outside air temperature, and the heating capacity, and the table. Then, the control device 50 determines whether or not the compression element discharge temperature matches the target value (step S2). If the compression element discharge temperature matches the target value in step S2, the control device 50 returns to step S1. If the compression element discharge temperature does not match the target value in step S2, the control device 50 controls the refrigerant flow rate with the expansion valve 6 so that the compression element discharge temperature matches the target value (step S3). . By controlling as described above, the COP during the high heating operation can be made sufficiently high.
- the superheat degree of the refrigerant coming out of the evaporator 7 is referred to as “evaporator outlet superheat degree”.
- the control device 50 may control the refrigerant flow rate with the expansion valve 6 so that the evaporator outlet superheat degree matches the target value, instead of the steps S2 and S3.
- the degree of superheat at the outlet of the evaporator 7 increases as the opening degree of the expansion valve 6 is reduced to lower the refrigerant flow rate.
- the evaporator outlet superheat degree can be detected as, for example, a temperature difference between the two temperature sensors provided with temperature sensors G and H in FIGS.
- the control device 50 stores a table that defines the relationship between parameters such as the heat pump outlet temperature, the outside air temperature, and the heating capacity and the target value of the evaporator outlet superheat degree.
- the target value of the evaporator outlet superheat degree is determined so as to obtain the maximum COP according to parameters such as the heat pump outlet temperature, the outside air temperature, and the heating capacity.
- the control device 50 determines a target value of the evaporator outlet superheat degree based on parameters such as the heat pump outlet temperature, the outside air temperature, the heating capacity, and the above table.
- step S2 the control apparatus 50 judges whether the evaporator exit superheat degree corresponds with target value. If the evaporator outlet superheat degree matches the target value, the control device 50 returns to step S1. When the evaporator outlet superheat degree does not coincide with the target value, the control device 50 replaces the refrigerant flow rate with the expansion valve 6 so that the evaporator outlet superheat degree coincides with the target value instead of step S3. Control. By controlling as described above, the COP during the high heating operation can be made sufficiently high.
- FIG. 6 is a pressure-enthalpy diagram of the low heating operation.
- a to H in FIG. 6 correspond to A to H in FIG.
- the refrigerant is compressed by the compression element 32 to a pressure equal to or lower than the critical pressure (A ⁇ B).
- the high-pressure refrigerant (B in FIG. 6) after being compressed by the compression element 32 is in a superheated gas state.
- the high-pressure refrigerant in the superheated gas state is cooled by the first heat exchanger 4 (B ⁇ C).
- the high-pressure refrigerant (C in FIG. 6) after being cooled by the first heat exchanger 4 is also in the superheated gas state.
- This high-pressure refrigerant is heated by the heat of the electric element 33 while reaching the internal space 39 (C ⁇ D).
- the state of the high-pressure refrigerant discharged from the second discharge passage 37 is D in FIG.
- This high-pressure refrigerant is condensed and liquefied by being cooled by the second heat exchanger 5 (D ⁇ E). Thereafter, the high-pressure refrigerant is further cooled by the high-low pressure heat exchanger 9 (E ⁇ F).
- the high-pressure refrigerant that has passed through the high-low pressure heat exchanger 9 is decompressed by the expansion valve 6 and becomes low-pressure refrigerant (F ⁇ G).
- This low-pressure refrigerant evaporates in the evaporator 7 (G ⁇ H).
- the low-pressure refrigerant evaporated in the evaporator 7 is heated in the high-low pressure heat exchanger 9 (H ⁇ A).
- the heat pump outlet temperature of 20 ° C. to 30 ° C. in such a low heating operation is lower than the critical temperature of carbon dioxide as a refrigerant.
- the compression element discharge pressure and the pressure of the refrigerant inside the first heat exchanger 4, the sealed container 31, and the second heat exchanger 5 become pressures below the critical pressure.
- FIG. 7 is a diagram illustrating an example of temperature changes of the refrigerant and water in the first heat exchanger 4 and the second heat exchanger 5 in the low heating operation. 7 correspond to B to E in FIGS. 2 and 6.
- the meaning of the horizontal axis in FIG. 7 is the same as the horizontal axis in FIG.
- the temperature of water entering the second heat exchanger 5, that is, the heat pump inlet temperature is about 9 ° C.
- the heat pump outlet temperature is about 25 ° C.
- the temperature of the refrigerant entering the first heat exchanger 4, that is, the compression element discharge temperature is about 45 ° C.
- the condensation saturation temperature of the refrigerant in the second heat exchanger 5 is about 22 ° C.
- condensation saturation temperature of the refrigerant in the second heat exchanger 5 is simply referred to as “condensation saturation temperature”.
- evaporation saturation temperature of the refrigerant in the evaporator 7 is simply referred to as “evaporation saturation temperature”.
- FIG. 8 is a flowchart showing the control operation of the control device 50 in the low heating operation.
- the control device 50 controls each actuator as follows.
- the control device 50 controls the compressor 3 so that the heating capacity of the heat pump unit 2 is lower than the heating capacity in the high heating operation, that is, lower than the rated capacity (step S11).
- step S ⁇ b> 11 the control device 50 controls the capacity of the compressor 3 to be lower than that in the high heating operation.
- the driving speed, driving frequency, etc. of the compressor 3 are lowered as compared with the high heating operation.
- the refrigerant flow rate in the low heating operation is lower than the refrigerant flow rate in the high heating operation.
- control device 50 controls the water flow rate by the pump 13 so that the heat pump outlet temperature detected by the heat pump outlet temperature sensor 30 becomes a predetermined heating temperature set value in the range of 20 ° C. to 30 ° C. .
- the water flow rate in the low heating operation is higher than the water flow rate in the high heating operation.
- control apparatus 50 controls the ventilation volume of the air blower 8 according to required evaporation capability.
- the control device 50 sets the refrigerant flow rate to the expansion valve 6 so that the state of the refrigerant flowing into the internal space 38 of the sealed container 31, that is, the state of the refrigerant in the second suction passage 36 becomes a superheated gas state.
- the opening degree of the expansion valve 6 is decreased, the refrigerant flow rate is decreased, and the degree of superheat of the refrigerant in the second suction passage 36 is increased.
- the degree of superheat is the difference between the temperature of superheated gas (that is, superheated steam) and the temperature of saturated steam. If the degree of superheat is greater than zero, the refrigerant is in a superheated gas state.
- the control device 50 estimates the degree of superheat SHsi of the refrigerant in the second suction passage 36 by a method described later (step S12).
- the control device 50 compares the estimated superheat degree SHsi with the reference value ⁇ (step S13).
- the reference value ⁇ is a predetermined value of zero or more. If the superheat degree SHsi is larger than the reference value ⁇ in step S13, it can be determined that the superheat degree SHsi is sufficiently large and the state of the refrigerant in the second suction passage 36 can be reliably maintained in the superheated gas state. In this case, the process returns to step S11.
- step S13 if the degree of superheat SHsi is equal to or less than the reference value ⁇ in step S13, it can be determined that the degree of superheat SHsi is not sufficient.
- the control device 50 increases the superheat degree SHsi by reducing the opening degree of the expansion valve 6 (step S14). Thereby, the state of the refrigerant in the second suction passage 36 can be reliably maintained in the superheated gas state.
- the degree of superheat SHsi of the refrigerant in the second suction passage 36 can be calculated from the condensation saturation temperature Tc and the refrigerant temperature Ts2 in the second suction passage 36 by the following equation.
- SHsi Ts2-Tc (2)
- the refrigerant has a higher heat transfer coefficient in the gas-liquid two-phase region than the region where the refrigerant is superheated gas and the region where the refrigerant is supercooled liquid. Heat transfer is promoted. For this reason, most of the region where the water temperature rises is a gas-liquid two-phase region.
- the low heating operation the water temperature change from the heat pump inlet temperature to the heat pump outlet temperature is small compared to the high heating operation.
- the low heating operation has a higher water flow rate and a higher heat transfer rate than the high heating operation.
- the temperature difference between the refrigerant and water at the pinch point is smaller in the low heating operation than in the high heating operation.
- the pinch point is a point at which the refrigerant temperature and the water temperature are closest.
- the gradient of the temperature change of the refrigerant with respect to the flow path direction is larger as it is closer to B (refrigerant inlet of the first heat exchanger 4) in FIG. 7, and is smaller as it is closer to the pinch point. Therefore, the inclination of the temperature change of the water with respect to the flow path direction is also small near the pinch point. Therefore, the water temperature Twp at the pinch point and the water temperature Twgc1i at the water inlet of the first heat exchanger 4 can be regarded as substantially equal. That is, the following equation holds. Twp ⁇ Twgc1i (3)
- the heat exchange amount Qgc1 in the first heat exchanger 4 can be calculated by the temperature difference between the refrigerant inlet and outlet. That is, the following equation holds.
- Qgc1 Gr ⁇ Cpr ⁇ (Td1 ⁇ Ts2) (4)
- Gr the refrigerant flow rate
- Cpr the constant pressure specific heat of the refrigerant
- Td1 the compression element discharge temperature.
- the refrigerant flow rate Gr can be estimated from the capacity of the compressor 3 and the outside air temperature.
- the compression element discharge temperature Td1 can be detected by the discharge temperature sensor 51.
- the heat exchange amount Qgc1 in the first heat exchanger 4 can also be calculated from the temperature difference between the refrigerant and water. That is, the following equation holds.
- Qgc1 Agc1 ⁇ Kgc1 ⁇ ⁇ Tgc1 (5)
- Agc1 is the heat transfer area of the first heat exchanger 4
- Kgc1 is the heat passage rate of the first heat exchanger 4
- ⁇ Tgc1 is the temperature difference between the refrigerant and water in the first heat exchanger 4.
- Agc1 is a fixed value.
- Kgc1 can be regarded as a substantially constant value.
- ⁇ Tgc1 can be calculated by the following equation, assuming an arithmetic average temperature difference.
- ⁇ Tgc1 (Td1 + Ts2) / 2 ⁇ (Two + Twgc1i) / 2 (6)
- Two is the heat pump outlet temperature.
- the arithmetic average temperature difference can be easily calculated by the above equation (6).
- a logarithmic average temperature difference may be used as ⁇ Tgc1. In that case, ⁇ Tgc1 can be calculated more accurately.
- the first heat exchange is performed based on the compression element discharge temperature Td1, the refrigerant temperature Ts2 of the second suction passage 36, and the heat pump outlet temperature Two by combining the expressions (4), (5), and (6).
- the water temperature Twgc1i at the water inlet of the vessel 4 can be estimated.
- Twgc1i thus estimated is equal to the water temperature Twp at the pinch point
- the water temperature Twp at the pinch point can be obtained.
- the condensation saturation temperature Tc can be calculated by the following equation.
- Tc Twp + ⁇ Tp (7)
- ⁇ Tp is the temperature difference between the refrigerant and water at the pinch point.
- the temperature difference ⁇ Tp between the refrigerant and the water at the pinch point is about 1 ° C. to 3 ° C.
- the superheat degree SHsi of the refrigerant in the second suction passage 36 can be obtained.
- the superheat degree SHsi of the refrigerant in the second suction passage 36 is set based on the compression element discharge temperature Td1, the refrigerant temperature Ts2 in the second suction passage 36, and the heat pump outlet temperature Two. Can be estimated.
- the method for estimating the water temperature Twgc1i at the water inlet of the first heat exchanger 4 may be as follows instead of the above method.
- the heat exchange amount Qgc1 in the first heat exchanger 4 can be calculated by the temperature difference between the water inlet and outlet. That is, the following equation holds.
- Qgc1 Gw ⁇ Cpw ⁇ (Two ⁇ Twgc1i)
- Gw is a water flow rate
- Cpw is the specific heat of water.
- the water flow rate Gw can be estimated from the driving speed of the pump 13. Alternatively, the water flow rate Gw may be detected by a flow rate sensor.
- the refrigerant temperature Ts2 of the second suction passage 36 Based on the compression element discharge temperature Td1, the refrigerant temperature Ts2 of the second suction passage 36, and the heat pump outlet temperature Two by combining any one of the formulas (4) and (5) with the formula (8).
- the water temperature Twgc1i at the water inlet of the first heat exchanger 4 can be estimated.
- Twgc1i estimated in this way is equal to the water temperature Twp at the pinch point
- the degree of superheat SHsi of the refrigerant in the second suction passage 36 can be estimated by using the above equations (7) and (2).
- the refrigerant temperature Ts2 in the second suction passage 36 can be detected by the refrigerant temperature sensor 52.
- the refrigerant temperature Ts2 in the second suction passage 36 may be detected by a temperature sensor provided on the outer surface of the sealed container 31 or the like.
- the refrigerant temperature Ts2 of the second suction passage 36 may be estimated as follows based on the compression element discharge temperature Td1 and the heat pump outlet temperature Two.
- the heat exchange amount Qgc1 in the first heat exchanger 4 can be regarded as being proportional to the temperature difference between the compression element discharge temperature Td1 and the heat pump outlet temperature Two. Therefore, if the proportionality coefficient is F, the following equation is established.
- Qgc1 F ⁇ (Td1 ⁇ Two) (9)
- the refrigerant temperature Ts2 of the second suction passage 36 can be estimated based on the compression element discharge temperature Td1 and the heat pump outlet temperature Two.
- the water temperature Twgc1i at the water inlet of the first heat exchanger 4 can be estimated based on the compression element discharge temperature Td1 and the heat pump outlet temperature Two by combining the above equations (8) and (9).
- Twgc1i estimated in this way is equal to the water temperature Twp at the pinch point
- the degree of superheat SHsi of the refrigerant in the second suction passage 36 can be estimated by using the above equations (7) and (2).
- the refrigerant in the second suction passage 36 is in a superheated gas state when calculating the heat exchange amount Qgc1 in the first heat exchanger 4. For this reason, assuming that the refrigerant in the second suction passage 36 is in a gas-liquid two-phase state, the heat exchange amount Qgc1 in the first heat exchanger 4 is estimated to be smaller than actual. Estimating the amount of heat exchange Qgc1 in the first heat exchanger 4 to be smaller than actual leads to estimating the temperature difference ⁇ Tgc1 of refrigerant and water in the first heat exchanger 4 to be smaller than actual.
- Estimating the temperature difference ⁇ Tgc1 between the refrigerant and water in the first heat exchanger 4 to be smaller than actual leads to estimating the water temperature Twgc1i at the water inlet of the first heat exchanger 4 higher than actual. Estimating the water temperature Twgc1i at the water inlet of the first heat exchanger 4 higher than actual leads to estimating the condensation saturation temperature Tc higher than actual.
- the superheat degree SHsi of the refrigerant in the second suction passage 36 is calculated by the above equation (2). For this reason, estimating the condensation saturation temperature Tc higher than actual leads to estimating the superheat degree SHsi of the refrigerant in the second suction passage 36 smaller than actual.
- the state of the refrigerant in the second suction passage 36 can be reliably controlled to the superheated gas state.
- step S12 of FIG. 8 instead of the method described above, the degree of superheat of the refrigerant in the second suction passage 36 based on the evaporation saturation temperature Te, the compression element suction temperature Ts1, and the compression element discharge temperature Td1 as follows. SHsi may be estimated.
- the polytropic index n can be regarded as a constant value determined from the physical property value of the refrigerant and the compressor efficiency.
- Td1 Ts1 ⁇ (Pd1 / Ps1) (n ⁇ 1) / n (10)
- Pd1 is a compression element discharge pressure.
- the compression element suction temperature Ts1 can be detected by providing a temperature sensor at A in FIGS.
- the compression element discharge temperature Td1 can be detected by a discharge temperature sensor 51 provided at B in FIGS.
- the evaporation saturation temperature Te can be detected by providing a temperature sensor at G in FIGS. Based on the evaporation saturation temperature Te, the evaporation saturation pressure Pe can be calculated from the relationship between the saturation temperature and the saturation pressure. If the pressure loss in the evaporator 7 is ignored, the compression element suction pressure Ps1 can be regarded as being equal to the evaporation saturation pressure Pe. Alternatively, the compression element suction pressure Ps1 may be calculated by subtracting a constant value of pressure loss from the evaporation saturation pressure Pe. The compression element discharge pressure Pd1 is calculated based on the evaporation saturation temperature Te, the compression element suction temperature Ts1, and the compression element discharge temperature Td1 by substituting the compression element suction pressure Ps1 thus determined in the above equation (10).
- the condensation saturation temperature Tc can be calculated from the relationship between the saturation temperature and the saturation pressure.
- the superheat degree SHsi of the refrigerant in the second suction passage 36 can be estimated.
- the heat pump device 1 of the first embodiment the following effects can be obtained.
- the superheat degree SHsi of the refrigerant in the second suction passage 36 can be estimated based on the detected temperatures of temperature sensors such as the heat pump outlet temperature sensor 30, the discharge temperature sensor 51, and the refrigerant temperature sensor 52. For this reason, it can control so that the state of the refrigerant
- the gas-liquid two-phase refrigerant can be reliably prevented from flowing into the sealed container 31 even during the low heating operation, the liquid refrigerant is not accumulated in the sealed container 31.
- the liquid refrigerant accumulated in the hermetic container 31 is heated by the compression element 32 or the electric element 33, the liquid refrigerant mixed with the refrigerating machine oil is vaporized, so that the refrigerating machine oil is foamed.
- the refrigerating machine oil is foamed, the refrigerating machine oil is mixed with the gas refrigerant, and the refrigerating machine oil flows out of the second discharge passage 37 along with the gas refrigerant.
- the refrigerating machine oil in the hermetic container 31 is insufficient, resulting in poor lubrication of the sliding portion of the compressor 3.
- a pressure sensor that detects the compression element discharge pressure Pd1 may be provided, and the degree of superheat of the refrigerant in the second suction passage 36 may be controlled based on the value of the pressure sensor.
- a temperature sensor may be provided in the water flow path 47 connecting the first heat exchanger 4 and the second heat exchanger 5, and the water temperature Twgc1i at the water inlet of the first heat exchanger 4 may be detected by the temperature sensor.
- a temperature sensor may be provided at an intermediate point of the refrigerant flow path of the second heat exchanger 5, and the condensation saturation temperature Tc may be directly detected by the temperature sensor.
- the effect of the present invention is particularly prominent when a refrigerant (for example, carbon dioxide) having a pressure at which the compression element discharge pressure during the high heating operation exceeds the critical pressure is used as in the first embodiment.
- a refrigerant for example, carbon dioxide
- the present invention can also be applied to the case of using a refrigerant whose compression element discharge pressure during high heating operation is a pressure equal to or lower than the critical pressure.
- refrigerant include R410A, R32, R22, R407C, propane, propylene, HFO-1234yf, HFO-1234ze, or a mixed refrigerant thereof.
- a general design method in the case of using a refrigerant whose compression element discharge pressure at the time of high heating operation is a pressure equal to or lower than the critical pressure is that the second suction passage 36 is adjusted according to the conditions at the time of high heating operation that operates at the rated capacity.
- the ratio of the size (heat exchange amount) of the first heat exchanger 4 and the second heat exchanger 5 is designed so that the refrigerant becomes superheated gas.
- the heat pump outlet temperature is low, the compression element discharge pressure is lowered, and the enthalpy difference between the first heat exchanger 4 and the second heat exchanger 5 is reduced.
- the refrigerant in the second suction passage 36 is likely to be in a gas-liquid two-phase state.
- the same effects as described above can be obtained by applying the present invention. Therefore, it is meaningful to apply the present invention even when a refrigerant is used in which the discharge pressure of the compression element during high heating operation is a critical pressure or less.
- FIG. 9 is a flowchart showing the control operation of the control device 50 in the low heating operation of the heat pump device 1 according to the second embodiment of the present invention. Steps S11 to S13 in FIG. 9 are the same as those in the first embodiment, and thus description thereof is omitted.
- the control device 50 causes the compressor 3 to increase the capacity of the compressor 3. Is controlled (for example, by increasing the driving speed of the compressor 3), the superheat degree SHsi of the refrigerant in the second suction passage 36 is increased (step S15).
- the state of the refrigerant in the second suction passage 36 can be more reliably maintained in the superheated gas state. Since the second embodiment is the same as the first embodiment except for the matters described above, further description is omitted.
- FIG. 10 is a flowchart showing the control operation of the control device 50 in the low heating operation of the heat pump device 1 according to the third embodiment of the present invention. Since step S11 to step S13 in FIG. 10 are the same as those in the first embodiment, the description thereof is omitted.
- the control device 50 controls the pump 13 so that the water flow rate becomes low.
- the superheat degree SHsi of the refrigerant in the second suction passage 36 is increased (step S16).
- the compression element discharge pressure increases.
- the saturated vapor line of the pressure-enthalpy diagram is inclined to the upper left, the enthalpy of the saturated gas becomes smaller as the pressure increases.
- the degree of superheat SHsi increases.
- the state of the refrigerant in the second suction passage 36 can be more reliably maintained in the superheated gas state. Since the third embodiment is the same as the first embodiment except for the matters described above, further description is omitted.
- FIG. 11 is a configuration diagram showing the heat pump unit 2 included in the heat pump device 1 according to the fourth embodiment of the present invention.
- the heat pump unit 2 according to the fourth embodiment has a configuration similar to that of the first embodiment, and a second suction passage from the first discharge passage 35 without passing through the first heat exchanger 4. Further, a bypass passage 55 for flowing the refrigerant to 36 and a bypass valve 56 provided in the bypass passage 55 are further provided.
- the bypass channel 55 is a channel that bypasses the refrigerant channel of the first heat exchanger 4.
- the bypass valve 56 is a flow path control element that makes the amount of refrigerant passing through the bypass flow path 55 variable.
- the bypass valve 56 is closed, all of the superheated gas refrigerant discharged from the first discharge passage 35 passes through the first heat exchanger 4. That is, the state is the same as in the first embodiment.
- the bypass valve 56 is opened, the superheated refrigerant discharged from the first discharge passage 35 flows separately into the refrigerant flow path of the first heat exchanger 4 and the bypass flow path 55. . Then, the refrigerant that has passed through the refrigerant flow path of the first heat exchanger 4 and the refrigerant that has passed through the bypass flow path 55 merge and flow to the second suction passage 36.
- FIG. 12 is a flowchart showing the control operation of the control device 50 in the low heating operation of the heat pump device 1 according to the fourth embodiment of the present invention. Steps S11 to S13 in FIG. 12 are the same as those in the first embodiment, and a description thereof will be omitted.
- the control device 50 when the superheat degree SHsi of the refrigerant in the second suction passage 36 is equal to or less than the reference value ⁇ in step S13, the control device 50 causes the bypass valve 56 to increase the opening degree of the bypass valve 56. By controlling 56, the superheat degree SHsi of the refrigerant in the second suction passage 36 is increased (step S17).
- step S17 when the bypass valve 56 is closed, the bypass valve 56 is opened to a predetermined opening, and when the bypass valve 56 is already open, the opening of the bypass valve 56 is increased.
- the opening degree of the bypass valve 56 is increased, the ratio of the refrigerant passing through the bypass passage 55 increases. Since the refrigerant in the superheated gas state that has passed through the bypass flow path 55 has not exchanged heat, it is at a higher temperature than the refrigerant that has passed through the refrigerant flow path of the first heat exchanger 4. Therefore, the degree of superheat SHsi of the refrigerant in the second suction passage 36 is increased by increasing the opening degree of the bypass valve 56 and increasing the ratio of the refrigerant passing through the bypass flow path 55.
- the state of the refrigerant in the second suction passage 36 can be more reliably maintained in the superheated gas state. Since the fourth embodiment is the same as the first embodiment except for the matters described above, further description is omitted.
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Abstract
Description
図1は、本発明の実施の形態1のヒートポンプ装置を示す構成図である。図1に示すように、本実施の形態1のヒートポンプ装置1は、水を加熱するヒートポンプユニット2と、貯湯タンク10と、制御装置50とを有する。貯湯タンク10は、上側が高温で下側が低温になる温度成層を形成して水を貯留する。貯湯タンク10の下部と、ヒートポンプユニット2の入口12とは、入口配管11を介して接続されている。入口配管11の途中には、ポンプ13が設置されている。貯湯タンク10の上部には、上部配管14の一端が接続されている。上部配管14の他端側は、二つに分岐して、給湯混合弁15の第一入口と風呂混合弁16の第一入口とにそれぞれ接続されている。ヒートポンプユニット2の出口17は、出口配管18を介して、上部配管14の途中の位置に接続されている。ヒートポンプユニット2の詳細については後述する。本実施の形態1では、加熱する対象流体が水である場合について説明するが、本発明における対象流体は、例えばブライン、不凍液など、水以外の流体でも良い。
C3=C1×Rhp+C2×(1-Rhp) ・・・(1)
SHsi=Ts2-Tc ・・・(2)
Twp≒Twgc1i ・・・(3)
Qgc1=Gr×Cpr×(Td1-Ts2) ・・・(4)
ただし、Grは冷媒流量、Cprは冷媒の定圧比熱、Td1は圧縮要素吐出温度である。冷媒流量Grは、圧縮機3の容量及び外気温度などから推定できる。圧縮要素吐出温度Td1は、吐出温度センサ51で検知できる。
Qgc1=Agc1×Kgc1×ΔTgc1 ・・・(5)
ただし、Agc1は第一熱交換器4の伝熱面積、Kgc1は第一熱交換器4の熱通過率、ΔTgc1は第一熱交換器4での冷媒と水の温度差である。Agc1は固定値である。Kgc1は、ほぼ一定値とみなせる。ΔTgc1は、算術平均温度差とすると、次式で算出できる。
ΔTgc1=(Td1+Ts2)/2-(Two+Twgc1i)/2 ・・・(6)
ただし、Twoはヒートポンプ出口温度である。算術平均温度差は上記(6)式で簡易に算出できる。また、ΔTgc1として、対数平均温度差を用いても良い。その場合には、より正確にΔTgc1を算出できる。
Tc=Twp+ΔTp ・・・(7)
ただし、ΔTpはピンチポイントでの冷媒と水の温度差である。ピンチポイントでの冷媒と水の温度差ΔTpは、約1℃~3℃程度である。上記(7)式で算出した凝縮飽和温度Tcを上記(2)式に代入することで第二吸入通路36の冷媒の過熱度SHsiを求めることができる。図8のステップS12では、以上のようにして、圧縮要素吐出温度Td1、第二吸入通路36の冷媒温度Ts2、及びヒートポンプ出口温度Twoに基づいて、第二吸入通路36の冷媒の過熱度SHsiを推定できる。
Qgc1=Gw×Cpw×(Two-Twgc1i) ・・・(8)
ただし、Gwは水流量、Cpwは水の比熱である。水流量Gwは、ポンプ13の駆動速度から推定できる。あるいは流量センサで水流量Gwを検知しても良い。上記(4)式及び(5)式のいずれか一方と、上記(8)とを連立することで、圧縮要素吐出温度Td1、第二吸入通路36の冷媒温度Ts2、及びヒートポンプ出口温度Twoに基づいて、第一熱交換器4の水入口の水温Twgc1iを推定できる。そのようにして推定したTwgc1iがピンチポイントでの水温Twpに等しいとみなし、上記(7)式及び(2)式を用いることで、第二吸入通路36の冷媒の過熱度SHsiを推定できる。
Qgc1=F×(Td1-Two) ・・・(9)
上記(4)式及び(9)式を連立することで、圧縮要素吐出温度Td1及びヒートポンプ出口温度Twoに基づいて、第二吸入通路36の冷媒温度Ts2を推定できる。また、上記(8)式及び(9)式を連立することで、圧縮要素吐出温度Td1及びヒートポンプ出口温度Twoに基づいて、第一熱交換器4の水入口の水温Twgc1iを推定できる。そのようにして推定したTwgc1iがピンチポイントでの水温Twpに等しいとみなし、上記(7)式及び(2)式を用いることで、第二吸入通路36の冷媒の過熱度SHsiを推定できる。
Td1=Ts1×(Pd1/Ps1)(n-1)/n ・・・(10)
ただし、Pd1は圧縮要素吐出圧力である。圧縮要素吸入温度Ts1は、図2及び図6中のAに温度センサを設けることで検知できる。圧縮要素吐出温度Td1は、図2及び図6中のBに設けた吐出温度センサ51で検知できる。
(1)貯湯運転時すなわち高加熱運転時には、圧縮要素吐出圧力Pd1が超臨界圧になり、第一熱交換器4及び第二熱交換器5の冷媒は凝縮しない。このため、COPが最大になるように膨張弁6で冷媒流量を制御できる。
(2)湯張り運転時すなわち低加熱運転時には、第二吸入通路36の冷媒の状態が過熱ガス状態になるように制御することで、密閉容器31の内部空間38に気液二相冷媒が流入することを確実に防止できる。これにより、信頼性を高めつつ、冷媒流量を適正に制御できる。その結果、効率の良い運転ができる。
(3)ヒートポンプ出口温度センサ30、吐出温度センサ51及び冷媒温度センサ52等の温度センサの検知温度に基づいて、第二吸入通路36の冷媒の過熱度SHsiを推定できる。このため、高価な圧力センサを用いずに、低加熱運転時の第二吸入通路36の冷媒の状態が過熱ガス状態になるように制御できる。
(4)低加熱運転時にも密閉容器31への気液二相冷媒の流入を確実に防止できるので、密閉容器31に液冷媒が蓄積されない。密閉容器31に蓄積された液冷媒が圧縮要素32あるいは電動要素33により加熱されると、冷凍機油と混合している液冷媒が気化することで冷凍機油が発泡する。冷凍機油が発泡すると、冷凍機油がガス冷媒に混合し、冷凍機油がガス冷媒に伴って第二吐出通路37から流出する。その結果、密閉容器31内の冷凍機油が不足し、圧縮機3の摺動部の潤滑不良が生じる。また、第二熱交換器5に冷凍機油が滞留し、冷媒の伝熱が阻害されて、性能が低下する。これに対し、本実施の形態1によれば、密閉容器31に液冷媒が蓄積されないので、これらの弊害を確実に防止できる。
次に、図9を参照して、本発明の実施の形態2について説明するが、上述した実施の形態1との相違点を中心に説明し、同一部分または相当部分は同一符号を付し説明を省略する。図9は、本発明の実施の形態2のヒートポンプ装置1の低加熱運転での制御装置50の制御動作を示すフローチャートである。図9のステップS11からステップS13は実施の形態1と同様であるので説明を省略する。本実施の形態2では、ステップS13で第二吸入通路36の冷媒の過熱度SHsiが参照値α以下である場合には、制御装置50は、圧縮機3の容量が大きくなるように圧縮機3を制御すること(例えば圧縮機3の駆動速度を速くすること)で、第二吸入通路36の冷媒の過熱度SHsiを上昇させる(ステップS15)。これにより、本実施の形態2では、第二吸入通路36の冷媒の状態をより確実に過熱ガス状態に維持することができる。本実施の形態2は、上述した事項以外は実施の形態1と同様であるので、これ以上の説明を省略する。
次に、図10を参照して、本発明の実施の形態3について説明するが、上述した実施の形態1との相違点を中心に説明し、同一部分または相当部分は同一符号を付し説明を省略する。図10は、本発明の実施の形態3のヒートポンプ装置1の低加熱運転での制御装置50の制御動作を示すフローチャートである。図10のステップS11からステップS13は実施の形態1と同様であるので説明を省略する。本実施の形態3では、ステップS13で第二吸入通路36の冷媒の過熱度SHsiが参照値α以下である場合には、制御装置50は、水流量が低くなるようにポンプ13を制御することで、第二吸入通路36の冷媒の過熱度SHsiを上昇させる(ステップS16)。水流量を低くすると、圧縮要素吐出圧力が上昇するが、圧力-エンタルピ線図の飽和蒸気線が左上に傾いているため、圧力が上昇するほど飽和ガスのエンタルピが小さくなる。その結果、過熱度SHsiが大きくなる。本実施の形態3によれば、第二吸入通路36の冷媒の状態をより確実に過熱ガス状態に維持することができる。本実施の形態3は、上述した事項以外は実施の形態1と同様であるので、これ以上の説明を省略する。
次に、図11及び図12を参照して、本発明の実施の形態4について説明するが、上述した実施の形態1との相違点を中心に説明し、同一部分または相当部分は同一符号を付し説明を省略する。図11は、本発明の実施の形態4のヒートポンプ装置1が備えるヒートポンプユニット2を示す構成図である。図11に示すように、本実施の形態4のヒートポンプユニット2は、実施の形態1と同様の構成に加え、第一吐出通路35から第一熱交換器4を経由せずに第二吸入通路36へ冷媒を流すバイパス流路55と、このバイパス流路55に設けられたバイパス弁56とをさらに備える。バイパス流路55は、第一熱交換器4の冷媒流路をバイパスする流路である。バイパス弁56は、バイパス流路55を通る冷媒の量を可変にする流路制御要素である。バイパス弁56を閉じた状態では、第一吐出通路35から吐出された過熱ガス状態の冷媒がすべて第一熱交換器4を通る状態になる。すなわち、実施の形態1と同様の状態になる。これに対し、バイパス弁56を開いた状態では、第一吐出通路35から吐出された過熱ガス状態の冷媒は、第一熱交換器4の冷媒流路と、バイパス流路55とに分かれて流れる。そして、第一熱交換器4の冷媒流路を通過した冷媒と、バイパス流路55を通過した冷媒とが合流し、第二吸入通路36へ流れる。
Claims (7)
- 密閉容器と、前記密閉容器の内部に設けられた圧縮要素と、前記密閉容器の外部から吸入される低圧冷媒を前記密閉容器の内部空間へ放出せずに前記圧縮要素へ導く第一吸入通路と、前記圧縮要素により圧縮された高圧冷媒を前記密閉容器の内部空間へ放出せずに前記密閉容器の外部へ吐出する第一吐出通路と、前記第一吐出通路から吐出された後に熱交換をした高圧冷媒を圧縮せずに前記密閉容器の内部空間へ放出する第二吸入通路と、前記密閉容器の内部空間の高圧冷媒を圧縮せずに前記密閉容器の外部へ吐出する第二吐出通路とを有する圧縮機と、
前記第一吐出通路から吐出された高圧冷媒の熱で対象流体を加熱する第一熱交換器と、
前記第二吐出通路から吐出された高圧冷媒の熱で前記対象流体を加熱する第二熱交換器と、
前記第二熱交換器を通過した高圧冷媒を膨張させて低圧冷媒にする膨張部と、
前記膨張部を通過した低圧冷媒を蒸発させる蒸発器と、
高加熱運転と、前記第一熱交換器及び前記第二熱交換器の合計の加熱量が前記高加熱運転に比べて小さい低加熱運転とを行う制御手段と、
を備え、
前記制御手段は、前記低加熱運転のとき、前記第二吸入通路の冷媒の状態が過熱ガス状態になるように制御するヒートポンプ装置。 - 前記高加熱運転のときには前記圧縮要素から吐出される冷媒の圧力が臨界圧力を超える圧力になり、前記低加熱運転のときには前記圧縮要素から吐出される冷媒の圧力が臨界圧力以下の圧力になる請求項1に記載のヒートポンプ装置。
- 前記制御手段は、前記高加熱運転のとき、前記圧縮要素から吐出される冷媒の温度または前記蒸発器から出る冷媒の過熱度が目標値になるように、前記膨張部により冷媒流量を制御する請求項1または請求項2に記載のヒートポンプ装置。
- 前記制御手段は、前記低加熱運転のとき、前記圧縮要素から吐出される冷媒の温度と、前記第二吸入通路の冷媒の温度と、前記第一熱交換器から出る前記対象流体の温度とに基づいて、前記第二吸入通路の冷媒の過熱度を推定し、その推定結果に基づいて、前記膨張部の開度、前記圧縮機の容量、及び前記対象流体の流量のうちの少なくとも一つを制御する請求項1から請求項3のいずれか一項に記載のヒートポンプ装置。
- 前記制御手段は、前記低加熱運転のとき、前記圧縮要素に吸入される冷媒の温度と、前記圧縮要素から吐出される冷媒の温度と、前記蒸発器の蒸発飽和温度とに基づいて、前記第二吸入通路の冷媒の過熱度を推定し、その推定結果に基づいて、前記膨張部の開度、前記圧縮機の容量、及び前記対象流体の流量のうちの少なくとも一つを制御する請求項1から請求項3のいずれか一項に記載のヒートポンプ装置。
- 前記第一吐出通路から前記第一熱交換器を経由せずに前記第二吸入通路へ冷媒を流すバイパス流路と、
前記バイパス流路を通る冷媒の量を可変にする流路制御要素と、
を備え、
前記制御手段は、前記低加熱運転のとき、前記第二吸入通路の冷媒の状態が過熱ガス状態になるように、前記バイパス流路を通る冷媒の量を前記流路制御要素により制御する請求項1から請求項3のいずれか一項に記載のヒートポンプ装置。 - 貯湯タンクを備え、
前記制御手段は、前記第一熱交換器及び前記第二熱交換器で加熱された水を前記貯湯タンクに流入させる貯湯運転のときは前記高加熱運転を行い、前記第一熱交換器及び前記第二熱交換器で加熱された水を浴槽へ供給する湯張り運転のときは前記低加熱運転を行う請求項1から請求項6のいずれか一項に記載のヒートポンプ装置。
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Cited By (3)
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CN105627630A (zh) * | 2016-03-01 | 2016-06-01 | 田幼华 | 一种热泵系统 |
CN108278751A (zh) * | 2017-12-26 | 2018-07-13 | 广东申菱环境系统股份有限公司 | 一种显热潜热双回收的节能空调系统 |
CN108278751B (zh) * | 2017-12-26 | 2021-11-16 | 广东申菱环境系统股份有限公司 | 一种显热潜热双回收的节能空调系统 |
Also Published As
Publication number | Publication date |
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EP3128256A4 (en) | 2017-12-27 |
JP6233499B2 (ja) | 2017-11-22 |
JPWO2015136595A1 (ja) | 2017-04-06 |
EP3128256A1 (en) | 2017-02-08 |
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