WO2016147389A1 - ヒートポンプシステム - Google Patents
ヒートポンプシステム Download PDFInfo
- Publication number
- WO2016147389A1 WO2016147389A1 PCT/JP2015/058291 JP2015058291W WO2016147389A1 WO 2016147389 A1 WO2016147389 A1 WO 2016147389A1 JP 2015058291 W JP2015058291 W JP 2015058291W WO 2016147389 A1 WO2016147389 A1 WO 2016147389A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- heat
- heat exchanger
- refrigerant
- mode
- port
- Prior art date
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- 239000003507 refrigerant Substances 0.000 claims abstract description 172
- 238000010438 heat treatment Methods 0.000 claims abstract description 70
- 238000005338 heat storage Methods 0.000 claims description 60
- 238000007906 compression Methods 0.000 claims description 35
- 230000006835 compression Effects 0.000 claims description 34
- 239000002826 coolant Substances 0.000 claims description 12
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 166
- 238000010586 diagram Methods 0.000 description 18
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 8
- 230000007423 decrease Effects 0.000 description 7
- 239000010721 machine oil Substances 0.000 description 6
- 229910002092 carbon dioxide Inorganic materials 0.000 description 4
- 239000001569 carbon dioxide Substances 0.000 description 4
- 230000003247 decreasing effect Effects 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 238000005260 corrosion Methods 0.000 description 2
- 230000007797 corrosion Effects 0.000 description 2
- 230000003628 erosive effect Effects 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 229920006395 saturated elastomer Polymers 0.000 description 2
- 239000011555 saturated liquid Substances 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 230000002528 anti-freeze Effects 0.000 description 1
- 239000012267 brine Substances 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000003673 groundwater Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000003921 oil Substances 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
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D3/00—Hot-water central heating systems
- F24D3/18—Hot-water central heating systems using heat pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
- F24D19/1015—Arrangement or mounting of control or safety devices for water heating systems for central heating using a valve or valves
- F24D19/1024—Arrangement or mounting of control or safety devices for water heating systems for central heating using a valve or valves a multiple way valve
-
- 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
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- 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
- F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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- 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
- F24H15/254—Room temperature
-
- 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
- F24H15/305—Control of valves
- F24H15/32—Control of valves of switching valves
-
- 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
-
- 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
- F24H15/395—Information to users, e.g. alarms
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- 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
- F24H15/45—Control of fluid heaters characterised by the type of controllers using electronic processing, e.g. computer-based remotely accessible
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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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/12—Hot water central heating systems using heat pumps
Definitions
- the present invention relates to a heat pump system.
- a hot water supply having a gas cooler having a high temperature side refrigerant pipe, a low temperature side refrigerant pipe and a water pipe, a sealed container, a compression unit, an electric motor, a suction pipe, a discharge pipe, a refrigerant reintroduction pipe and a refrigerant redischarge pipe
- a hot water supply cycle device including a compressor is disclosed.
- the low-pressure refrigerant is directly guided to the compression section by the suction pipe, and the high-pressure refrigerant compressed by the compression section is discharged directly from the discharge pipe to the outside of the sealed container without being discharged into the sealed container.
- the refrigerant after heat exchange through the pipe is guided into the sealed container from the refrigerant reintroduction pipe, and the refrigerant after passing through the electric motor in the sealed container is re-discharged out of the sealed container from the refrigerant re-discharge pipe, and the low-temperature side refrigerant Send to piping.
- Patent Document 2 includes a first compression unit, a first heat exchanger, a second compression unit, and a second heat exchanger, branches water supplied from a water inlet pipe, and includes a first heat exchanger and a second heat exchanger.
- An apparatus for flowing heat in parallel with two heat exchangers to perform heat exchange is disclosed.
- the refrigerant flows in series to the high temperature side refrigerant pipe and the low temperature side refrigerant pipe, and water exchanges heat in series in the order of the low temperature side refrigerant pipe and the high temperature side refrigerant pipe.
- the incoming water temperature is 9 ° C.
- the outgoing hot water temperature is 65 ° C.
- the temperature difference between the water outlet and the inlet of the gas cooler is large, and the water flow rate is small.
- the temperature difference between the water outlet and the inlet of the gas cooler is, for example, about 5 ° C. to 10 ° C. If the heating capacity is the same as the hot water storage operation, the water flow rate becomes extremely large. For this reason, when a gas cooler designed for hot water storage operation is used for heating operation, the flow rate of water increases and the pressure loss of water increases. In addition, corrosion (erosion) may occur in the heat transfer tubes.
- the present invention has been made to solve the above-described problems, and provides a heat pump system that can satisfactorily cope with both an operation with a high heat medium flow rate and an operation with a low heat medium flow rate. Objective.
- the heat pump system of the present invention includes a compressor for compressing a refrigerant, a refrigerant compressed by the compressor, a first heat exchanger for exchanging heat between the heat medium, a refrigerant compressed by the compressor, A second heat exchanger that exchanges heat with the heat medium, a first pipe through which the refrigerant supplied from the compressor to the first heat exchanger passes, and a refrigerant that returns from the first heat exchanger to the compressor pass The second pipe, the third pipe through which the refrigerant supplied from the compressor to the second heat exchanger after returning from the first heat exchanger passes, and the switching for switching the flow of the heat medium between the first mode and the second mode And in the first mode, the heat medium flows through the first heat exchanger and the second heat exchanger in series, and in the second mode, the heat medium parallels the first heat exchanger and the second heat exchanger. It is flowing.
- the heat pump system includes the switching device that switches the flow of the heat medium between the first mode and the second mode, and in the first mode, the heat medium connects the first heat exchanger and the second heat exchanger in series. In the second mode, the heat medium flows in parallel through the first heat exchanger and the second heat exchanger, so that it can cope with both operation with a high heat medium flow rate and operation with a low heat medium flow rate. It becomes possible to provide a simple heat pump system.
- Ph diagram that is, a Mollier diagram, of the refrigerant circuit of the heat pump system in the second mode (heating operation). It is a graph which shows the change of the temperature of the refrigerant
- It is a block diagram which shows the heat pump system of Embodiment 2 of this invention. It is a figure which shows the state of the 1st mode of the heat pump system of Embodiment 3 of this invention. It is a figure which shows the state of the 2nd mode of the heat pump system of Embodiment 3 of this invention.
- water is a concept including liquid water of all temperatures from low-temperature cold water to high-temperature hot water.
- FIG. 1 is a configuration diagram showing a heat pump system according to Embodiment 1 of the present invention.
- the heat pump system 1 of Embodiment 1 includes a refrigerant circuit including a compressor 3, a first heat exchanger 4, a second heat exchanger 5, an expansion valve 6, and an evaporator 7. .
- the first heat exchanger 4 and the second heat exchanger 5 are heat exchangers that heat the heat medium with the heat of the refrigerant.
- the first heat exchanger 4 has a refrigerant passage 4a and a heat medium passage 4b. Heat is exchanged between the refrigerant flowing through the refrigerant passage 4a and the heat medium flowing through the heat medium passage 4b.
- the second heat exchanger 5 has a refrigerant passage 5a and a heat medium passage 5b. Heat is exchanged between the refrigerant flowing through the refrigerant passage 5a and the heat medium flowing through the heat medium passage 5b.
- the heat medium in the present invention may be a fluid other than water, such as brine or antifreeze.
- the expansion valve 6 is a decompression device that decompresses the refrigerant.
- the evaporator 7 is a heat exchanger that evaporates the refrigerant.
- the evaporator 7 is an air refrigerant heat exchanger that performs heat exchange between air and the refrigerant.
- the heat pump system 1 further includes a blower 8 that blows air to the evaporator 7 and a high and 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 the present invention is not limited to the one that exchanges heat between the air and the refrigerant, and may be one that exchanges heat between the ground water, solar hot water, and the refrigerant, for example.
- the high / low pressure heat exchanger 9 has a high pressure passage 9a and a low pressure passage 9b. Heat exchange is performed between the high-pressure refrigerant flowing through the high-pressure passage 9a and the low-pressure refrigerant flowing through the low-pressure passage 9b.
- the compressor 3 includes a sealed container 31, a compression unit 32, and an electric motor 33.
- the compression unit 32 and the electric motor 33 are disposed inside the sealed container 31.
- a compression unit 32 is disposed below the electric motor 33.
- the compression unit 32 is driven by the electric motor 33.
- the electric motor 33 includes a stator 33a and a rotor 33b.
- a first pipe 35, a second pipe 36, a third pipe 37, and a fourth pipe 34 are connected to the compressor 3.
- the high-pressure refrigerant compressed by the compression unit 32 is discharged to the first pipe 35.
- the high-pressure refrigerant is supplied to the refrigerant passage 4 a of the first heat exchanger 4 through the first pipe 35 without being discharged into the internal spaces 38 and 39 of the sealed container 31.
- the high-pressure refrigerant is cooled with water while passing through the refrigerant passage 4 a of the first heat exchanger 4.
- the high-pressure refrigerant that has passed through the first heat exchanger 4 passes through the second pipe 36 and returns from the first heat exchanger 4 to the compressor 3.
- the outlet of the second pipe 36 is located in the internal space 38 between the electric motor 33 and the compression unit 32.
- the high-pressure refrigerant that has been sucked into the compressor 3 through the second pipe 36 is discharged into the internal space 38 between the electric motor 33 and the compression unit 32 without being compressed.
- the inlet of the third pipe 37 is located in the internal space 39 above the electric motor 33.
- the high-pressure refrigerant in the internal space 38 reaches the internal space 39 on the upper side of the electric motor 33 through the gap between the rotor 33 b and the stator 33 a of the electric motor 33.
- the electric motor 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 motor 33.
- the high-pressure refrigerant in the internal space 39 on the upper side of the electric motor 33 is supplied to the refrigerant passage 5a of the second heat exchanger 5 through the third pipe 37 without being compressed.
- the high-pressure refrigerant is cooled with water while passing through the refrigerant passage 5a of the second heat exchanger 5.
- the high-pressure refrigerant that has passed through the second heat exchanger 5 flows into the high-pressure passage 9 a of the high-low pressure heat exchanger 9.
- the high-pressure refrigerant that has passed through the high-pressure passage 9 a reaches the expansion valve 6.
- the high-pressure refrigerant is decompressed by being expanded by the expansion valve 6 and becomes a low-pressure refrigerant.
- This low-pressure refrigerant flows into 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 flows into the low-pressure passage 9 b of the high-low pressure heat exchanger 9.
- the low-pressure refrigerant that has passed through the low-pressure passage 9 b passes through the fourth pipe 34 and is sucked into the compressor 3.
- the low-pressure refrigerant that has passed through the fourth pipe 34 is guided to the compression unit 32 without being discharged into the internal spaces 38 and 39 of the sealed container 31.
- the high pressure refrigerant in the high pressure passage 9a is cooled and the low pressure refrigerant in the low pressure passage 9b is heated by heat exchange of the high and low pressure heat exchanger 9.
- the pressure of the refrigerant discharged from the compression unit 32 is referred to as “compression unit discharge pressure”, and the pressure of the refrigerant sucked into the compression unit 32 is referred to as “compression unit suction pressure”.
- the temperature of the refrigerant is referred to as “compression section discharge temperature”, and the temperature of the refrigerant sucked into the compression section 32 is referred to as “compression section suction temperature”.
- the pressure of the high-pressure refrigerant in the first pipe 35 is equal to the compression section discharge pressure.
- the pressure of the high-pressure refrigerant that has passed through the first pipe 35 decreases due to the pressure loss that reaches the second pipe 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 in the first pipe 35, that is, the compression portion discharge pressure.
- the heat pump system 1 includes a switching device that switches the flow of the heat medium between the first mode and the second mode. In the first mode, the heat medium flows through the first heat exchanger 4 and the second heat exchanger 5 in series. In the second mode, the heat medium flows through the first heat exchanger 4 and the second heat exchanger 5 in parallel.
- the heat pump system 1 includes a heat medium inlet 10, a heat medium outlet 11, a four-way valve 12, and a check valve 13.
- the four-way valve 12 is a flow path switching valve (direction switching valve) having a first port 12a, a second port 12b, a third port 12c, and a fourth port 12d.
- the four-way valve 12 communicates the first port 12a and the second port 12b, and communicates the first port 12a and the fourth port 12d with the first state in which the third port 12c and the fourth port 12d are communicated. And the second state in which the second port 12b and the third port 12c communicate with each other can be switched.
- the first passage 14 connects the first port 12 a and the heat medium outlet 11.
- the second passage 15 connects between the second port 12 b and the heat medium passage 4 b of the first heat exchanger 4.
- path 16 connects between the branch part 17 which branches the water before a heating in the 2nd mode, and the 3rd port 12c.
- the fourth passage 18 includes a junction 19 where the water heated by the first heat exchanger 4 and the heat medium heated by the second heat exchanger merge in the second mode, and the fourth port 12d. Connect between them.
- the check valve 13 prevents the back flow of the fourth passage 18.
- the fifth passage 20 connects between the heat medium inlet 10 and the heat medium passage 5 b of the second heat exchanger 5. There is a branching portion 17 in the middle of the fifth passage 20.
- the sixth passage 21 connects between the heat medium passage 4 b of the first heat exchanger 4 and the heat medium passage 5 b of the second heat exchanger 5. There is a heat medium passage 4 b between the second passage 15 and the sixth passage 21. There is a junction 19 in the middle of the sixth passage 21. There is a heat medium passage 5 b between the fifth passage 20 and the sixth passage 21.
- the check valve 13 allows the flow in the direction from the merging portion 19 toward the fourth port 12d, and blocks the flow in the reverse direction.
- the sixth passage 21 corresponds to a switching device that switches the flow of the heat medium between the first mode and the second mode.
- FIG. 2 is a configuration diagram showing the hot water supply / heating system according to the first embodiment of the present invention.
- the hot water supply and heating system 100 of the first embodiment shown in FIG. 2 includes the heat pump unit 2, the heat storage tank 22, the circulation pump 23, the control device 50, the terminal device 60, and the indoor heating device 90.
- the heat pump unit 2 incorporates the heat pump system 1 shown in FIG. Water is stored in the heat storage tank 22.
- a temperature stratification in which the upper side is a high temperature and the lower side is a low temperature can be formed due to a difference in water density due to a temperature difference.
- a water supply pipe 30 is connected to the lower part of the heat storage tank 22.
- the hot water supply and heating system 100 can perform a heat storage operation in which heat generated by the heat pump system 1 of the heat pump unit 2 is stored in the heat storage tank 22.
- hot water heated by the heat pump system 1 is stored in the heat storage tank 22.
- the heat exchanger illustrated omitted which heat-exchanges the heat medium and water which were heated with the heat pump system 1 is provided, and the hot water heated with the said heat exchanger is stored in a thermal storage tank. 22 may be stored.
- hot water stored in the heat storage tank 22 is sent out to the hot water supply pipe 25.
- the heat storage tank 22 has a first water outlet 26 and a first water inlet 27. Water inside the heat storage tank 22 exits from the first water outlet 26. Hot water heated by the heat pump system 1 of the heat pump unit 2 enters the heat storage tank 22 from the first water inlet 27.
- the first water outlet 26 is in the lower part of the heat storage tank 22.
- the first water inlet 27 is at the top of the heat storage tank 22.
- the three-way valve 24 is a flow path switching valve (direction switching valve) having a first port 24a, a second port 24b, and a third port 24c.
- the three-way valve 24 has a state in which the third port 24c communicates with the first port 24a and blocks the second port 24b, and a state in which the third port 24c communicates with the second port 24b and blocks the first port 24a. Can be switched to.
- the lower pipe 28 connects between the first water outlet 26 of the heat storage tank 22 and the upstream end of the first common pipe 29.
- the downstream end of the first common pipe 29 is connected to the heat medium inlet 10 of the heat pump system 1 of the heat pump unit 2.
- a circulation pump 23 is connected in the middle of the first common pipe 29.
- the output of the circulation pump 23 is preferably variable.
- a pump provided with a pulse width modulation control (PWM control) type DC motor whose output can be changed by a speed command voltage from the control device 50 can be preferably used.
- the second common pipe 40 connects between the heat medium outlet 11 of the heat pump system 1 of the heat pump unit 2 and the third port 24 c of the three-way valve 24.
- the upper pipe 41 connects between the first port 24 a of the three-way valve 24 and the first water inlet 27 of the heat storage tank 22.
- the circulation pump 23 is connected in the middle of the first common pipe 29.
- the circulation pump 23 may be connected in the middle of the second common pipe 40.
- the circulation pump 23 may be built in the heat pump unit 2.
- the circulation flow rate of the heat medium may be changed by providing a plurality of circulation pumps 23 for circulating a heat medium such as water and changing the number of circulating pumps 23 to be driven.
- the hot water supply / heating system 100 can perform a heating operation in which the temperature of indoor air is increased by supplying hot water heated by the heat pump system 1 of the heat pump unit 2 to the indoor heating device 90.
- the indoor heating device 90 for example, at least one of a floor heating panel installed under the floor, a radiator or panel heater installed on the indoor wall surface, and a fan convector can be used.
- the fan convector includes a blower for circulating indoor air and a heat exchanger that exchanges heat between a heated liquid such as water and room air, and performs heating by forced convection.
- a plurality of indoor heating devices 90 may be provided.
- the connection method in the case of providing the plurality of indoor heating devices 90 may be any of a combination of series, parallel, series and parallel. When providing the some indoor heating apparatus 90, those types may be the same and may differ.
- the heat storage tank 22 and the room heating device 90 are connected via the forward pipe 42 and the return pipe 43.
- the forward pipe 42 connects between the second port 24 b of the three-way valve 24 and the water inlet of the indoor heating device 90.
- the return pipe 43 connects between the water outlet of the indoor heating device 90 and the upstream end of the first common pipe 29.
- the control device 50 and the terminal device 60 are connected to be able to communicate with each other.
- the user can input commands related to the operation of the hot water supply and heating system 100, changes in set values, and the like from the terminal device 60.
- the control device 50 includes a storage unit including a ROM (Read Only Memory), a RAM (Random Access Memory), and a nonvolatile memory, and a CPU (Central Processing Unit) that executes arithmetic processing based on a program stored in the storage unit. ) And an input / output port for inputting / outputting an external signal to / from the CPU.
- Actuators and sensors included in the hot water supply and heating system 100 including the heat pump system 1 are electrically connected to the control device 50.
- the control device 50 controls the operation of the hot water supply and heating system 100 including the heat pump system 1 based on the detection values of the sensors, the signal from the terminal device 60, and the like.
- the terminal device 60 is equipped with a display unit that displays information such as the state of the hot water / heating system 100, an operation unit such as a switch operated by a user, a speaker, a microphone, and the like.
- a plurality of temperature sensors may be attached to the surface of the heat storage tank 22 at intervals in the vertical direction.
- the control device 50 can calculate the amount of stored hot water, the amount of stored heat, the amount of remaining hot water, etc. in the heat storage tank 22 by detecting the temperature distribution in the vertical direction in the heat storage tank 22 using these temperature sensors.
- the second common pipe 40 may be provided with a temperature sensor (not shown) that detects the temperature of water flowing out from the heat medium outlet 11 of the heat pump system 1 (hereinafter referred to as “heat pump outlet temperature”).
- a temperature sensor (not shown) that detects the temperature of water flowing into the heat medium inlet 10 of the heat pump system 1 (hereinafter referred to as “heat pump inlet temperature”) may be attached to the first common pipe 29.
- the heat storage operation of the hot water supply / heating system 100 will be described.
- the three-way valve 24 is controlled to a state in which the third port 24c communicates with the first port 24a and the second port 24b is shut off, and the heat pump system 1 and the circulation pump 23 are operated.
- the low-temperature water in the lower part of the heat storage tank 22 is sent to the heat pump unit 2 through the first water outlet 26, the lower pipe 28, and the first common pipe 29.
- the water which became high temperature by being heated by the heat pump system 1 of the heat pump unit 2 is the second common pipe 40, the third port 24c of the three-way valve 24, the first port 24a, the upper pipe 41, and the first It passes through the water inlet 27 and flows into the upper part of the heat storage tank 22.
- the water circulates as described above, whereby high-temperature water is stored in the heat storage tank 22 from the top to the bottom, and the amount of heat stored in the heat storage tank 22 increases.
- the above-described water circulation circuit during the heat storage operation is referred to as a “heat storage circuit”.
- the control device 50 may automatically start the heat storage operation when the remaining hot water amount or the heat storage amount in the heat storage tank 22 is equal to or lower than a preset low level. When the amount of stored hot water and the amount of heat stored in the heat storage tank 22 increase due to the heat storage operation and reach a preset high level, the control device 50 may automatically end the heat storage operation.
- the heating operation of the hot water supply / heating system 100 will be described.
- the three-way valve 24 is controlled to a state in which the third port 24c is communicated with the second port 24b and the first port 24a is shut off, and the heat pump system 1 and the circulation pump 23 are operated.
- water heated by the heat pump system 1 of the heat pump unit 2 passes through the second common pipe 40, the third port 24c of the three-way valve 24, the second port 24b, and the forward pipe 42 and is sent to the indoor heating device 90. It is done. While this water passes through the indoor heating device 90, the temperature is lowered by heat being taken away by the indoor air or the floor.
- the water whose temperature has decreased is returned to the heat pump unit 2 through the return pipe 43 and the first common pipe 29.
- the water returned to the heat pump unit 2 is reheated and recirculated.
- the above-described water circulation circuit during heating operation is referred to as a “heating circuit”.
- the heat storage circuit and the heating circuit can be switched by the three-way valve 24.
- an indoor remote controller (not shown) with a built-in room temperature sensor may be arranged.
- the indoor remote controller and the control device 50 may be configured to be able to communicate wirelessly.
- the indoor remote controller may transmit information on the room temperature detected by the room temperature sensor to the control device 50.
- the controller 50 may end the heating operation when the room temperature transmitted from the indoor remote controller reaches a preset target temperature during the heating operation.
- the user may instruct the control device 50 to start and end the heating operation by operating the indoor remote controller.
- the control device 50 performs control so that the heat pump outlet temperature matches the target value.
- the control device 50 can control the heat pump outlet temperature by adjusting the output of the circulation pump 23.
- the control device 50 can control the heat pump outlet temperature to match the target value by increasing the output of the circulation pump 23 and increasing the water circulation flow rate.
- the control device 50 can control the heat pump outlet temperature to match the target value by lowering the output of the circulation pump 23 and lowering the circulation flow rate of water.
- the control device 50 may control the heat pump outlet temperature by adjusting the operation of the refrigerant circuit of the heat pump system 1.
- the control device 50 sets the target value of the heat pump outlet temperature to the first target temperature.
- the control device 50 sets the target value of the heat pump outlet temperature to a second target temperature that is lower than the first target temperature.
- the first target temperature is preferably a temperature included in a range of about 65 ° C. to 90 ° C., for example.
- the second target temperature is desirably a temperature included in a range of about 30 ° C. to 50 ° C., for example.
- FIG. 3 is a diagram showing a state of the first mode of the heat pump system 1.
- the four-way valve 12 is controlled to a first state in which the first port 12a and the second port 12b are communicated and the third port 12c and the fourth port 12d are communicated.
- FIG. 4 is a Ph diagram, that is, a Mollier diagram, of the refrigerant circuit of the heat pump system 1 in the first mode (heat storage operation).
- the curves in FIG. 4 are a saturated vapor line and a saturated liquid line of carbon dioxide that is a refrigerant. 4 correspond to the refrigerant pressure and specific enthalpy at positions A to H in FIG.
- the compressor 32 of the compressor 3 the refrigerant is compressed to a supercritical state (A ⁇ B).
- the high-pressure refrigerant is discharged into the first pipe 35, cooled by the first heat exchanger 4, and then returned into the sealed container 31 (C).
- the high-pressure refrigerant is heated by cooling the electric motor 33 in the sealed container 31 and then discharged from the third pipe 37 (D).
- This high-pressure refrigerant is cooled by the second heat exchanger 5 (E).
- the high-pressure refrigerant is further cooled by the high-low pressure heat exchanger 9 (F).
- the high-pressure refrigerant is decompressed by the expansion valve 6 and becomes a low-pressure refrigerant (G).
- This low-pressure refrigerant evaporates in the evaporator 7 (H).
- the low-pressure refrigerant is heated by the high-low pressure heat exchanger 9 (A).
- FIG. 5 is a graph showing changes in the refrigerant and water temperatures of the heat pump system 1 in the first mode (heat storage operation).
- the horizontal axis of FIG. 5 is the specific enthalpy of the refrigerant.
- B to E in FIG. 5 correspond to the temperature and specific enthalpy of the refrigerant at positions B to E in FIG.
- FIG. In the first mode the refrigerant and water flows countercurrently in the second heat exchanger 5 and the first heat exchanger 4.
- the heat storage amount of the heat storage tank 22 can be increased efficiently.
- it since it is necessary to increase the difference between the heat pump outlet temperature and the heat pump inlet temperature, it is necessary to reduce the flow rate of water. It can suppress that the flow rate of the water in the 1st heat exchanger 4 and the 2nd heat exchanger 5 becomes low by setting it as the 1st mode at the time of heat storage operation. As a result, it is possible to suppress a decrease in water-side heat transfer coefficient in the first heat exchanger 4 and the second heat exchanger 5.
- the refrigerant and water flows in the first heat exchanger 4 and the second heat exchanger 5 are both counter-current, and even if the difference between the heat pump outlet temperature and the heat pump inlet temperature is large, Heat can be exchanged efficiently. For this reason, the heat pump outlet temperature can be increased more efficiently.
- Refrigerant pressure and temperature are highest in the first pipe 35 (B).
- the temperature of the refrigerant (D) in the second pipe 36 is lower than the temperature of the refrigerant (B) in the first pipe 35.
- the heat medium passage 5b of the second heat exchanger 5 and the heat medium passage 4b of the first heat exchanger 4 are arranged in series, and the refrigerant of the second heat exchanger 5 and the first heat exchanger 4 is used.
- the electric motor 33 can be cooled by flowing the refrigerant in the order of the compression unit 32, the first heat exchanger 4, the electric motor 33, and the second heat exchanger 5. As a result, since the efficiency of the electric motor 33 can be increased, the heat pump outlet temperature can be increased more efficiently.
- FIG. 6 is a diagram illustrating a state of the second mode of the heat pump system 1.
- the four-way valve 12 is controlled to a second state in which the first port 12a and the fourth port 12d are communicated and the second port 12b and the third port 12c are communicated.
- the water flowing in from the heat medium inlet 10 is divided into a flow going to the third passage 16 and a flow going on the fifth passage 20 as it is at the branching portion 17.
- the water in the third passage 16 flows into the heat medium passage 4 b of the first heat exchanger 4 through the four-way valve 12 and the second passage 15.
- the water in the fifth passage 20 flows into the heat medium passage 5 b of the second heat exchanger 5.
- the water that has passed through the heat medium passage 4 b of the first heat exchanger 4 and the water that has passed through the heat medium passage 5 b of the second heat exchanger 5 merge at the junction 19 of the sixth passage 21.
- the merged water flows out from the heat medium outlet 11 through the fourth passage 18, the check valve 13, the four-way valve 12, and the first passage 14.
- Such a flow of the heat medium corresponds to the second mode. Hot water heated using the second mode flows into the indoor heating device 90.
- the second mode water flows in parallel through the first heat exchanger 4 and the second heat exchanger 5.
- FIG. 7 is a Ph diagram, that is, a Mollier diagram, of the refrigerant circuit of the heat pump system 1 in the second mode (heating operation).
- the curves in FIG. 7 are saturated vapor lines and saturated liquid lines of carbon dioxide, which is a refrigerant. 7 corresponds to the refrigerant pressure and specific enthalpy at positions A to H in FIG.
- the operation of the refrigerant circuit in the second mode is basically the same as the operation of the refrigerant circuit in the first mode, but differs in the following points.
- the compression part discharge pressure in the second mode is lower than the compression part discharge pressure in the first mode.
- the specific enthalpy of the refrigerant (E) exiting from the second heat exchanger 5 in the second mode is higher than that in the first mode.
- FIG. 8 is a graph showing changes in the refrigerant and water temperatures of the heat pump system 1 in the second mode (heating operation).
- the horizontal axis of FIG. 8 is the specific enthalpy of the refrigerant. 8 correspond to the refrigerant temperature and specific enthalpy at positions B to E in FIG.
- the refrigerant and water flows in the second heat exchanger 5 are countercurrent.
- the temperature of the water exiting from the second heat exchanger 5 is higher than the temperature of the refrigerant (E) exiting from the second heat exchanger 5.
- the refrigerant and water flows in the first heat exchanger 4 are parallel.
- the temperature of the water exiting from the first heat exchanger 4 is lower than the temperature of the refrigerant (C) exiting from the first heat exchanger 4.
- the difference between the heat pump outlet temperature and the heat pump inlet temperature is small, it is necessary to increase the water flow rate.
- an increase in water-side pressure loss in the first heat exchanger 4 and the second heat exchanger 5 can be suppressed, and the water flow rate can be sufficiently increased.
- the flow path cross-sectional areas of the heat medium passage 4b of the first heat exchanger 4 and the heat medium passage 5b of the second heat exchanger 5 are designed to be small. There is. Even in such a case, an increase in pressure loss during the heating operation can be suppressed, and the water flow rate can be sufficiently increased.
- the cooling amount of the refrigerant in the first heat exchanger 4 is too large because the refrigerant and water flows in the first heat exchanger 4 are in parallel flow in the second mode. Can be prevented.
- Refrigerating machine oil is discharged from the compressor 32 of the compressor 3 together with the refrigerant.
- Refrigerating machine oil flows through the heat medium passage 4b and the second pipe 36 of the first heat exchanger 4 together with the refrigerant.
- the refrigerant and the refrigerating machine oil flow into the sealed container 31 from the second pipe 36 and are separated from each other. If the refrigerant is cooled too much in the first heat exchanger 4, the refrigerant flowing into the internal space 38 of the compressor 3 becomes low temperature and high density.
- the temperature of the water that enters the first heat exchanger 4 is lower than that in the first mode. Therefore, in the second mode, the temperature of the refrigerant coming out of the first heat exchanger 4 tends to decrease.
- the separation efficiency of the refrigerating machine oil can be suppressed. As a result, an increase in the oil circulation rate of the refrigeration cycle can be suppressed and the reliability of the refrigeration cycle can be increased.
- the temperature difference between the refrigerant and water is larger than that in the second heat exchanger 5.
- the amount of heat exchange increases, the temperature of the water exiting the first heat exchanger 4 increases, and the temperature of the refrigerant exiting the first heat exchanger 4 increases. Lower. Since the refrigerant cooled by the first heat exchanger 4 flows into the second heat exchanger 5, when the temperature of the refrigerant that exits the first heat exchanger 4 decreases, the temperature of the water that exits the second heat exchanger 5 decreases. Lower.
- the refrigerant and water in the second heat exchanger 5 are counter-current both in the first mode and in the second mode.
- coolant which comes out of the 2nd heat exchanger 5 can be made low, and COP can be made high.
- the temperature difference between the refrigerant and water is smaller than that in the first heat exchanger 4. Therefore, it is desirable to increase the heat exchange amount of the second heat exchanger 5 by increasing the heat transfer area of the second heat exchanger 5 compared to the heat transfer area of the first heat exchanger 4.
- FIG. 9 is a flowchart showing the control operation of the control device 50 according to the first embodiment.
- the control device 50 determines whether the operation state of the hot water supply / heating system 100 is a heat storage operation or a heating operation (step S1). When the operation state of the hot water supply and heating system 100 is the heat storage operation, the control device 50 proceeds to step S2. In step S2, the control device 50 selects the first mode and sets the flow of the heat medium to the first mode. On the other hand, when the operation state of the hot water supply / heating system 100 is the heating operation, the control device 50 proceeds to step S3. In step S3, the control device 50 selects the second mode and sets the flow of the heat medium to the second mode.
- control device 50 that controls switching between the first mode and the second mode according to the operating state
- the first mode and the second mode are automatically switched according to the operating state according to the above flowchart. And appropriate operation can be ensured.
- a switching device that switches between the first mode and the second mode is configured by using one four-way valve 12 and one check valve 13.
- the check valve 13 is automatically switched between open and closed depending on the flow and pressure difference. Therefore, the actuator that needs to be operated in the switching device is only one four-way valve 12. For this reason, switching between the first mode and the second mode can be easily performed.
- FIG. 10 is a configuration diagram showing the heat pump system 1 according to the second embodiment of the present invention.
- the heat pump system 1 of the second embodiment shown in FIG. 10 includes a three-way valve 44, a temperature sensor 45, and a temperature sensor 46 in addition to the configuration of the first embodiment.
- the three-way valve 44 has an inlet 44a, a first outlet 44b, and a second outlet 44c.
- the inlet 44 a communicates with the heat medium inlet 10.
- the first outlet 44 b communicates with the heat medium passage 5 b of the second heat exchanger 5 through the fifth passage 20.
- the second outlet 44 c communicates with the third passage 16.
- the three-way valve 44 can change the ratio of the cross-sectional area of the first outlet 44b and the cross-sectional area of the second outlet 44c. In the second mode, the flow rate of the water in the first heat exchanger 4 and the second heat exchanger are changed by changing the ratio of the channel cross-sectional area of the first outlet 44b and the channel cross-sectional area of the second outlet 44c.
- the ratio of the water flow rate of 5 can be changed.
- the three-way valve 44 corresponds to an adjustment device that adjusts the ratio of the flow rate of water in the first heat exchanger 4 and the flow rate of water in the second heat exchanger 5 when in the second mode. .
- the temperature sensor 45 detects the temperature of water coming out of the first heat exchanger 4 in the second mode.
- the temperature sensor 46 detects the temperature of the water leaving the second heat exchanger 5 in the second mode.
- the control device 50 causes the first outlet 44b of the three-way valve 44 so that the temperature detected by the temperature sensor 45 is equal to or close to the temperature detected by the temperature sensor 46. It is desirable to adjust the ratio of the channel cross-sectional area of the second outlet 44c to the channel cross-sectional area of the second outlet 44c.
- the operating conditions such as the outside air temperature and the heat pump inlet temperature change, so that the temperature of the water coming out of the first heat exchanger 4 even if the refrigerant pressure and temperature change,
- the state where the temperature of the water exiting from the second heat exchanger 5 is equal or close can be maintained. Therefore, it is possible to more reliably suppress the loss of mixing water of different temperatures and to operate more efficiently.
- FIG. 11 is a diagram illustrating a state of the first mode of the heat pump system 1 according to the third embodiment of the present invention.
- FIG. 12 is a diagram illustrating a state of the second mode of the heat pump system 1 according to the third embodiment of the present invention.
- the heat pump system 1 of the third embodiment shown in these drawings instead of the four-way valve 12 and the check valve 13 of the first embodiment, three two-way valves 47 and two-way valves 48 that open and close the flow path are shown. , And a two-way valve 49.
- the first passage 14 connects between one port of the two-way valve 47 and the heat medium outlet 11.
- One end of the second passage 15 is connected to the heat medium passage 4 b of the first heat exchanger 4.
- One end of the third passage 16 is connected to the branch portion 17.
- the other end of the second passage 15 and the other end of the third passage 16 are connected together and connected to the other port of the two-way valve 47.
- a two-way valve 48 is connected in the middle of the third passage 16.
- the fourth passage 18 connects the junction 19 and the middle of the first passage 14.
- a two-way valve 49 is connected in the middle of the fourth passage 18.
- the first mode is set by opening the two-way valve 47 and closing the two-way valve 48 and the two-way valve 49.
- the second mode is set.
- the fifth passage 20 and the sixth passage 21 correspond to a switching device that switches the flow of the heat medium between the first mode and the second mode. According to the third embodiment, since the first mode and the second mode can be switched by the switching device using a plurality of two-way valves having a simple structure, the cost can be reduced.
- the two-way valve 48 is preferably a valve whose opening degree can be changed.
- the ratio of the flow rate of the water in the first heat exchanger 4 and the flow rate of the water in the second heat exchanger 5 can be changed by changing the opening of the two-way valve 48. If the opening degree of the two-way valve 48 is increased, the flow rate of water in the first heat exchanger 4 is increased, and if the opening degree of the two-way valve 48 is decreased, the flow rate of water in the first heat exchanger 4 is decreased.
- the two-way valve 48 corresponds to an adjustment device that adjusts the ratio of the flow rate of water in the first heat exchanger 4 and the flow rate of water in the second heat exchanger 5 in the second mode.
- the control device 50 sets the opening of the two-way valve 48 so that the temperature detected by the temperature sensor 45 and the temperature detected by the temperature sensor 46 are equal or close to each other. It is desirable to adjust. Thereby, the same effect as in the second embodiment can be obtained.
- the refrigerant in the present invention is not limited to carbon dioxide.
- the present invention is also applicable to a heat pump system using a compressor that further compresses the refrigerant sucked through the second pipe and discharges it to the third pipe.
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Abstract
Description
図1は、本発明の実施の形態1のヒートポンプシステムを示す構成図である。図1に示すように、本実施の形態1のヒートポンプシステム1は、圧縮機3、第一熱交換器4、第二熱交換器5、膨張弁6、及び蒸発器7を含む冷媒回路を備える。第一熱交換器4及び第二熱交換器5は、冷媒の熱で熱媒体を加熱する熱交換器である。第一熱交換器4は、冷媒通路4a及び熱媒体通路4bを有する。冷媒通路4aを流れる冷媒と、熱媒体通路4bを流れる熱媒体との間で熱交換する。第二熱交換器5は、冷媒通路5a及び熱媒体通路5bを有する。冷媒通路5aを流れる冷媒と、熱媒体通路5bを流れる熱媒体との間で熱交換する。本実施の形態1では、熱媒体が水である場合について説明するが、本発明における熱媒体は、例えばブライン、不凍液など、水以外の流体でも良い。
蓄熱運転のとき、ヒートポンプシステム1は、熱媒体の流れを第一モードにする。以下、第一モード及び蓄熱運転について説明する。図3は、ヒートポンプシステム1の第一モードの状態を示す図である。図3に示すように、四方弁12は、第一ポート12aと第二ポート12bとを連通させ、且つ第三ポート12cと第四ポート12dとを連通させる第一状態に制御される。熱媒体入口10から流入した水は、第五通路20、第二熱交換器5の熱媒体通路5b、第六通路21、第一熱交換器4の熱媒体通路4b、第二通路15、四方弁12、第一通路14をこの順に経由し、熱媒体出口11から流出する。このような熱媒体の流れが第一モードに相当する。第一モードを用いて加熱された湯が蓄熱槽22に貯められる。第三通路16と第四通路18とは、四方弁12を介して連通する。第二熱交換器5を通過する水の圧力損失により、第三通路16に比べて第四通路18の方が圧力が低い。このことと、第四通路18に逆止弁13があることから、第三通路16及び第四通路18には水は流れない。
暖房運転のとき、ヒートポンプシステム1は、熱媒体の流れを第二モードにする。以下、第二モード及び暖房運転について説明する。図6は、ヒートポンプシステム1の第二モードの状態を示す図である。図6に示すように、四方弁12は、第一ポート12aと第四ポート12dとを連通させ、且つ第二ポート12bと第三ポート12cとを連通させる第二状態に制御される。熱媒体入口10から流入した水は、分岐部17において、第三通路16へ行く流れと、そのまま第五通路20を進む流れとに分かれる。第三通路16の水は、四方弁12及び第二通路15を経て、第一熱交換器4の熱媒体通路4bに流入する。第五通路20の水は、第二熱交換器5の熱媒体通路5bに流入する。第一熱交換器4の熱媒体通路4bを通過した水と、第二熱交換器5の熱媒体通路5bを通過した水とが第六通路21の合流部19で合流する。この合流した水は、第四通路18、逆止弁13、四方弁12、第一通路14を経て、熱媒体出口11から流出する。このような熱媒体の流れが第二モードに相当する。第二モードを用いて加熱された温水が室内暖房機器90に流入する。このようにして、第二モードでは、第一熱交換器4と第二熱交換器5とに水が並列に流れる。
次に、図10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10は、本発明の実施の形態2のヒートポンプシステム1を示す構成図である。図10に示す本実施の形態2のヒートポンプシステム1は、実施の形態1の構成に加えて、三方弁44、温度センサ45、及び温度センサ46を備える。
次に、図11及び図12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及び2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3のヒートポンプシステム1の第一モードの状態を示す図である。図12は、本発明の実施の形態3のヒートポンプシステム1の第二モードの状態を示す図である。これらの図に示す本実施の形態3のヒートポンプシステム1は、実施の形態1の四方弁12及び逆止弁13に代えて、流路を開閉する3個の二方弁47、二方弁48、及び二方弁49を備える。
Claims (10)
- 冷媒を圧縮する圧縮機と、
前記圧縮機で圧縮された前記冷媒と、熱媒体との間で熱を交換する第一熱交換器と、
前記圧縮機で圧縮された前記冷媒と、前記熱媒体との間で熱を交換する第二熱交換器と、
前記圧縮機から前記第一熱交換器へ供給される前記冷媒が通る第一管と、
前記第一熱交換器から前記圧縮機へ戻る前記冷媒が通る第二管と、
前記第一熱交換器から戻った後に前記圧縮機から前記第二熱交換器へ供給される冷媒が通る第三管と、
前記熱媒体の流れを第一モードと第二モードとに切り替える切替装置と、
を備え、
前記第一モードで前記熱媒体は前記第一熱交換器及び前記第二熱交換器を直列に流れ、前記第二モードで前記熱媒体は前記第一熱交換器及び前記第二熱交換器を並列に流れるヒートポンプシステム。 - 前記圧縮機は、前記冷媒が圧縮される圧縮部と、前記圧縮部を駆動する電動機と、前記圧縮部及び前記電動機を収納する密閉容器とを備え、
前記圧縮部で圧縮された冷媒は、前記密閉容器の内部空間へ放出されることなく、前記第一管を通って前記第一熱交換器へ供給され、
前記第二管を通過した冷媒は、前記密閉容器の内部空間へ放出され、
前記密閉容器の内部空間の冷媒は、前記第三管を通って前記第二熱交換器へ供給される請求項1に記載のヒートポンプシステム。 - 前記第二モードのとき、前記第一熱交換器の冷媒及び熱媒体の流れが並流になり、前記第二熱交換器の冷媒及び熱媒体の流れが向流になる請求項1または請求項2に記載のヒートポンプシステム。
- 前記第一モードのとき、前記第一熱交換器及び前記第二熱交換器の冷媒及び熱媒体の流れが向流になる請求項1から請求項3のいずれか一項に記載のヒートポンプシステム。
- 前記第二モードのときに前記第一熱交換器の熱媒体の流量と前記第二熱交換器の熱媒体の流量との比を調整する調整装置を備える請求項1から請求項4のいずれか一項に記載のヒートポンプシステム。
- 前記切替装置は、第一ポート、第二ポート、第三ポート及び第四ポートを有する四方弁と、逆流を阻止する逆止弁とを備え、
前記四方弁は、前記第一ポートと前記第二ポートとを連通させ、且つ前記第三ポートと前記第四ポートとを連通させる第一状態と、前記第一ポートと前記第四ポートとを連通させ、且つ前記第二ポートと前記第三ポートとを連通させる第二状態とを切り替える請求項1から請求項5のいずれか一項に記載のヒートポンプシステム。 - 前記切替装置は、
前記ヒートポンプシステムの熱媒体出口と、前記第一ポートとの間をつなぐ第一通路と、
前記第一熱交換器の熱媒体通路と、前記第二ポートとの間をつなぐ第二通路と、
前記第二モードのときに加熱前の熱媒体が分岐する分岐部と、前記第三ポートとの間をつなぐ第三通路と、
前記第二モードのときに前記第一熱交換器で加熱された熱媒体と前記第二熱交換器で加熱された熱媒体とが合流する合流部と、前記第四ポートとの間をつなぐ第四通路と、
をさらに備え、
前記逆止弁は、前記第四通路の逆流を阻止する請求項6に記載のヒートポンプシステム。 - 前記切替装置は、流路を開閉する複数の二方弁を備える請求項1から請求項5のいずれか一項に記載のヒートポンプシステム。
- 前記第一モードと前記第二モードとの切り替えを制御する制御装置を備える請求項1から請求項8のいずれか一項に記載のヒートポンプシステム。
- 前記制御装置は、蓄熱槽に蓄熱する蓄熱運転のときには前記第一モードを選択し、室内暖房機器に前記熱媒体を流す暖房運転のときには前記第二モードを選択する請求項9に記載のヒートポンプシステム。
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