EP3594588B1 - Dispositif de pompe à chaleur géothermique - Google Patents

Dispositif de pompe à chaleur géothermique Download PDF

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Publication number
EP3594588B1
EP3594588B1 EP17899277.2A EP17899277A EP3594588B1 EP 3594588 B1 EP3594588 B1 EP 3594588B1 EP 17899277 A EP17899277 A EP 17899277A EP 3594588 B1 EP3594588 B1 EP 3594588B1
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EP
European Patent Office
Prior art keywords
heat
water
heat exchanger
refrigerant
underground
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EP17899277.2A
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German (de)
English (en)
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EP3594588A1 (fr
EP3594588A4 (fr
Inventor
Yoshiro Aoyagi
Kazutaka Suzuki
Koji Matsuzawa
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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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
    • F24D17/00—Domestic hot-water supply systems
    • F24D17/02—Domestic hot-water supply systems using heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
    • F24D19/1066—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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/375—Control of heat pumps
    • F24H15/38—Control of compressors of heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/40—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
    • 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
    • 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
    • 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
    • F25B30/00—Heat pumps
    • F25B30/06—Heat pumps characterised by the source of low potential heat
    • 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
    • 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
    • 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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/227—Temperature of the refrigerant in heat pump cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/281—Input from user
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/375—Control of heat pumps
    • F24H15/385—Control of expansion valves of heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • 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
    • 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 brine as a heat medium to circulate through an underground heat exchanger, collects heat using the 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).
  • Patent Literature 3 discloses a geothermal heat pump system for switching a heat source supplying mechanism between a single source and multiple sources, wherein if a heat capacity provided by a underground source heat exchanger is lower than an amount of the required heat capacity, a controller of the geothermal heat pump system performs the simultaneous operation of both an air-source heat exchanger and the underground source heat exchanger.
  • Patent Literature 4 discloses a geothermal heat pump system for heat and cooling operations comprises an underground source heat exchanger as a main source heat exchanger and an electrical heater as an auxiliary heat exchanger. When the heat capacity provided by the underground source heat exchanger is lower than an amount of the required heat capacity, the electrical heater starts heating on flowing refrigerants to achieve the required heat capacity.
  • 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 the present invention is defined by appended independent claim 1.
  • the geothermal heat pump device of the present invention an effect is achieved that the limit value for heat collection from underground is set by using a simple method using the data defined by independent claim 1, and using, for example, additional 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, i.e. 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 i.e. 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 indoorside 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 an operation frequency of the compressor 1 of the heat pump heat source unit 22 and the opening degree of the expansion valve 3, for example, 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 Q1required (step S1).
  • a unit necessary evaporation capacity QDrequired per unit length is calculated from the necessary evaporator capacity Q2required and the total length Dinput 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, i.e. the brine, that actually flows and the time required for the heat medium, i.e. the brine, to travel from the outlet to the inlet 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 outlet to the inlet 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 length 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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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Computer Hardware Design (AREA)
  • Fluid Mechanics (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Claims (5)

  1. Dispositif de pompe à chaleur géothermique (15) comprenant :
    une unité source de chaleur de pompe à chaleur (22) présentant un circuit de fluide frigorigène dans lequel sont connectés en série, un compresseur (1), un échangeur de chaleur eau - fluide frigorigène (2), une soupape d'expansion (3), et un échangeur de chaleur fluide frigorigène - saumure (4), auquel est connecté un échangeur de chaleur enterré (18, 19) de telle sorte qu'une saumure circule à partir de l'échangeur de chaleur souterrain (18, 19) ;
    une unité dispositif de chauffage d'eau chaude (23), configurée pour fournir l'eau chaude chauffée au niveau de l'échangeur de chaleur eau - fluide frigorigène (2), à un dispositif de chauffage, de climatisation et de fourniture d'eau chaude, de telle sorte que l'eau chaude circule ; et
    un contrôleur (16), configuré pour commander la limite supérieure de la fréquence de fonctionnement du compresseur (1),
    le dispositif de pompe à chaleur géothermique étant caractérisé en ce que le contrôleur (16) est configuré pour commander la limite supérieure de la fréquence de fonctionnement du compresseur (1), sur la base d'une valeur limite de collecte de chaleur, fixée en comparant une capacité d'évaporation nécessaire unitaire calculée à partir de la longueur totale d'un trou vertical ou d'une zone enterrée d'un tube de l'échangeur de chaleur souterrain (18, 19), et d'une quantité totale de collecte de chaleur préconçue et estimée de l'échangeur de chaleur souterrain (18, 19), à une capacité d'évaporation réelle unitaire calculée à partir des températures en entrée et en sortie, et du débit de circulation de la saumure qui circule à travers l'échangeur de chaleur fluide frigorigène - saumure (4).
  2. Dispositif de pompe à chaleur géothermique (15) selon la revendication 1, comprenant un capteur de débit de collecte de chaleur (6), configuré pour mesurer le débit de la saumure qui circule entre l'échangeur de chaleur souterrain (18, 19), et l'échangeur de chaleur fluide frigorigène - saumure (4), dans lequel la capacité d'évaporation réelle unitaire est calculée en utilisant le débit de circulation détecté par le capteur de débit de collecte de chaleur (6).
  3. Dispositif de pompe à chaleur géothermique (15) selon la revendication 1 ou 2, comprenant une commande à distance (17) connectée au contrôleur (16), dans lequel la longueur d'une canalisation de l'échangeur de chaleur souterrain (18, 19) enterrée dans le sol, et une capacité de chauffage nécessaire préréglée, sont enregistrées par l'intermédiaire de la commande à distance (17).
  4. Dispositif de pompe à chaleur géothermique (15) selon l'une quelconque des revendications 1 à 3, dans lequel, dans un cas où la capacité d'évaporation nécessaire unitaire est inférieure à la capacité d'évaporation réelle unitaire, la valeur limite de collecte de chaleur souterraine, est fixée à partir de la capacité d'évaporation nécessaire unitaire, et dans un cas où la capacité d'évaporation nécessaire unitaire est supérieure à la capacité d'évaporation réelle unitaire, la valeur limite de collecte de chaleur souterraine, est fixée à partir de la capacité d'évaporation réelle unitaire, et la commande de fonctionnement est exécutée de telle sorte qu'un chauffage supplémentaire pendant une pénurie de chaleur correspondant à une différence, soit exécuté par un dispositif de chauffage électrique (10) fourni au niveau d'un circuit d'eau chaude de l'unité dispositif de chauffage d'eau chaude (23).
  5. Dispositif de pompe à chaleur géothermique (15) selon l'une quelconque des revendications 1 à 3, dans lequel la limite supérieure de la fréquence de fonctionnement du compresseur (1), est limitée en outre en utilisant une différence entre une capacité d'évaporation cumulative de la chaleur collectée jusqu'ici sur la base de la capacité d'évaporation réelle unitaire, et une valeur limite cumulative de collecte de chaleur.
EP17899277.2A 2017-03-09 2017-03-09 Dispositif de pompe à chaleur géothermique Active EP3594588B1 (fr)

Applications Claiming Priority (1)

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CN110878956B (zh) * 2019-12-23 2023-10-17 北京市热力集团有限责任公司 用于热泵系统的控制方法及热泵系统
CN114234445A (zh) * 2021-12-14 2022-03-25 广东芬尼克兹节能设备有限公司 变频热泵恒温供水控制方法

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JP2003130494A (ja) * 2001-10-19 2003-05-08 Ohbayashi Corp 地中熱交換器を利用した空気調和システムおよびその空気調和システムの運転方法
JP4782462B2 (ja) * 2005-04-13 2011-09-28 新日鉄エンジニアリング株式会社 地中熱利用ヒートポンプ装置、これを備えた地中熱利用装置、および地中熱利用ヒートポンプ装置の制御方法
US9423159B2 (en) * 2009-12-21 2016-08-23 Trane International Inc. Bi-directional cascade heat pump system
KR101116927B1 (ko) * 2010-03-15 2012-02-27 한밭대학교 산학협력단 지열 열펌프 시스템
JP5690650B2 (ja) * 2011-05-09 2015-03-25 新日鉄住金エンジニアリング株式会社 地盤熱特性解析方法及び装置、土壌熱源ヒートポンプシステムの運転調整方法及び装置、並びにプログラム
JP5619698B2 (ja) * 2011-09-13 2014-11-05 株式会社コロナ 地中熱ヒートポンプ装置
CN104704302B (zh) * 2012-10-05 2017-05-17 三菱电机株式会社 热泵装置
JP6008772B2 (ja) * 2013-03-27 2016-10-19 三菱重工業株式会社 熱源システム及びその制御装置並びにその制御方法
DE102013214063A1 (de) * 2013-07-16 2015-01-22 Robert Bosch Gmbh Verfahren zum Steuern eines Kompressors einer Wärmepumpe

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EP3594588A1 (fr) 2020-01-15
EP3594588A4 (fr) 2020-04-08
JPWO2018163347A1 (ja) 2019-11-07

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