EP3594588A1 - Geothermal heat pump device - Google Patents
Geothermal heat pump device Download PDFInfo
- Publication number
- EP3594588A1 EP3594588A1 EP17899277.2A EP17899277A EP3594588A1 EP 3594588 A1 EP3594588 A1 EP 3594588A1 EP 17899277 A EP17899277 A EP 17899277A EP 3594588 A1 EP3594588 A1 EP 3594588A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat
- heat exchanger
- refrigerant
- water
- evaporation capacity
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 109
- 239000003507 refrigerant Substances 0.000 claims abstract description 55
- 230000008020 evaporation Effects 0.000 claims abstract description 43
- 238000001704 evaporation Methods 0.000 claims abstract description 43
- 238000010438 heat treatment Methods 0.000 claims abstract description 32
- 239000012267 brine Substances 0.000 claims abstract description 24
- 238000004378 air conditioning Methods 0.000 claims abstract description 9
- 230000001186 cumulative effect Effects 0.000 claims description 20
- 238000010586 diagram Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 4
- 238000001514 detection method Methods 0.000 description 4
- 230000008014 freezing Effects 0.000 description 4
- 238000007710 freezing Methods 0.000 description 4
- 238000005057 refrigeration Methods 0.000 description 4
- DNIAPMSPPWPWGF-UHFFFAOYSA-N Propylene glycol Chemical compound CC(O)CO DNIAPMSPPWPWGF-UHFFFAOYSA-N 0.000 description 3
- 230000015556 catabolic process Effects 0.000 description 3
- 239000007789 gas Substances 0.000 description 3
- 238000005259 measurement Methods 0.000 description 3
- HPALAKNZSZLMCH-UHFFFAOYSA-M sodium;chloride;hydrate Chemical compound O.[Na+].[Cl-] HPALAKNZSZLMCH-UHFFFAOYSA-M 0.000 description 3
- 239000002689 soil Substances 0.000 description 3
- 229910002092 carbon dioxide Inorganic materials 0.000 description 2
- FXRLMCRCYDHQFW-UHFFFAOYSA-N 2,3,3,3-tetrafluoropropene Chemical compound FC(=C)C(F)(F)F FXRLMCRCYDHQFW-UHFFFAOYSA-N 0.000 description 1
- 239000004215 Carbon black (E152) Substances 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 230000006870 function Effects 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 239000008236 heating water Substances 0.000 description 1
- 229910052734 helium Inorganic materials 0.000 description 1
- 239000001307 helium Substances 0.000 description 1
- SWQJXJOGLNCZEY-UHFFFAOYSA-N helium atom Chemical compound [He] SWQJXJOGLNCZEY-UHFFFAOYSA-N 0.000 description 1
- 229930195733 hydrocarbon Natural products 0.000 description 1
- 150000002430 hydrocarbons Chemical class 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000012212 insulator Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 230000000153 supplemental effect Effects 0.000 description 1
- 239000008400 supply water Substances 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
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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
- F24D17/00—Domestic hot-water supply systems
- F24D17/02—Domestic hot-water supply systems using heat pumps
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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
- 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
- F24D19/1066—Arrangement or mounting of control or safety devices for water heating systems for the combination of central heating and domestic hot water
- F24D19/1072—Arrangement or mounting of control or safety devices for water heating systems for the combination of central heating and domestic hot water 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
- F24H15/00—Control of fluid heaters
- F24H15/20—Control of fluid heaters characterised by control inputs
- F24H15/238—Flow rate
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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
- F24H15/30—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
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
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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
- F25B27/00—Machines, plants or systems, using particular sources of energy
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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
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
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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
- F25B30/00—Heat pumps
- F25B30/06—Heat pumps characterised by the source of low potential heat
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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
- F25B49/022—Compressor control arrangements
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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
- F24D2200/00—Heat sources or energy sources
- F24D2200/08—Electric heater
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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
- F24D2200/00—Heat sources or energy sources
- F24D2200/11—Geothermal energy
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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
- F24D2200/00—Heat sources or energy sources
- F24D2200/12—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
- F24H15/00—Control of fluid heaters
- F24H15/20—Control of fluid heaters characterised by control inputs
- F24H15/212—Temperature of the water
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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
- F24H15/227—Temperature of the refrigerant in heat pump cycles
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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
- F24H15/281—Input from user
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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
- F24H15/30—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
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/002—Compression machines, plants or systems with reversible cycle not otherwise provided for geothermal
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/003—Indoor unit with water as a heat sink or heat source
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/004—Outdoor unit with water as a heat sink or heat source
Definitions
- the present invention relates to a geothermal heat pump device that uses the ground as a heat source, causes a heat medium to circulate through an underground heat exchanger, collects heat using a heat pump, and supplies warm water to a load side.
- a geothermal heat pump system that uses the ground and lakes as heat sources, causes a heat medium to circulate through an underground heat exchanger, collects and releases heat using a heat pump, and supplies warm water for heating or household use to a load side is a device using renewable energy.
- the geothermal heat pump system is regarded as a highly efficient device with low running cost and is capable of reducing the emission of CO2, and hence has attracted more attention recently.
- an outlet temperature of heat medium water is measured using a temperature sensor, a soil temperature is calculated from the outlet temperature of the heat medium water by a controller in which a program or data that has been input in advance is installed, and the limit values for heat collection and release are set. Furthermore, the limit values are determined also on the basis of the soil temperature of the previous year.
- a technology for grasping an operation status and geothermal heat characteristics as needed, estimating operation and performance on the basis of the operation status and geothermal heat characteristics, and adjusting system operating time and the amount of heat to be collected or released is disclosed (for example, see Patent Literature 2).
- the present invention has been made to solve the above-described problem, and an object thereof is to set a limit value for heat collection from underground by using a simple method using, for example, detection data obtained from a geothermal heat pump device and specifications of a geothermal heat pump device, and provide pleasant air conditioning and hot water supply that meet users' requests without the freezing and breakdown of an underground heat exchanger.
- a geothermal heat pump device includes a heat pump heat source unit having a refrigerant circuit in which a compressor, a water-refrigerant heat exchanger, an expansion valve, and a refrigerant-brine heat exchanger in which a heat medium from an underground heat exchanger buried underground is connected such that the heat medium circulates are serially connected, a warm-water heater unit configured to supply warm water heated at the water-refrigerant heat exchanger to heating and air conditioning and hot water supply such that it circulates, and a controller configured to control an upper limit of an operation frequency of the compressor based on a heat collection limit value set by comparing a unit necessary evaporation capacity calculated from information on the underground heat exchanger with a unit actual evaporation capacity calculated from inlet and outlet temperatures and a circulation flow rate of the heat medium circulating through the refrigerant-brine heat exchanger.
- a geothermal heat pump device of an embodiment of the present invention includes a heat pump heat source unit having a refrigerant circuit in which a compressor, a water-refrigerant heat exchanger, an expansion valve, and a refrigerant-brine heat exchanger in which a heat medium from an underground heat exchanger buried underground is connected such that the heat medium circulates are serially connected, a warm-water heater unit configured to supply warm water heated at the water-refrigerant heat exchanger to heating and air conditioning and hot water supply such that the warm water circulates, a controller configured to control an upper limit of an operation frequency of the compressor based on a heat collection limit value set by comparing a unit necessary evaporation capacity calculated from information on the underground heat exchanger with a unit actual evaporation capacity calculated from inlet and outlet temperatures and a circulation flow rate of the heat medium circulating through the refrigerant-brine heat exchanger.
- An effect is achieved that the limit value for heat collection from underground is set by using a simple method using, for example, detection data obtained from the geothermal heat pump device and specifications of the geothermal heat pump device, and pleasant air conditioning and hot water supply that meet users' requests can be provided without the freezing and breakdown of the underground heat exchanger.
- Fig. 1 is a circuit diagram illustrating a schematic configuration of a geothermal heat pump device according to Embodiment 1 of the present invention
- Fig. 2 is a block diagram illustrating an electrical configuration of a controller of the geothermal heat pump device. The overall configuration will be described on the basis of Figs. 1 and 2 .
- a geothermal heat pump device 15 of Fig. 1 is a heat-pump hot water system using geothermal heat.
- the heat-pump hot water system causes a heat medium to circulate through an underground heat exchanger, collects heat using a heat pump, and supplies warm water for heating or living to a load side.
- the geothermal heat pump device 15 includes a heat pump heat source unit 22 and a warm-water heater unit 23, the heat pump heat source unit 22 performing a heat pump cycle (refrigeration cycle) operation using a refrigerant circuit, the warm-water heater unit 23 having a function of supplying warm water for heating to an indoor space and including devices, such as a heated-water tank 12 that stores warm water.
- An underground heat exchanger 18 or 19 buried underground is connected to the heat pump heat source unit 22, a heat medium is caused to circulate, and heat is collected using the heat pump.
- the geothermal heat pump device 15 of the present invention is a heat-pump air-conditioning hot water system that exchanges heat between refrigerant inside the refrigerant circuit of the heat pump heat source unit 22, which performs the heat pump cycle (refrigeration cycle) operation, and a heat medium (for example, such as brine) of a circulation circuit using the underground heat exchanger, exchanges heat between the refrigerant inside the refrigerant circuit of the heat pump heat source unit 22 and water in a water circuit connected to the warm-water heater unit 23, performs a heating operation by supplying, through the circulation of this water, warm water for heating to an indoor space, and that can further perform a hot-water supply operation by heating water stored in the heated-water tank 12.
- a heat medium for example, such as brine
- the underground heat exchangers 18 and 19 will be described.
- a borehole system in which a 100-m to 150-m vertical hole is bored in the ground and a heat exchange pipe is inserted therein
- a horizontal loop system in which a heat exchange pipe is horizontally buried into a shallow ground (1 m to 2.5 m) and heat is collected.
- the underground heat exchanger 18 is used to show the borehole system
- the underground heat exchanger 19 is used to show the horizontal loop system.
- Examples of the refrigerant used in the refrigeration cycle of the heat pump heat source unit 22 include a HFO single refrigerant such as HFO-1234yf, a mixed refrigerant containing a HFO refrigerant and a HFC refrigerant such as R32, and natural refrigerants such as hydrocarbon, helium, and carbon dioxide.
- a HFO single refrigerant such as HFO-1234yf
- a mixed refrigerant containing a HFO refrigerant and a HFC refrigerant such as R32
- natural refrigerants such as hydrocarbon, helium, and carbon dioxide.
- the heat pump heat source unit 22 is equipped with structural devices of the refrigerant circuit such as a refrigerant-brine heat exchanger (for example, a plate heat exchanger) 4 configured to exchange heat between a ground side heat medium and refrigerant, a water-refrigerant heat exchanger (for example, a plate heat exchanger) 2 configured to exchange heat between water on the warm-water heater side and refrigerant, a compressor 1 configured to compress refrigerant, and an expansion valve 3.
- a refrigerant-brine heat exchanger for example, a plate heat exchanger 4 configured to exchange heat between a ground side heat medium and refrigerant
- a water-refrigerant heat exchanger for example, a plate heat exchanger 2 configured to exchange heat between water on the warm-water heater side and refrigerant
- a compressor 1 configured to compress refrigerant
- the heat pump heat source unit 22 is provided with a heat collection pump 5 for causing the heat medium to circulate through the underground heat exchanger 18, 19, a heat collection flow rate sensor 6 configured to detect flow rate of the heat medium for heat collection, and a heat collection return sensor 7 and a heat collection supply sensor 8 for heat collection control and protection.
- the warm-water heater unit 23 is provided with, in addition to the heated-water tank 12, a pump 9 configured to cause water inside the water circuit to circulate, the water having exchanged heat with refrigerant inside a refrigerant circuit in the water-refrigerant heat exchanger (for example, a plate heat exchanger) 2, an electric heater 10 capable of further complementarily heating warm water heated at the water-refrigerant heat exchanger 2 at the time of heating, a three-way valve 21 serving as a channel switching unit that performs switching of a circulation destination of the water having exchanged heat at the water-refrigerant heat exchanger 2, a warm-water circulation flow rate sensor 14 for water flow rate detection, a controller 16 configured to perform overall operation control, a remote control 17 through which a user can perform a setting operation, and water temperature sensors 11 and 13 used for control and protection for a heating operation and a hot-water supply operation.
- a pump 9 configured to cause water inside the water circuit to circulate, the water having exchanged heat with refrigerant
- the directions of arrows indicate the direction of flow of the refrigerant at the time of heating, the direction of flow of the water, and the direction of the heat medium in the ground.
- the warm water obtained from the heat pump heat source unit 22 reaches the three-way valve 21 via the electric heater 10.
- the three-way valve 21 can switch a circulation destination of the warm water between a water-supply path to an indoor-side air-conditioning radiator and the side where the heated-water tank 12 is provided. Heating can be performed by switching the circulation destination to the indoor side at the three-way valve 21 and causing the warm water to circulate through the indoor radiator.
- the water stored in the heated-water tank 12 can be heated by switching the circulation destination to the tank 12 side at the three-way valve 21 and causing the warm water to circulate through the tank.
- the water whose temperature has been reduced by passing through an indoor space or the heated-water tank 12 returns to the water-refrigerant heat exchanger 2 via the warm-water circulation pump 9 and circulates again.
- the heated-water tank 12 is substantially cylindrically shaped, and at least its outside is composed of, for example, a metal material, such as stainless steel.
- a water supply pipe that supplies water from, for example, a waterworks outside the system is connected to a lower portion of the heated-water tank 12. Water supplied from the water supply pipe flows into and stored in the heated-water tank 12. The water stored in the heated-water tank 12 is heated by performing the heating operation described above, and warm water is generated. In the heated-water tank 12, hot water is stored so as to form temperature layers such that high temperature layers are on the upper side and low temperature layers are on the lower side.
- a hot-water output pipe is connected to an upper portion of the heated-water tank 12 to remove warm water generated in the heated-water tank 12.
- the warm water generated in the heated-water tank 12 is supplied to the outside of a geothermal heat pump system 12 through the hot-water output pipe and is used as, for example, water for domestic use.
- the heated-water tank 12 is covered by a heat insulator to suppress heat dissipation from the stored warm water.
- the compressor 1 is a capacity controllable type whose rotation speed is controlled by an inverter, and provides a high-temperature, high-pressure state by suctioning and compressing refrigerant.
- the expansion valve 3 is an electronic expansion valve whose opening degree is variably controlled.
- the water-refrigerant heat exchanger 2 exchanges heat between water and refrigerant by using, for example, the warm-water circulation pump 9.
- the refrigerant-brine heat exchanger 4 exchanges heat between the heat medium flowing in the underground heat exchanger 18, 19 and refrigerant by using, for example, the heat collection pump 5.
- Fig. 2 is a control block diagram according to Embodiment 1 of the present invention.
- Fig. 2 illustrates a connection configuration of the controller 16 configured to perform various types of measurement control on the geothermal heat pump device 15 of Embodiment 1 and operation information, actuators, and other devices connected to the controller 16.
- the controller 16 of the geothermal heat pump device 15 controls, for example, an operation frequency of the compressor 1 of the heat pump heat source unit 22 and the opening degree of the expansion valve 3 on the basis of measurement information from the temperature sensors 7, 8, 11, and 13 and operation details instructed and set by the user of the geothermal heat pump device 15.
- a high-temperature, high-pressure gas refrigerant discharged from the compressor 1 flows into the water-refrigerant heat exchanger 2 in the refrigerant circuit of the heat pump cycle.
- the gas refrigerant condenses and liquefies while dissipating heat at the water-refrigerant heat exchanger 2 serving as a condenser to become a high-pressure, low-temperature liquid refrigerant. Heat dissipated from the refrigerant is supplied to water on the load side to warm the water.
- the high-pressure, low-temperature refrigerant output from the water-refrigerant heat exchanger 2 flows into the refrigerant-brine heat exchanger 4 serving as an evaporator, absorbs heat and evaporates there, and is gasified. Thereafter, the gas is suctioned by the compressor 1 and circulates.
- an installation contractor inputs, from the remote control 17, sets, and registers a necessary heating capacity estimated from a use-side set load and information on, for example, conditions for the underground heat exchanger 18, 19 or for the ground side.
- a necessary heating capacity estimated from a use-side set load and information on, for example, conditions for the underground heat exchanger 18, 19 or for the ground side.
- data such as the total length of a vertical hole in the case of a borehole system and a tube buried area in the case of a horizontal loop system is input.
- information on the total quantity of heat collection pre-designed and estimated for underground heat exchangers to be used is also input through the remote control 17.
- the controller 16 sets a heat collection limit value calculated from a computation performed using detected temperature data to prevent occurrence of a case where stored heat is used up before winter ends by performing a heating operation excessively during wintertime and the underground heat exchanger for heat collection is frozen and broken. The operation of the heat pump is stopped or made less active such that the set limit value is not exceeded.
- the controller 16 sets the heat collection limit value on the basis of the input ground-side information and the necessary capacity information, and controls the upper limit of the operation frequency of the compressor. This control will be described below together with a flow chart of Fig. 3 illustrating a control procedure.
- a necessary evaporator capacity Q2required is calculated by subtracting a compressor input Wcomp in a heat pump cycle from ground-side information input from the remote control 17, such as the total length Dinput of a vertical hole in the case of a borehole system, and a necessary heating capacity Q1 required (step S1).
- a unit necessary evaporation capacity QDrequired per unit length is calculated from the necessary evaporator capacity Q2required and the total length Dimput of the vertical hole regarding and for burying the underground heat exchanger 18 (step S2).
- an actual evaporation capacity Qacutual is calculated from the flow rate of a heat medium that actually flows and the difference between an inlet temperature and an outlet temperature of the refrigerant-brine heat exchanger.
- the flow rate of the heat medium that actually flows is measured by the heat collection flow rate sensor 6, and the difference between the inlet temperature and outlet temperature of the refrigerant-brine heat exchanger is calculated from measurement values of the heat collection return sensor 7 and the heat collection supply sensor 8.
- a unit actual evaporation capacity QDacutual per unit length is calculated by dividing the calculated actual evaporation capacity Qacutual by a total length Dactual of an actual vertical hole for the underground heat exchanger 18 to be actually used for heat collection.
- the calculation is performed using the flow rate of the heat medium that actually flows and the time required for the heat medium to travel from the inlet to the outlet of the refrigerant-brine heat exchanger.
- the flow rate of the heat medium that actually flows is measured by the heat collection flow rate sensor 6, and the time required to travel from the inlet to the outlet of the refrigerant-brine heat exchanger is measured by the controller 16 (step S3).
- the controller 16 compares the unit necessary evaporation capacity QDrequired per unit time with the unit actual evaporation capacity QDacutual per unit length, which have been calculated so far (step S4).
- step S5 This comparison shows that, in a case where the unit necessary evaporation capacity QDrequired per unit length, which is preset, is smaller than the unit actual evaporation capacity QDacutual per unit length for an actual heat collection operation, the unit necessary evaporation capacity QDrequired, which is calculated, is set as a limit value for heat collection from underground and is used for a compressor operation in a heat pump refrigeration cycle (step S5).
- step S5 makes it possible to keep using the heat pump heat source unit 22 of the geothermal heat pump device 15 all year round (geothermal heat stored during summertime is not used up until winter ends), thereby resulting in a high energy saving effect since no electric heater is used.
- the unit actual evaporation capacity QDacutual which is calculated, is set as a limit value for heat collection in a heat pump device operation (step S6), and the controller 16 performs control such that operation switching is conducted so that the difference between the unit necessary evaporation capacity QDrequired and the unit actual evaporation capacity QDacutual, which is calculated, corresponds to a heating operation to be performed by the electric heater 10.
- the unit necessary evaporation capacity QDrequired per unit length is greater than the unit actual evaporation capacity QDacutual per unit length
- the unit actual evaporation capacity QDacutual which is calculated, is set as the limit value for heat collection in the heat pump device operation, and operation control is conducted such that the heating operation is performed in which the difference is compensated with additional heating performed by the electric heater 10 capable of conducting supplemental heating.
- the upper limit of the operation frequency of the compressor is limited on the basis of a heat collection cumulative limit value, a cumulative evaporation capacity, and the temperature of the heat medium circulating through the underground heat exchanger.
- the upper limit of the operation frequency of the compressor is limited on the basis of the heat collection cumulative limit value and the temperature of the heat medium circulating through the underground heat exchanger, the heat collection cumulative limit value being based on the cumulative evaporation capacity calculated cumulatively from the total operation time and the flow rate of the heat medium by using the unit actual evaporation capacity.
- the vertical axis represents the heat collection cumulative limit value
- the horizontal axis represents the upper limit of the operation frequency of the compressor.
- the difference between the heat collection cumulative limit value and the cumulative evaporation capacity is calculated as needed, and in a case where half the difference and the temperature of the heat medium circulating through the underground heat exchanger at the time when the heat medium flows into the refrigerant-brine heat exchanger 4 are lower than a predetermined temperature T1, the upper limit of the operation frequency of the compressor is limited. As illustrated in Fig. 4 , as the difference between the heat collection cumulative limit value and the cumulative evaporation capacity is reduced, the upper limit of the operation frequency of the compressor is limited and decreased.
- the upper limit of the operation frequency is not limited and the operation continues as is.
- the heat pump heat source unit 22 stops operating and the operation is completely switched to an operation performed by the electric heater 10. In this manner, in a case where the difference between the heat collection cumulative limit value and the cumulative evaporation capacity reaches 0, the operation is switched to an operation performed by the electric heater 10 and a heating operation is handled, thereby lessening the energy saving effect.
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Abstract
Description
- The present invention relates to a geothermal heat pump device that uses the ground as a heat source, causes a heat medium to circulate through an underground heat exchanger, collects heat using a heat pump, and supplies warm water to a load side.
- A geothermal heat pump system that uses the ground and lakes as heat sources, causes a heat medium to circulate through an underground heat exchanger, collects and releases heat using a heat pump, and supplies warm water for heating or household use to a load side is a device using renewable energy. In particular, because of the use of geothermal heat of which the temperature is stable all year round, the geothermal heat pump system is regarded as a highly efficient device with low running cost and is capable of reducing the emission of CO2, and hence has attracted more attention recently.
- To keep using a geothermal heat pump system all year round, it is necessary to cause the ground to store heat during summertime and to effectively use the stored heat during wintertime. Since the amount of stored heat is limited, in a case where a heating operation is excessively performed during wintertime, the amount of heat consumed is large, the stored heat is consumed before winter ends, the heating operation is no longer performed, and an underground heat exchanger buried underground for heat collection may be frozen and broken in the end. Thus, an outlet temperature of heat medium water is made measurable using a temperature sensor, a soil temperature is calculated from the outlet temperature of the heat medium water, and limit values for heat collection and heat release to be performed by an underground heat exchanger are made settable. In addition, not to exceed the set limit values, a heat pump can stop operating or be operated less actively (for example, see Patent Literature 1).
- As a method for setting limit values, an outlet temperature of heat medium water is measured using a temperature sensor, a soil temperature is calculated from the outlet temperature of the heat medium water by a controller in which a program or data that has been input in advance is installed, and the limit values for heat collection and release are set. Furthermore, the limit values are determined also on the basis of the soil temperature of the previous year. A technology for grasping an operation status and geothermal heat characteristics as needed, estimating operation and performance on the basis of the operation status and geothermal heat characteristics, and adjusting system operating time and the amount of heat to be collected or released is disclosed (for example, see Patent Literature 2).
-
- Patent Literature 1: Japanese Unexamined Patent Application Publication No.
2006-292310 - Patent Literature 2: Japanese Unexamined Patent Application Publication No.
2012-233669 - However, the above-mentioned existing systems require a great many programs and many pieces of data to deal with environmental conditions, such as places where the devices are used and climates of the places, and various types of grounds and underground heat exchangers, thereby requiring complicated controllers. In a case where appropriate control is not possible, there is a problem in that underground heat exchangers may be frozen and broken and a complaint that heating is insufficient may arise.
- The present invention has been made to solve the above-described problem, and an object thereof is to set a limit value for heat collection from underground by using a simple method using, for example, detection data obtained from a geothermal heat pump device and specifications of a geothermal heat pump device, and provide pleasant air conditioning and hot water supply that meet users' requests without the freezing and breakdown of an underground heat exchanger.
- A geothermal heat pump device according to an embodiment of the present invention includes a heat pump heat source unit having a refrigerant circuit in which a compressor, a water-refrigerant heat exchanger, an expansion valve, and a refrigerant-brine heat exchanger in which a heat medium from an underground heat exchanger buried underground is connected such that the heat medium circulates are serially connected, a warm-water heater unit configured to supply warm water heated at the water-refrigerant heat exchanger to heating and air conditioning and hot water supply such that it circulates, and a controller configured to control an upper limit of an operation frequency of the compressor based on a heat collection limit value set by comparing a unit necessary evaporation capacity calculated from information on the underground heat exchanger with a unit actual evaporation capacity calculated from inlet and outlet temperatures and a circulation flow rate of the heat medium circulating through the refrigerant-brine heat exchanger.
- A geothermal heat pump device of an embodiment of the present invention includes a heat pump heat source unit having a refrigerant circuit in which a compressor, a water-refrigerant heat exchanger, an expansion valve, and a refrigerant-brine heat exchanger in which a heat medium from an underground heat exchanger buried underground is connected such that the heat medium circulates are serially connected, a warm-water heater unit configured to supply warm water heated at the water-refrigerant heat exchanger to heating and air conditioning and hot water supply such that the warm water circulates, a controller configured to control an upper limit of an operation frequency of the compressor based on a heat collection limit value set by comparing a unit necessary evaporation capacity calculated from information on the underground heat exchanger with a unit actual evaporation capacity calculated from inlet and outlet temperatures and a circulation flow rate of the heat medium circulating through the refrigerant-brine heat exchanger. An effect is achieved that the limit value for heat collection from underground is set by using a simple method using, for example, detection data obtained from the geothermal heat pump device and specifications of the geothermal heat pump device, and pleasant air conditioning and hot water supply that meet users' requests can be provided without the freezing and breakdown of the underground heat exchanger.
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- [
Fig. 1] Fig. 1 is a circuit diagram illustrating a schematic configuration of a geothermal heat pump device according toEmbodiment 1 of the present invention. - [
Fig. 2] Fig. 2 is a block diagram illustrating an electrical configuration of a controller of the geothermal heat pump device according toEmbodiment 1 of the present invention. - [
Fig. 3] Fig. 3 is a flowchart illustrating a control operation of the geothermal heat pump device according toEmbodiment 1 of the present invention. - [
Fig. 4] Fig. 4 is a characteristic diagram illustrating compressor operation frequency control performed by the geothermal heat pump device according toEmbodiment 1 of the present invention. -
Fig. 1 is a circuit diagram illustrating a schematic configuration of a geothermal heat pump device according toEmbodiment 1 of the present invention, andFig. 2 is a block diagram illustrating an electrical configuration of a controller of the geothermal heat pump device. The overall configuration will be described on the basis ofFigs. 1 and2 . - A geothermal
heat pump device 15 ofFig. 1 is a heat-pump hot water system using geothermal heat. The heat-pump hot water system causes a heat medium to circulate through an underground heat exchanger, collects heat using a heat pump, and supplies warm water for heating or living to a load side. The geothermalheat pump device 15 includes a heat pumpheat source unit 22 and a warm-water heater unit 23, the heat pumpheat source unit 22 performing a heat pump cycle (refrigeration cycle) operation using a refrigerant circuit, the warm-water heater unit 23 having a function of supplying warm water for heating to an indoor space and including devices, such as a heated-water tank 12 that stores warm water. Anunderground heat exchanger heat source unit 22, a heat medium is caused to circulate, and heat is collected using the heat pump. - The geothermal
heat pump device 15 of the present invention is a heat-pump air-conditioning hot water system that exchanges heat between refrigerant inside the refrigerant circuit of the heat pumpheat source unit 22, which performs the heat pump cycle (refrigeration cycle) operation, and a heat medium (for example, such as brine) of a circulation circuit using the underground heat exchanger, exchanges heat between the refrigerant inside the refrigerant circuit of the heat pumpheat source unit 22 and water in a water circuit connected to the warm-water heater unit 23, performs a heating operation by supplying, through the circulation of this water, warm water for heating to an indoor space, and that can further perform a hot-water supply operation by heating water stored in the heated-water tank 12. - Here, the
underground heat exchangers Fig. 1 , theunderground heat exchanger 18 is used to show the borehole system, and theunderground heat exchanger 19 is used to show the horizontal loop system. - Examples of the refrigerant used in the refrigeration cycle of the heat pump
heat source unit 22 include a HFO single refrigerant such as HFO-1234yf, a mixed refrigerant containing a HFO refrigerant and a HFC refrigerant such as R32, and natural refrigerants such as hydrocarbon, helium, and carbon dioxide. - The heat pump
heat source unit 22 is equipped with structural devices of the refrigerant circuit such as a refrigerant-brine heat exchanger (for example, a plate heat exchanger) 4 configured to exchange heat between a ground side heat medium and refrigerant, a water-refrigerant heat exchanger (for example, a plate heat exchanger) 2 configured to exchange heat between water on the warm-water heater side and refrigerant, acompressor 1 configured to compress refrigerant, and anexpansion valve 3. - In addition, the heat pump
heat source unit 22 is provided with aheat collection pump 5 for causing the heat medium to circulate through theunderground heat exchanger flow rate sensor 6 configured to detect flow rate of the heat medium for heat collection, and a heatcollection return sensor 7 and a heat collection supply sensor 8 for heat collection control and protection. - The warm-
water heater unit 23 is provided with, in addition to the heated-water tank 12, apump 9 configured to cause water inside the water circuit to circulate, the water having exchanged heat with refrigerant inside a refrigerant circuit in the water-refrigerant heat exchanger (for example, a plate heat exchanger) 2, anelectric heater 10 capable of further complementarily heating warm water heated at the water-refrigerant heat exchanger 2 at the time of heating, a three-way valve 21 serving as a channel switching unit that performs switching of a circulation destination of the water having exchanged heat at the water-refrigerant heat exchanger 2, a warm-water circulationflow rate sensor 14 for water flow rate detection, acontroller 16 configured to perform overall operation control, aremote control 17 through which a user can perform a setting operation, andwater temperature sensors - In
Fig. 1 , the directions of arrows indicate the direction of flow of the refrigerant at the time of heating, the direction of flow of the water, and the direction of the heat medium in the ground. - At the time of a heating operation or a hot-water supply operation through which the water stored in the heated-
water tank 12 is heated at the warm-water heater unit 23, refrigerant is discharged from thecompressor 1 in the directions of the arrows inFig. 1 and water is heated by the refrigerant at the water-refrigerant heat exchanger 2 in the heat pumpheat source unit 22, so that warm water (hot water) is generated. Thereafter, the pressure on the refrigerant is reduced by theexpansion valve 3, and the refrigerant exchanges heat at the refrigerant-brine heat exchanger 4 with the heat medium circulating through theunderground heat exchanger - The warm water obtained from the heat pump
heat source unit 22 reaches the three-way valve 21 via theelectric heater 10. The three-way valve 21 can switch a circulation destination of the warm water between a water-supply path to an indoor-side air-conditioning radiator and the side where the heated-water tank 12 is provided. Heating can be performed by switching the circulation destination to the indoor side at the three-way valve 21 and causing the warm water to circulate through the indoor radiator. Moreover, the water stored in the heated-water tank 12 can be heated by switching the circulation destination to thetank 12 side at the three-way valve 21 and causing the warm water to circulate through the tank. The water whose temperature has been reduced by passing through an indoor space or the heated-water tank 12 returns to the water-refrigerant heat exchanger 2 via the warm-water circulation pump 9 and circulates again. - The heated-
water tank 12 is substantially cylindrically shaped, and at least its outside is composed of, for example, a metal material, such as stainless steel. A water supply pipe that supplies water from, for example, a waterworks outside the system is connected to a lower portion of the heated-water tank 12. Water supplied from the water supply pipe flows into and stored in the heated-water tank 12. The water stored in the heated-water tank 12 is heated by performing the heating operation described above, and warm water is generated. In the heated-water tank 12, hot water is stored so as to form temperature layers such that high temperature layers are on the upper side and low temperature layers are on the lower side. A hot-water output pipe is connected to an upper portion of the heated-water tank 12 to remove warm water generated in the heated-water tank 12. The warm water generated in the heated-water tank 12 is supplied to the outside of a geothermalheat pump system 12 through the hot-water output pipe and is used as, for example, water for domestic use. The heated-water tank 12 is covered by a heat insulator to suppress heat dissipation from the stored warm water. - Next, the heat pump
heat source unit 22 will be described. Thecompressor 1 is a capacity controllable type whose rotation speed is controlled by an inverter, and provides a high-temperature, high-pressure state by suctioning and compressing refrigerant. Theexpansion valve 3 is an electronic expansion valve whose opening degree is variably controlled. The water-refrigerant heat exchanger 2 exchanges heat between water and refrigerant by using, for example, the warm-water circulation pump 9. The refrigerant-brine heat exchanger 4 exchanges heat between the heat medium flowing in theunderground heat exchanger heat collection pump 5. -
Fig. 2 is a control block diagram according toEmbodiment 1 of the present invention. -
Fig. 2 illustrates a connection configuration of thecontroller 16 configured to perform various types of measurement control on the geothermalheat pump device 15 ofEmbodiment 1 and operation information, actuators, and other devices connected to thecontroller 16. - The
controller 16 of the geothermalheat pump device 15 controls, for example, an operation frequency of thecompressor 1 of the heat pumpheat source unit 22 and the opening degree of theexpansion valve 3 on the basis of measurement information from thetemperature sensors heat pump device 15. - An operation of the heat pump
heat source unit 22 will be described. At the time of a heating and hot-water supply operation, a high-temperature, high-pressure gas refrigerant discharged from thecompressor 1 flows into the water-refrigerant heat exchanger 2 in the refrigerant circuit of the heat pump cycle. The gas refrigerant condenses and liquefies while dissipating heat at the water-refrigerant heat exchanger 2 serving as a condenser to become a high-pressure, low-temperature liquid refrigerant. Heat dissipated from the refrigerant is supplied to water on the load side to warm the water. Thereafter, the high-pressure, low-temperature refrigerant output from the water-refrigerant heat exchanger 2 flows into the refrigerant-brine heat exchanger 4 serving as an evaporator, absorbs heat and evaporates there, and is gasified. Thereafter, the gas is suctioned by thecompressor 1 and circulates. - To adapt the geothermal heat pump device to various types of grounds and underground heat exchangers and use the geothermal heat pump device all year round and not to use up geothermal heat stored during summertime before winter ends, when a main body of the geothermal
heat pump device 15 is locally installed, an installation contractor inputs, from theremote control 17, sets, and registers a necessary heating capacity estimated from a use-side set load and information on, for example, conditions for theunderground heat exchanger underground heat exchange remote control 17. - In the geothermal heat pump device according to the present invention, to keep using the geothermal heat pump system all year round, the
controller 16 sets a heat collection limit value calculated from a computation performed using detected temperature data to prevent occurrence of a case where stored heat is used up before winter ends by performing a heating operation excessively during wintertime and the underground heat exchanger for heat collection is frozen and broken. The operation of the heat pump is stopped or made less active such that the set limit value is not exceeded. - That is, the
controller 16 sets the heat collection limit value on the basis of the input ground-side information and the necessary capacity information, and controls the upper limit of the operation frequency of the compressor. This control will be described below together with a flow chart ofFig. 3 illustrating a control procedure. - First, a necessary evaporator capacity Q2required is calculated by subtracting a compressor input Wcomp in a heat pump cycle from ground-side information input from the
remote control 17, such as the total length Dinput of a vertical hole in the case of a borehole system, and a necessary heating capacity Q1 required (step S1). A unit necessary evaporation capacity QDrequired per unit length is calculated from the necessary evaporator capacity Q2required and the total length Dimput of the vertical hole regarding and for burying the underground heat exchanger 18 (step S2). - Next, an actual evaporation capacity Qacutual is calculated from the flow rate of a heat medium that actually flows and the difference between an inlet temperature and an outlet temperature of the refrigerant-brine heat exchanger. The flow rate of the heat medium that actually flows is measured by the heat collection
flow rate sensor 6, and the difference between the inlet temperature and outlet temperature of the refrigerant-brine heat exchanger is calculated from measurement values of the heatcollection return sensor 7 and the heat collection supply sensor 8. - A unit actual evaporation capacity QDacutual per unit length is calculated by dividing the calculated actual evaporation capacity Qacutual by a total length Dactual of an actual vertical hole for the
underground heat exchanger 18 to be actually used for heat collection. In this case, to calculate the total length Dactual of the actual vertical hole, the calculation is performed using the flow rate of the heat medium that actually flows and the time required for the heat medium to travel from the inlet to the outlet of the refrigerant-brine heat exchanger. The flow rate of the heat medium that actually flows is measured by the heat collectionflow rate sensor 6, and the time required to travel from the inlet to the outlet of the refrigerant-brine heat exchanger is measured by the controller 16 (step S3). - The
controller 16 compares the unit necessary evaporation capacity QDrequired per unit time with the unit actual evaporation capacity QDacutual per unit length, which have been calculated so far (step S4). - This comparison shows that, in a case where the unit necessary evaporation capacity QDrequired per unit length, which is preset, is smaller than the unit actual evaporation capacity QDacutual per unit length for an actual heat collection operation, the unit necessary evaporation capacity QDrequired, which is calculated, is set as a limit value for heat collection from underground and is used for a compressor operation in a heat pump refrigeration cycle (step S5). This makes it possible to keep using the heat pump
heat source unit 22 of the geothermalheat pump device 15 all year round (geothermal heat stored during summertime is not used up until winter ends), thereby resulting in a high energy saving effect since no electric heater is used. - In contrast, in a case where the unit necessary evaporation capacity QDrequired per unit length is greater than the unit actual evaporation capacity QDacutual per unit length, the unit actual evaporation capacity QDacutual, which is calculated, is set as a limit value for heat collection in a heat pump device operation (step S6), and the
controller 16 performs control such that operation switching is conducted so that the difference between the unit necessary evaporation capacity QDrequired and the unit actual evaporation capacity QDacutual, which is calculated, corresponds to a heating operation to be performed by theelectric heater 10. - In a case where the unit necessary evaporation capacity QDrequired per unit length is greater than the unit actual evaporation capacity QDacutual per unit length, the unit actual evaporation capacity QDacutual, which is calculated, is set as the limit value for heat collection in the heat pump device operation, and operation control is conducted such that the heating operation is performed in which the difference is compensated with additional heating performed by the
electric heater 10 capable of conducting supplemental heating. To cause the heat pump device to operate as much as possible, the upper limit of the operation frequency of the compressor is limited on the basis of a heat collection cumulative limit value, a cumulative evaporation capacity, and the temperature of the heat medium circulating through the underground heat exchanger. - As illustrated in
Fig. 4 , the upper limit of the operation frequency of the compressor is limited on the basis of the heat collection cumulative limit value and the temperature of the heat medium circulating through the underground heat exchanger, the heat collection cumulative limit value being based on the cumulative evaporation capacity calculated cumulatively from the total operation time and the flow rate of the heat medium by using the unit actual evaporation capacity. InFig. 4 , the vertical axis represents the heat collection cumulative limit value, and the horizontal axis represents the upper limit of the operation frequency of the compressor. The difference between the heat collection cumulative limit value and the cumulative evaporation capacity is calculated as needed, and in a case where half the difference and the temperature of the heat medium circulating through the underground heat exchanger at the time when the heat medium flows into the refrigerant-brine heat exchanger 4 are lower than a predetermined temperature T1, the upper limit of the operation frequency of the compressor is limited. As illustrated inFig. 4 , as the difference between the heat collection cumulative limit value and the cumulative evaporation capacity is reduced, the upper limit of the operation frequency of the compressor is limited and decreased. In this case, the predetermined temperature T1 is higher than a freezing start temperature of a brine heat medium by α deg and is a value based on brine characteristics. For example, in the case of propylene glycol, α = 0 degrees C. - That is, even when half the difference between the heat collection cumulative limit value and the cumulative evaporation capacity is reached, in a case where the inflow temperature at the refrigerant-
brine heat exchanger 4 is greater than or equal to T1 degrees C, the upper limit of the operation frequency is not limited and the operation continues as is. - In a case where the difference between the heat collection cumulative limit value and the cumulative evaporation capacity reaches 0, the heat pump
heat source unit 22 stops operating and the operation is completely switched to an operation performed by theelectric heater 10. In this manner, in a case where the difference between the heat collection cumulative limit value and the cumulative evaporation capacity reaches 0, the operation is switched to an operation performed by theelectric heater 10 and a heating operation is handled, thereby lessening the energy saving effect. Learning control is thus performed in the next winter such that the upper limit of the operation frequency of the compressor is limited in a case where half the difference between the heat collection cumulative limit value and the cumulative evaporation capacity and the inflow temperature at the refrigerant-brine heat exchanger 4 are below (T1 + 1) degrees C, thereby making it possible to prolong a period during which the heat pump can perform a heating operation. - In this manner, to perform optimization by performing learning control year after year, to prolong the period during which the heat pump can operate, and to keep using the geothermal heat pump device all year round on various types of grounds and geothermal water heat exchangers, operation control is possible such that the geothermal heat stored during summertime is not used up before winter ends. An effect is achieved that the limit value for heat collection from underground is set by using a simple method using, for example, detection data obtained from the geothermal heat pump device and specifications of the geothermal heat pump device, and pleasant air conditioning and hot water supply that meet users' requests can be provided without the freezing and breakdown of the underground heat exchanger. Reference Signs List
- 1
compressor 2 water-refrigerant heat exchanger 3expansion valve 4 refrigerant-brine heat exchanger 5heat collection pump 6 heat collectionflow rate sensor 7 heat collection return sensor 8 heatcollection supply sensor 9 warm-water circulation pump 10electric heater 11 warm-water circulation supplywater temperature sensor 12 heated-water tank 13 warm-water circulation returnwater temperature sensor 14 warm-water circulationflow rate sensor 15 geothermalheat pump device 16controller 17remote control 18 underground heat exchanger (borehole system) 19 underground heat exchanger (horizontal loop system) 20 heated-water tank sensor 21 three-way valve 22 heat pumpheat source unit 23 warm-water heater unit
Claims (5)
- A geothermal heat pump device comprising:a heat pump heat source unit having a refrigerant circuit in which a compressor, a water-refrigerant heat exchanger, an expansion valve, and a refrigerant-brine heat exchanger in which a heat medium from an underground heat exchanger buried underground is connected such that the heat medium circulates are serially connected;a warm-water heater unit configured to supply warm water heated at the water-refrigerant heat exchanger to heating and air conditioning and hot water supply such that the warm water circulates; anda controller configured to control an upper limit of an operation frequency of the compressor based on a heat collection limit value set by comparing a unit necessary evaporation capacity calculated from information on the underground heat exchanger with a unit actual evaporation capacity calculated from inlet and outlet temperatures and a circulation flow rate of the heat medium circulating through the refrigerant-brine heat exchanger.
- The geothermal heat pump device of claim 1, comprising a heat collection flow rate sensor configured to measure a flow rate of the heat medium circulating between the underground heat exchanger and the refrigerant-brine heat exchanger, wherein the unit actual evaporation capacity is calculated using a circulation flow rate detected by the heat collection flow rate sensor.
- The geothermal heat pump device of claim 1 or 2, comprising a remote control connected to the controller, wherein a length of a pipe of the underground heat exchanger buried underground and a preset necessary heating capacity are registered through the remote control.
- The geothermal heat pump device of any one of claims 1 to 3, wherein in a case where the unit necessary evaporation capacity is smaller than the unit actual evaporation capacity, an upper limit for underground heat collection is set from the unit necessary evaporation capacity, and in a case where the unit necessary evaporation capacity is greater than the unit actual evaporation capacity, an upper limit value for underground heat collection is set from the unit actual evaporation capacity and operation control is performed such that additional heating for a heat shortage corresponding to a difference is performed by an electric heater provided at a warm water circuit of the warm-water heater unit.
- The geothermal heat pump device of any one of claims 1 to 3, wherein the upper limit of the operation frequency of the compressor is limited using a difference between a cumulative evaporation capacity for heat collected so far based on the unit actual evaporation capacity and a heat collection cumulative limit value.
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RU2809315C1 (en) * | 2023-02-20 | 2023-12-11 | Сергей Викторович Коровкин | Heat pump heating system |
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CN110878956B (en) * | 2019-12-23 | 2023-10-17 | 北京市热力集团有限责任公司 | Control method for heat pump system and heat pump system |
CN114234445A (en) * | 2021-12-14 | 2022-03-25 | 广东芬尼克兹节能设备有限公司 | Constant-temperature water supply control method for variable-frequency heat pump |
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JP2003130494A (en) * | 2001-10-19 | 2003-05-08 | Ohbayashi Corp | Air conditioning system utilizing underground heat exchanger, and operating method for the same |
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KR101116927B1 (en) * | 2010-03-15 | 2012-02-27 | 한밭대학교 산학협력단 | Heat pump system using ground heat source |
JP5690650B2 (en) * | 2011-05-09 | 2015-03-25 | 新日鉄住金エンジニアリング株式会社 | Geothermal characteristics analysis method and apparatus, soil heat source heat pump system operation adjustment method and apparatus, and program |
JP5619698B2 (en) * | 2011-09-13 | 2014-11-05 | 株式会社コロナ | Geothermal heat pump device |
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JP6008772B2 (en) * | 2013-03-27 | 2016-10-19 | 三菱重工業株式会社 | Heat source system, control device therefor, and control method therefor |
DE102013214063A1 (en) * | 2013-07-16 | 2015-01-22 | Robert Bosch Gmbh | Method for controlling a compressor of a heat pump |
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RU2809315C1 (en) * | 2023-02-20 | 2023-12-11 | Сергей Викторович Коровкин | Heat pump heating system |
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Publication number | Publication date |
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EP3594588B1 (en) | 2022-07-13 |
EP3594588A4 (en) | 2020-04-08 |
WO2018163347A1 (en) | 2018-09-13 |
JPWO2018163347A1 (en) | 2019-11-07 |
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