WO2014122922A1 - 暖房システム - Google Patents

暖房システム Download PDF

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Publication number
WO2014122922A1
WO2014122922A1 PCT/JP2014/000576 JP2014000576W WO2014122922A1 WO 2014122922 A1 WO2014122922 A1 WO 2014122922A1 JP 2014000576 W JP2014000576 W JP 2014000576W WO 2014122922 A1 WO2014122922 A1 WO 2014122922A1
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WO
WIPO (PCT)
Prior art keywords
heat
temperature
hot water
evaporator
heat exchanger
Prior art date
Application number
PCT/JP2014/000576
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
▲祥▼▲隆▼ 久米
Original Assignee
株式会社デンソー
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by 株式会社デンソー filed Critical 株式会社デンソー
Priority to DE112014000726.9T priority Critical patent/DE112014000726T5/de
Publication of WO2014122922A1 publication Critical patent/WO2014122922A1/ja

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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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D11/00—Central heating systems using heat accumulated in storage masses
    • F24D11/02—Central heating systems using heat accumulated in storage masses using heat pumps
    • F24D11/0257—Central heating systems using heat accumulated in storage masses using heat pumps air heating system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1084—Arrangement or mounting of control or safety devices for air heating systems
    • F24D19/1087—Arrangement or mounting of control or safety devices for air heating systems system using a heat pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D5/00—Hot-air central heating systems; Exhaust gas central heating systems
    • F24D5/02—Hot-air central heating systems; Exhaust gas central heating systems operating with discharge of hot air into the space or area to be heated
    • 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
    • F24D5/00—Hot-air central heating systems; Exhaust gas central heating systems
    • F24D5/12—Hot-air central heating systems; Exhaust gas central heating systems using 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
    • F24H15/10—Control of fluid heaters characterised by the purpose of the control
    • F24H15/136—Defrosting or de-icing; Preventing freezing
    • 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
    • F24H15/10—Control of fluid heaters characterised by the purpose of the control
    • F24H15/156—Reducing the quantity of energy consumed; Increasing efficiency
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/212—Temperature of the water
    • F24H15/223—Temperature of the water in the water storage tank
    • F24H15/225—Temperature of the water in the water storage tank at different heights of the tank
    • 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
    • F24H15/231—Temperature of the refrigerant in heat pump cycles at the evaporator
    • 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
    • F24H15/235—Temperature of exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/305—Control of valves
    • F24H15/32—Control of valves of switching valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/375—Control of heat pumps
    • F24H15/38—Control of compressors of heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/375—Control of heat pumps
    • F24H15/385—Control of expansion valves of heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2200/00—Heat sources or energy sources
    • F24D2200/12—Heat pump
    • F24D2200/123—Compression type heat pumps
    • 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
    • F24D2200/16—Waste heat
    • F24D2200/22—Ventilation air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/242—Pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/40—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B10/00—Integration of renewable energy sources in buildings
    • Y02B10/70—Hybrid systems, e.g. uninterruptible or back-up power supplies integrating renewable energies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/13—Hot air central heating systems using heat pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency

Definitions

  • the present disclosure relates to a heating system including a heat pump cycle.
  • Patent Document 1 discloses an air conditioning system including a ventilation heat exchanger and a heat pump cycle.
  • the ventilation heat exchanger when the ventilation heat exchanger ventilates the room that is the air-conditioning target space, the ventilation heat exchanger uses exhaust air (inside air) exhausted from the room to the outside and supply air (outside air) taken into the room from the outside. Heat exchange is performed to suppress the indoor temperature change due to ventilation. Further, the heat pump cycle fulfills a function of heating the supply air that has flowed out of the ventilation heat exchanger during the heating operation for heating the room.
  • the air conditioning system of Patent Document 1 is provided with a bypass air passage that guides exhausted air discharged from the room to the outside to bypass the ventilation heat exchanger to the evaporator side of the heat pump cycle. Then, during heating operation, a part of the exhaust air (inside air) that is higher than the outside air temperature is led to the evaporator side via the bypass air passage to suppress the frost formation of the evaporator. We are trying to suppress the deterioration of the heat exchange performance of the evaporator.
  • Such an increase in the heating capacity of the heat pump cycle causes an increase in energy consumption of the heat pump cycle. Furthermore, if the heating capacity of the heat pump cycle is increased, the refrigerant evaporation temperature in the evaporator is lowered, so that the frost formation in the evaporator may not be sufficiently suppressed with only the heat of some exhaust air. is there.
  • the present disclosure provides heat exchange of an evaporator by frost formation while achieving sufficient heating of a space to be heated without causing an increase in energy consumption of the heat pump cycle in a heating system including a heat pump cycle.
  • the purpose is to suppress the decline in ability.
  • the heating system in the present disclosure includes a heat pump cycle, a heat medium tank, a ventilation heat exchanger, a high temperature side heater core, a ventilation path forming member, a heat quantity detector, A discharge capacity control unit and a defrost necessity determination unit are provided.
  • the heat pump cycle includes: (i) a compressor that compresses and discharges the refrigerant; (ii) a heat medium-refrigerant heat exchanger that heats the heat medium by exchanging heat between the refrigerant discharged from the compressor and the heat medium; iii) a decompressor for depressurizing the refrigerant flowing out from the heat medium-refrigerant heat exchanger, and (iv) an evaporator for evaporating the refrigerant depressurized by the depressurizer.
  • the heat medium tank stores the heat medium heated by the heat medium-refrigerant heat exchanger.
  • the ventilation heat exchanger exchanges heat between exhaust air discharged from the space to be heated to the outside of the room and supply air taken from the outside to the space to be heated.
  • the high temperature side heater core heats the supply air flowing out from the ventilation heat exchanger using the heat medium stored in the heat medium tank as a heat source.
  • a ventilation path formation member forms the ventilation path which guides the exhaust air which flowed out from the ventilation heat exchanger to the evaporator side.
  • the heat quantity detector detects the heat quantity of the heat medium stored in the heat medium tank.
  • the discharge capacity control unit controls the operation of the compressor.
  • a defrost necessity determination part determines whether it is necessary to defrost an evaporator.
  • the discharge capacity control unit determines that the evaporator needs to be defrosted by the defrost necessity determination unit, and the amount of heat detected by the heat quantity detector is equal to or greater than a predetermined reference heat amount Reduces the refrigerant discharge capacity of the compressor.
  • the refrigerant discharge capacity of the compressor is reduced. Therefore, the power consumption of the compressor can be reduced. That is, the energy consumption of the heat pump cycle can be reduced.
  • the ventilation path formation member which forms the ventilation path which guides the exhaust air which flowed out from the ventilation heat exchanger to the evaporator side is provided, the defrost of the evaporator is performed by the exhaust air which is comparatively high temperature. be able to. At this time, since the refrigerant discharge capacity of the compressor is reduced, the progress of frost formation in the evaporator is suppressed, and efficient defrosting can be performed by the discharged air.
  • the heat quantity of the heat medium stored in the heat medium tank is equal to or higher than the reference heat quantity, even if the refrigerant discharge capacity of the compressor is reduced, the high temperature side heater core flows out of the ventilation heat exchanger and is subject to heating. It is possible to raise the temperature of the intake air taken into the space. Therefore, it is desirable that the reference heat amount be set to a value that allows the high-temperature side heater core to raise the supply air to a temperature necessary for heating the space to be heated.
  • reducing the refrigerant discharge capacity of the compressor in the present disclosure does not simply mean lowering the refrigerant discharge capacity in a state where the compressor is operated, but may also stop the compressor. Including meaning.
  • the heating system includes a throttle opening degree control unit that controls the operation of the decompressor.
  • the throttle opening degree control unit determines that the evaporator needs to be defrosted by the defrost necessity determination unit, and when the amount of heat detected by the heat quantity detector is lower than the reference heat amount, The throttle opening of the decompressor may be increased.
  • the high temperature refrigerant discharged from the compressor flows into the evaporator by increasing the throttle opening of the decompressor.
  • the evaporator can be defrosted.
  • the heating system 1 of the present embodiment is applied to a residential house, and heats each room (heating target space) such as a living room, a kitchen, and a bedroom. Furthermore, this residential house is a highly airtight house called a so-called high airtight house, and requires constant ventilation.
  • the heating system 1 includes a heat pump cycle 10 that heats hot water, a hot water storage tank 20 that stores hot water heated by the heat pump cycle 10, and indoor ventilation.
  • a supply air heating unit 30 for heating supply air (outside air) taken into the room from the outside is provided.
  • the heat pump cycle 10 is a vapor compression refrigeration cycle configured by sequentially connecting a compressor 11, a water-refrigerant heat exchanger 12, an electric expansion valve 13, an evaporator 14 and the like with refrigerant pipes.
  • this heat pump cycle 10 employs carbon dioxide as a refrigerant, and the refrigerant pressure on the high pressure side of the cycle from the discharge port side of the compressor 11 to the inlet side of the electric expansion valve 13 is equal to or higher than the critical pressure of the refrigerant.
  • the refrigerant is mixed with refrigerating machine oil for lubricating the compressor 11, and a part of the refrigerating machine oil circulates in the cycle together with the refrigerant.
  • the compressor 11 sucks the refrigerant in the heat pump cycle 10 and compresses and discharges the refrigerant until it reaches a critical pressure or higher.
  • an electric compressor that drives a fixed displacement type compression mechanism with a fixed discharge capacity by an electric motor is employed as the compressor 11.
  • the operation (the number of rotations) of the electric motor of the compressor 11 is controlled by a control signal output from a control device described later.
  • the water-refrigerant heat exchanger 12 heats the hot water by exchanging heat between the refrigerant discharged from the compressor 11 and the hot water.
  • Hot water is a fluid to be heated in the heat pump cycle 10 and is stored in a hot water storage tank 20 described later, and then supplied to a kitchen or a bath.
  • the hot water supply of the present embodiment also functions as a heat medium for transferring the heat generated in the heat pump cycle 10 to the hot water stored in the hot water storage tank 20.
  • the water-refrigerant heat exchanger 12 of this embodiment constitutes a heat medium-refrigerant heat exchanger.
  • a plurality of tubes for circulating the refrigerant are provided as the refrigerant passage 12a, a water passage 12b is formed between adjacent tubes, and the refrigerant, cooling water, It is possible to employ a heat exchanger or the like configured by arranging inner fins that promote heat exchange between the two.
  • a counter flow type heat exchanger is employed as the water-refrigerant heat exchanger 12 in which the flow direction of the refrigerant flowing through the refrigerant passage 12a and the flow direction of hot water flowing through the water passage 12b are opposite flows. is doing.
  • heat is exchanged between the refrigerant on the inlet side of the refrigerant passage 12a and hot water on the outlet side of the water passage 12b, and heat is supplied to the refrigerant on the outlet side of the refrigerant passage 12a and the hot water on the inlet side of the water passage 12b. Since it can be exchanged, the temperature difference between the hot water and the refrigerant can be ensured over the entire heat exchange region, and the heat exchange efficiency can be improved.
  • the heat pump cycle 10 of the present embodiment constitutes a supercritical refrigeration cycle as described above, the refrigerant is not condensed in the refrigerant passage 12a of the water-refrigerant heat exchanger 12 in a supercritical state. Dissipate heat and reduce its enthalpy.
  • the electric expansion valve 13 is a decompressor that decompresses the refrigerant flowing out from the refrigerant passage 12a of the water-refrigerant heat exchanger 12.
  • the electric expansion valve 13 is a variable throttle mechanism that includes a valve body that can change the throttle opening degree and an electric actuator that changes the throttle opening degree of the valve body. . Further, the operation of the electric actuator is controlled by a control signal output from the control device.
  • the evaporator 14 exchanges heat between the refrigerant decompressed by the electric expansion valve 13 and the outside air blown from a blower fan (not shown) or exhaust air flowing out from a ventilation heat exchanger 34 of a supply air heating unit 30 described later. Evaporate.
  • a fin-and-tube heat exchanger or the like can be employed as such an evaporator 14.
  • the refrigerant outlet side of the evaporator 14 is connected to the suction port side of the compressor 11.
  • the compressor 11, the water-refrigerant heat exchanger 12, the electric expansion valve 13, and the evaporator 14 (constituent devices in the range surrounded by the one-dot chain line in FIG. 1) constituting the heat pump cycle 10 are in one housing. It is housed in the body or in one frame structure and is integrally configured as a heat pump unit.
  • the hot water storage tank 20 is formed of a metal having excellent corrosion resistance (for example, stainless steel), and has a heat insulating structure in which the outer periphery is covered with a heat insulating material or a vacuum heat insulating structure with a double tank, and keeps hot hot water hot for a long time. It is a heat medium tank that can.
  • the hot water storage tank 20 is disposed outside the room.
  • Hot water stored in the hot water storage tank 20 is discharged from a hot water outlet provided in the upper part of the hot water storage tank 20, mixed with cold water from a water tap at a temperature control valve (not shown), and then adjusted in temperature (for example, cooking) Hot water is supplied to places and baths.
  • tap water is supplied from a water supply port provided in the lower part of the hot water storage tank 20, and hot water for the amount of hot water supplied to the room is replenished.
  • the hot water storage tank 20 is connected to the water passage 12 b of the water-refrigerant heat exchanger 12 of the heat pump cycle 10 by the first water circulation circuit 21.
  • the first water circulation circuit 21 is a water circulation circuit that circulates hot water between the hot water storage tank 20 and the water-refrigerant heat exchanger 12.
  • the first water circulation circuit 21 is provided with a first water circulation pump 22 as a water pressure feeding unit for circulating hot water.
  • the first water circulation pump 22 sucks hot water flowing out from a hot water outlet provided at the lower side of the hot water storage tank 20 and pumps the hot water into the water passage 12 b of the water-refrigerant heat exchanger 12. It is a water pump. Further, the operation (rotation speed) of the first water circulation pump 22 is controlled by a control signal output from the control device.
  • the first water circulation pump 22 when the first water circulation pump 22 is operated, hot water is supplied from the hot water outlet provided at the lower side of the hot water storage tank 20 ⁇ the first water circulation pump 22 ⁇ the water passage 12b of the water-refrigerant heat exchanger 12 ⁇ the hot water storage tank. It circulates in order of the hot water supply inlet provided on the upper side of 20. Accordingly, the hot water heated by the water-refrigerant heat exchanger 12 flows out to the upper side of the hot water storage tank 20, and the temperature distribution in which the temperature of the hot water is decreased from the upper side to the lower side in the hot water storage tank 20. Occurs.
  • thermoelectric heat exchanger 12 since a counter-flow type heat exchanger is adopted as the water-refrigerant heat exchanger 12, hot water flowing out from the hot water outlet provided on the lower side of the hot water storage tank 20 is water. -Heat exchange is performed with a refrigerant having a relatively low enthalpy flowing in the refrigerant flow downstream of the refrigerant passage 12a of the refrigerant heat exchanger 12. That is, the low-temperature hot-water supply on the lower side of the hot water storage tank 20 is exchanged by the water-refrigerant heat exchanger 12 with a heat medium that directly exchanges heat with the refrigerant flowing into the electric expansion valve 13 on the downstream side of the refrigerant passage 12a. Become.
  • hot water flowing out of the water passage 12b of the water-refrigerant heat exchanger 12 exchanges heat with a refrigerant having a relatively high enthalpy flowing through the refrigerant flow upstream side of the refrigerant passage 12a of the water-refrigerant heat exchanger 12. Heated. That is, the hot hot water on the upper side of the hot water storage tank 20 becomes a heat medium directly heated by the high-temperature high-pressure refrigerant discharged from the compressor 11 of the heat pump cycle 10 in the water-refrigerant heat exchanger 12. .
  • the exhaust air ventilation path 32 through which the exhaust air exhausted from the room to the outside flows and the air supply ventilation through which the air taken from the outside into the room flows.
  • It has the casing 31 in which the path 33 was formed.
  • an exhaust air blower fan 32a, an air supply blower fan 33a, a ventilation heat exchanger 34, and a high temperature side heater core 35 are accommodated.
  • the exhaust air blower fan 32 a is an electric blower that blows exhaust air from the room to the outside, and is disposed on the most upstream side of the exhaust air flow in the exhaust air ventilation path 32.
  • the supply air blower fan 33 a is an electric blower that blows supply air from the outside to the inside of the room, and is disposed on the most upstream side of the supply air flow path 33.
  • the exhaust air blower fan 32a and the supply air blower fan 33a are both controlled in operating rate, that is, the number of rotations (the amount of blown air) by a control voltage output from the control device.
  • the ventilation heat exchanger 34 exchanges heat between the exhaust air and the supply air when the room is ventilated. Therefore, the ventilation heat exchanger 34 can heat the supply air by, for example, exchanging heat between the high-temperature exhaust air and the low-temperature supply air during indoor heating. That is, the ventilation heat exchanger 34 functions to suppress the temperature drop in the room due to ventilation by recovering the heat energy that is exhausted to the outside of the room together with the exhaust air during heating, and heating the supply air.
  • a ventilation heat exchanger 34 As such a ventilation heat exchanger 34, a plurality of metal plates (for example, an aluminum plate and a copper plate) having excellent heat conductivity are laminated in parallel to each other, and an exhaust air passage and an intake air are disposed between adjacent metal plates. Adopting a heat exchanger or the like that is formed by alternately forming passages and arranging inner fins that promote heat exchange between exhaust air and supply air inside each exhaust air passage and supply air passage Can do.
  • the ventilation heat exchanger 34 can also cool the supply air by, for example, exchanging heat between the high-temperature air supply and the low-temperature exhaust air during indoor cooling.
  • the high-temperature side heater core 35 is a heat exchanger for heating that circulates hot water therein and heats the supply air that flows out of the ventilation heat exchanger 34 using this hot water as a heat source (supply air downstream of the ventilation heat exchanger 34). .
  • the high temperature side heater core 35 is disposed in a second water circulation circuit 37 that circulates warm water, and is connected to a warm water passage 38 disposed in the hot water storage tank 20.
  • the second water circulation circuit 37 is a water circulation circuit that circulates hot water between the hot water passage 38 and the high temperature side heater core 35. Further, the second water circulation circuit 37 is provided with a second water circulation pump 39 as a water pressure feeding section for circulating hot water.
  • the hot water circulating in the second water circulation circuit 37 is a heat medium that moves the heat of hot water stored in the hot water storage tank 20 to the supply air, and uses the same tap water or ethylene glycol aqueous solution as the hot water. Can be adopted. That is, in the heating system 1 of the present embodiment, the heat generated in the heat pump cycle 10 is moved to the intake air via two types of heat medium, hot water and hot water.
  • the hot water passage 38 is configured by hot water piping arranged to extend in the vertical direction while meandering in the hot water storage tank 20. Therefore, by circulating the hot water through the hot water passage 38, the hot water can be heated using hot water stored in the hot water storage tank 20 as a heat source.
  • the hot water inlet of the hot water passage 38 of this embodiment is provided below the hot water storage tank 20, and the hot water outlet of the hot water passage 38 is provided above the hot water storage tank 20.
  • the hot water supply in the hot water storage tank 20 has a temperature distribution in which the temperature increases from the lower side to the upper side, so that the hot water flowing through the hot water passage 38 is also from the lower side (hot water inlet side). The temperature increases toward the upper side (warm water outlet side).
  • the second water circulation pump 39 is an electric water pump that sucks hot water flowing out from the high temperature side heater core 35 and pumps it to the hot water inlet side of the hot water passage 38.
  • the operation (rotation speed) of the second water circulation pump 39 is controlled by a control signal output from the control device.
  • the hot water is arranged at the second water circulation pump 39 ⁇ the hot water inlet 38 of the hot water passage 38 arranged on the lower side of the hot water storage tank 20 ⁇ the hot water passage 38 ⁇ the upper side of the hot water storage tank 20.
  • the hot water passage 38 is circulated in the order of the hot water outlet ⁇ the high temperature side heater core 35.
  • a duct 36 is connected as a ventilation path forming member that forms a ventilation path leading to the evaporator 14 side of the heat pump cycle 10.
  • a control device (not shown) includes a known microcomputer including a CPU, a ROM, a RAM, and the like and peripheral circuits thereof. This control device performs various calculations and processes based on the control program stored in the ROM, and controls the operations of the various electric actuators 11, 13, 22, 32a, 33a, 39, etc. described above.
  • various controls such as a high pressure side pressure sensor, a boiling temperature sensor, an evaporator temperature sensor 41, an outside air temperature sensor, an outlet side hot water temperature sensor, an in-tank temperature sensor 42, and an outlet side exhaust air temperature sensor 43 are provided. Sensor groups are connected, and detection signals from these sensor groups are input to the control device.
  • the high pressure side pressure sensor is a high pressure side pressure detector that detects the high pressure side refrigerant pressure Pd of the high pressure refrigerant discharged from the compressor 11.
  • the boiling temperature sensor is a boiling temperature detector that detects the boiling temperature Two of hot water flowing out from the water passage of the water-refrigerant heat exchanger 12.
  • the evaporator temperature sensor 41 is an evaporator temperature detector that detects a refrigerant evaporation temperature (an evaporator temperature of the evaporator 14) Ts in the evaporator 14.
  • the outside air temperature sensor is an outside air temperature detector that detects the outside air temperature Tam.
  • the outlet side exhaust air temperature sensor 43 is an outlet side hot water temperature detector that detects an outlet temperature Tout of hot water flowing out from the hot water passage 38.
  • the in-tank temperature sensor 42 detects the temperature of the hot water stored in the hot water storage tank 20.
  • the outlet side exhaust air temperature sensor 43 is an exhaust air temperature detector that detects the outlet side exhaust air temperature Texo of the exhaust air flowing out from the ventilation heat exchanger 34.
  • the evaporator temperature sensor 41 of the present embodiment specifically detects the heat exchange fin temperature of the evaporator 14.
  • a temperature detector that detects the temperature of other parts of the evaporator 14 may be adopted as the evaporator temperature sensor 41, or a temperature detector that directly detects the temperature of the refrigerant itself flowing through the evaporator 14 may be used. It may be adopted.
  • the in-tank temperature sensor 42 of the present embodiment is constituted by a plurality of (in the present embodiment, five) temperature sensors arranged in the vertical direction in the hot water storage tank 20.
  • the control device can detect the temperature and temperature distribution of the hot water supply according to the water level in the hot water storage tank 20 based on the output signals of the plurality of in-tank temperature sensors 42.
  • the amount of heat Qt of the hot water (heat medium) stored in the hot water storage tank 20 is calculated from the water level of the hot water in the hot water storage tank 20 calculated from the detection value of the tank temperature sensor 42 and the temperature distribution.
  • the in-tank temperature sensor 42 including the plurality of temperature sensors of the present embodiment constitutes a heat quantity detector.
  • an operation panel (not shown) is connected to the input side of the control device.
  • This operation panel is provided with an operation switch that outputs an operation request signal for requesting the operation of the heating system 1, a temperature setting switch that sets a boiling temperature (target heating temperature) of hot water. Operation signals of these switches are input to the control device.
  • control device of the present embodiment is configured such that a control unit that controls various devices to be controlled connected to the output side is integrally configured.
  • movement of each control object apparatus among the control apparatuses comprises the control part which controls the operation
  • a configuration (hardware and software) that controls the operation of the compressor 11 constitutes a discharge capacity control unit, and the operation of the electric expansion valve 13 (electric type).
  • the configuration (hardware and software) for controlling the throttle opening degree of the expansion valve 13 constitutes the throttle opening degree control unit.
  • the discharge capacity control unit and the throttle opening degree control unit may be configured as separate devices with respect to the control device.
  • the operation of the heating system 1 of the present embodiment in addition to the operation in the normal heating operation mode in which the room is heated, the operation can be switched to the operation in the first defrosting operation mode or the second defrosting operation mode.
  • the first defrosting operation mode the evaporator 14 is defrosted while the heat pump cycle 10 is operated.
  • the second defrosting operation mode the evaporator 14 is defrosted while the operation of the heat pump cycle 10 is stopped.
  • the normal heating operation mode will be described.
  • the control device stores in advance in a ROM (storage circuit). It is started by executing a control process (control program).
  • control process the operation signal of the operation panel and the detection signal detected by the control sensor group described above are read. Based on the read operation signal and detection signal, the control states (specifically, control signals or control voltages output to the various control target devices) of the various control target devices connected to the output side of the control device are determined. Is done.
  • the control map stored in the ROM of the control device is referred to based on the hot water temperature setting signal from the operation panel and the outside air temperature Tam detected by the outside air temperature sensor. Determined. Specifically, the rotational speed (refrigerant discharge capacity) of the compressor 1 is determined to increase as the set temperature is increased by the hot water supply temperature setting signal and the outside air temperature Tam is decreased.
  • control signal output to the electric actuator of the electric expansion valve 13 is determined so that the high-pressure side refrigerant pressure Pd of the heat pump cycle 10 becomes the target high pressure.
  • the target high pressure is determined so that the coefficient of performance (COP) of the heat pump cycle 10 is maximized based on the outside air temperature Tam and the rotational speed of the compressor 11 with reference to the control map stored in the ROM of the control device. Is done.
  • the boiling temperature of the hot water flowing out from the water passage 12b of the water-refrigerant heat exchanger 12 is used by using a feedback control method or the like. Two is determined so as to approach the target heating temperature (for example, 80 ° C.-90 ° C.) set by the temperature setting switch.
  • control voltage output to the exhaust air blower fan 32a and the supply air blower fan 33a is determined so that the exhaust air blower fan 32a and the supply air blower fan 33a can exhibit a predetermined air blowing capability.
  • the exit temperature Tout of the warm water which flows out from the warm water channel 38 (the warm water which flows into the high temperature side heater core 35) Temperature) is determined to be a predetermined reference heating temperature KTh (in this embodiment, 40 ° C.-50 ° C.).
  • This reference heating temperature KTh is such that the supply air that has exchanged heat with the hot water that has flowed out of the hot water passage 38 in the high-temperature side heater core 35 becomes a temperature at which indoor heating can be appropriately realized (for example, 30 ° C.-40 ° C.). It is a value determined in.
  • control device outputs the control signal and the control voltage determined as described above to various devices to be controlled. Furthermore, the control device operates the heat pump cycle 10 so that the amount of heat Qt of hot water stored in the hot water storage tank 20 obtained from the detection value of the in-tank temperature sensor 42 becomes equal to or higher than a reference heat amount KQt described later.
  • control device reads the detection signal and the operation signal at a predetermined control cycle until the operation switch of the operation panel is turned off and the operation stop of the heating system 1 is requested.
  • Control routines such as state determination ⁇ output of control voltages and control signals to various devices to be controlled are repeated.
  • the high-temperature and high-pressure refrigerant discharged from the compressor 11 flows into the refrigerant passage 12a of the water-refrigerant heat exchanger 12, and dissipates heat to the hot water flowing through the water passage 12b. To do. Thereby, the hot water supplied through the water passage 12b is heated.
  • the high-pressure refrigerant that has flowed out of the refrigerant passage 12a flows into the electric expansion valve 13 and is decompressed until it becomes a low-pressure refrigerant.
  • the low-pressure refrigerant decompressed by the electric expansion valve 13 flows into the evaporator 14, absorbs heat from the exhaust air flowing out from the exhaust air ventilation path 32 of the supply air heating unit 30, and evaporates.
  • the refrigerant flowing out of the evaporator 14 is sucked into the compressor 11 and compressed again.
  • the relatively low temperature hot water supplied from the first water circulation pump 22 on the lower side of the hot water storage tank 20 is heated when it flows through the water passage 12 b of the water-refrigerant heat exchanger 12. Is done. Hot water that has been heated by the water-refrigerant heat exchanger 12 to a high temperature is stored above the hot water storage tank 20.
  • the warm water flows out from the warm water outlet on the upper side of the warm water passage 38.
  • the hot water flowing out from the hot water outlet of the hot water passage 38 is heated by the hot water supply water having a relatively high temperature above the hot water storage tank 20 and rises in temperature until reaching the reference heating temperature KTh.
  • the hot water whose temperature has been increased to the reference heating temperature KTh flows into the high temperature side heater core 35 and exchanges heat with the supply air flowing out from the ventilation heat exchanger 34 to dissipate heat. Thereby, the supply air flowing out from the ventilation heat exchanger 34 is heated until it reaches a temperature at which the room can be appropriately heated.
  • hot water stored in the hot water storage tank 20 (heat medium) is used as a heat source, and the air flowing out from the ventilation heat exchanger 34 is indirectly heated through the hot water.
  • the hot water whose temperature has decreased by releasing heat to the supply air at the high-temperature side heater core 35 is sucked into the second water circulation pump 39 and is pumped to the hot water inlet side of the hot water passage 38 disposed on the lower side in the hot water storage tank 20.
  • supply air (outside air) blown from the supply air blowing fan 33 a flows into the supply passage of the ventilation heat exchanger 34.
  • the supply air that has flowed into the supply air passage of the ventilation heat exchanger 34 is exchanged with the exhaust air (inside air) that is blown from the discharge air blowing fan 32a and flows through the discharge air passage of the ventilation heat exchanger 34.
  • the supply air that has flowed out of the ventilation heat exchanger 34 is further heated by the high-temperature heater core 35 and blown into each room that is a space to be heated through a duct (not shown), while it flows out of the ventilation heat exchanger 34.
  • the exhaust air thus exhausted is sent to the evaporator 14 side of the heat pump cycle 10 through the exhaust air ventilation path 32 and the duct 36.
  • the hot water heated by the water-refrigerant heat exchanger 2 of the heat pump cycle 10 can be stored in the hot water storage tank 20. Furthermore, each room
  • chamber interior can be implement
  • the operation in the first defrosting operation mode and the second defrosting operation mode is performed from the normal heating operation mode to the first defrosting operation mode or the first operation by executing the control process of the flowchart of FIG. 2 in the normal heating operation mode. 2 Defrosting operation mode is switched.
  • FIG. 2 is a control process executed as a subroutine with respect to the main routine of the control process executed in the normal heating operation mode. Further, each control step in FIG. 2 constitutes various function realizing units included in the control device.
  • step S1 it is determined whether or not it is necessary to perform a defrosting operation. Specifically, in step S1, the evaporator temperature Ts read in the main routine is less than or equal to a predetermined frosting reference temperature KTs1 (specifically, ⁇ 10 ° C.) and a predetermined time has elapsed. 14 determines that it is necessary to perform a defrosting operation due to frost formation. Therefore, control step S1 of this embodiment comprises the defrost necessity determination part.
  • a predetermined frosting reference temperature KTs1 specifically, ⁇ 10 ° C.
  • step S1 When it is determined in step S1 that it is not necessary to perform the defrosting operation, the process returns to the main routine, and the control process of the normal heating operation mode is executed. On the other hand, if it is determined in step S1 that it is necessary to perform the defrosting operation, the process proceeds to step S2, and the amount of heat Qt of hot water stored in the hot water storage tank 20 is equal to or greater than a predetermined reference heat amount KQt. It is determined whether or not.
  • the reference heat amount KQt is a value determined so that when the supply air is heated by the high temperature side heater core 35, the supply air can be raised to a temperature required for heating the space to be heated. is there.
  • step S2 When it is determined in step S2 that the heat quantity Qt of the hot water stored in the hot water storage tank 20 is not equal to or greater than the reference heat quantity KQt, the process proceeds to step S3, where the heat pump cycle 10 is operated and evaporated.
  • the control process of the 1st defrost operation mode which performs the defrost of the container 14 is performed.
  • step S3 the throttle opening of the electric expansion valve 13 is fully opened in step S3, and the process proceeds to step S4.
  • step S4 a so-called hot gas cycle in which the high-temperature refrigerant discharged from the compressor 11 flows into the evaporator 14 is configured to remove the evaporator 14. Frost can be done.
  • step S4 a detection signal of the evaporator temperature Ts is read, and the process proceeds to step S5.
  • step S5 it is determined whether or not the defrosting is completed. Specifically, in step S5, the defrosting is completed when the evaporator temperature Ts read in step S4 is equal to or higher than a predetermined defrosting reference temperature KTs2 (specifically, 0 ° C.). And return to the main routine. On the other hand, when the evaporator temperature Ts is lower than a predetermined defrost reference temperature KTs2 (specifically, 0 ° C.), it is determined that the defrost has not been completed, and the elapse of a predetermined control cycle is awaited. Return to step S4.
  • a predetermined defrost reference temperature KTs2 specifically, 0 ° C.
  • step S2 determines whether or not the heat quantity Qt of the hot water stored in the hot water storage tank 20 is equal to or greater than the reference heat quantity KQt.
  • the process proceeds to step S6, and the outlet side exhaust air read in step S2 It is determined whether or not the temperature Texo is equal to or higher than a predetermined reference exhaust air temperature KTexo (specifically, about 1 ° C.).
  • the reference exhaust air temperature KTexo performs defrosting of the evaporator 14 by guiding the exhaust air flowing out from the ventilation heat exchanger 34 to the evaporator 14 side where frost formation has occurred through the duct 36. It is a value determined so that
  • step S6 When it is determined in step S6 that the outlet side exhaust air temperature Texo is not equal to or higher than the reference exhaust air temperature KTexo, the process proceeds to step S3, and the control process of the first defrosting operation mode described above is executed. . On the other hand, when it is determined in step S6 that the outlet side exhaust air temperature Texo is equal to or higher than the reference exhaust air temperature KTexo, the process proceeds to step S7, and the evaporator is operated with the operation of the heat pump cycle 10 stopped. The control process of the 2nd defrosting operation mode which performs 14 defrosting is performed.
  • Step S7 that is, the operation of the compressor 11 is stopped
  • Step S8 is performed. Proceed to Even if the operation of the compressor 11 is stopped in this way, the heat quantity Qt of hot water stored in the hot water storage tank 20 is equal to or higher than the reference heat quantity KQt, and the outlet side exhaust air temperature Texo is the reference exhaust air temperature. Since it is equal to or greater than KTexo, the evaporator 14 can be defrosted by guiding the exhaust air to the evaporator 14 side via the duct 36.
  • step S8 a detection signal of the evaporator temperature Ts is read, and the process proceeds to step S9.
  • step S9 similarly to step S5, it is determined whether or not the defrosting is completed. If it is determined in step S9 that the defrosting has been completed, the process returns to the main routine. On the other hand, when it is determined in step S9 that the defrosting is not completed, the process proceeds to step S10.
  • step S10 as in step S2, it is determined whether or not the amount of heat Qt of hot water stored in the hot water storage tank 20 is equal to or greater than the reference amount of heat KQt. If it is determined in step S10 that the amount of heat Qt of hot water stored in the hot water storage tank 20 is not equal to or greater than the reference amount of heat KQt, the process proceeds to step S3, and the control process of the first defrosting operation mode described above is performed. Is executed.
  • step S10 when it is determined in step S10 that the heat quantity Qt of the hot water stored in the hot water storage tank 20 is equal to or greater than the reference heat quantity KQt, the process waits for the elapse of a predetermined control cycle as in step S5. Return to step S7.
  • the control step S1 determines that constitutes the defrost necessity determination unit that it is necessary to defrost the evaporator 14 and is stored in the hot water storage tank 20.
  • the operation in the second defrosting operation mode is executed.
  • the operation of the compressor 11 is stopped, so that the power consumption of the compressor 11 can be reduced. As a result, the energy consumption of the heat pump cycle 10 can be reduced.
  • the duct 36 that forms the ventilation path that guides the exhaust air that has flowed out of the ventilation heat exchanger 34 to the evaporator 14 side is provided, defrosting of the evaporator 14 is performed by the exhaust air that is relatively hot. It can be carried out. At this time, since the compressor 11 is stopped, the progress of frost formation in the evaporator 14 is suppressed, and efficient defrosting can be performed by the discharged air.
  • the hot water heater core 35 flows out of the ventilation heat exchanger 34 even if the compressor 11 is stopped.
  • the supply air taken into each room can be sufficiently heated up to a temperature required for heating each room.
  • the heat exchange capacity of the evaporator 14 is reduced due to frost formation while realizing sufficient heating in each room without increasing the energy consumption of the heat pump cycle 10. Can be suppressed.
  • the operation in the second defrosting operation mode is executed. Reliable defrosting of the evaporator 14 can be realized.
  • the heat quantity Qt of the hot water stored in the hot water storage tank 20 becomes lower than the reference heat quantity KQt.
  • the evaporator 14 can be defrosted by performing the operation in the first defrosting operation mode.
  • the heat of the exhaust air is also obtained in the normal heating operation mode. It can be effectively used to heat the hot water supply by causing the refrigerant to absorb heat. As a result, the thermal energy of the exhaust air can be suppressed from being released to the outside, and the thermal energy of the exhaust air can be effectively utilized for heating the room.
  • the hot water supply water may be operated without heating the room.
  • the operations of the exhaust air blowing fan 32a, the supply air blowing fan 33a, and the second water circulation pump 39 are stopped, and the evaporator 14 may be operated so that the refrigerant absorbs heat from the outside air and evaporates.
  • a ventilation path switching valve 40 is provided in the duct 36 as shown in the overall configuration diagram of FIG. 3 with respect to the first embodiment.
  • This ventilation path switching valve 40 discharges the exhausted air that flows out from the exhausted air ventilation path 32 of the supply air heating unit 30 (that is, the exhausted air that flows out of the ventilation heat exchanger 34) to the outside of the room without guiding it to the evaporator 14 side. It is a discharge part to be made.
  • the ventilation path switching valve 40 discharges the exhaust air flowing out from the ventilation heat exchanger 34 to the evaporator 14 side and the exhaust air flowing out from the ventilation heat exchanger 34 to the outside.
  • a ventilation path switching device configured to include an electric actuator including a servo motor that displaces the door. The operation of the electric actuator is controlled by a control signal output from the control device.
  • the control device when it is determined in the control step S6 described in FIG. 2 of the first embodiment that the outlet side exhaust air temperature Texo is lower than the reference exhaust air temperature KTexo, the control device The operation of the ventilation path switching valve 40 is controlled so that the exhausted air flowing out from the ventilation heat exchanger 34 is released to the outside of the room.
  • the control device when it is determined that the outlet side exhaust air temperature Texo is equal to or higher than the reference exhaust air temperature KTexo, the control device causes the exhaust air flowing out from the ventilation heat exchanger 34 to flow to the evaporator 14 side.
  • the operation of the switching valve 40 is controlled. That is, the control device controls the operation of the ventilation path switching valve 40 so as to guide the exhaust air that is equal to or higher than the reference exhaust air temperature KTexo to the evaporator 14 side in the second defrosting operation mode.
  • the example in which the operation of the ventilation path switching valve 40 is controlled so as to guide the exhaust air to the evaporator 14 side in the second defrosting operation mode has been described.
  • the outlet side When the exhaust air temperature Texo is equal to or higher than the refrigerant evaporation temperature of the evaporator 14 (specifically, the evaporator temperature Ts of the evaporator 14), the ventilation path is switched so as to guide the exhaust air to the evaporator 14 side.
  • the operation of the valve 40 may be controlled. Thereby, at the time of normal heating operation mode, it can utilize in order to make a refrigerant
  • a low temperature side heater core 44, a bypass passage 45, and three types of flow rate adjustment valves 46 are added to the second water circulation circuit 37 as shown in the overall configuration diagram of FIG. An example will be described.
  • the low temperature side heater core 44 circulates hot water that has flowed out of the high temperature side heater core 35 and reduced in temperature therein, and uses this hot water as a heat source to flow into the ventilation heat exchanger 34 (the supply air upstream of the ventilation heat exchanger 34). It is a heat exchanger for heating which heats the gas.
  • the inlet side of the second water circulation pump 39 is connected to the hot water outlet side of the low temperature side heater core 44.
  • the bypass passage 45 is a warm water flow path that guides the warm water flowing out from the high temperature side heater core 35 to the suction side of the second water circulation pump 39 by bypassing the low temperature side heater core 36.
  • the three types of flow rate adjusting valves 46 are arranged on the upstream side of the hot water flow of the low temperature side heater core 44.
  • the flow rate adjusting valve 46 adjusts the flow rate ratio between the hot water flow rate flowing into the low temperature side heater core 44 side and the warm water flow rate flowing into the bypass passage 46 side among the hot water flowing out from the high temperature side heater core 35, thereby reducing the low temperature side heater core.
  • the flow rate of hot water flowing into 44 is adjusted.
  • the flow rate adjusting valve 46 adjusts the flow rate of hot water flowing into the low temperature side heater core 44, thereby adjusting the heating capacity of the supply air in the low temperature side heater core 44. That is, the flow rate adjustment valve 46 of the present embodiment constitutes a heating capacity adjustment unit.
  • the flow rate adjusting valve 46 is an electric flow rate adjusting valve whose operation is controlled by a control signal output from the control device. Therefore, in this embodiment, the structure (hardware and software) which controls the action
  • the control device controls the operation of the flow rate adjusting valve 46 so that the entire flow rate of the hot water flowing out from the high temperature side heater core 35 flows into the bypass passage 45 side.
  • the control device controls the operation of the flow rate adjusting valve 46 so that the entire flow rate of the hot water flowing out from the high temperature side heater core 35 flows into the bypass passage 45 side.
  • the hot water that has been heated to a desired temperature can be stored in the hot water storage tank 20 by operating in exactly the same manner as in the first embodiment. Heating can be realized.
  • step S6 when it is determined in step S6 that the outlet side exhaust air temperature Texo is not equal to or higher than the reference exhaust air temperature KTexo, the process proceeds to step S61 and the low temperature side heater core 44 is heated. The capacity is increased and the process proceeds to step S7.
  • the control device controls the operation of the flow rate control valve 46 to increase the flow rate of hot water flowing into the low temperature side heater core 44 so that the outlet side exhaust air temperature Texo is equal to or higher than the reference exhaust air temperature KTexo. .
  • the temperature of the supply air flowing into the ventilation heat exchanger 34 is raised, and the temperature of the exhaust air heat exchanged with the supply air in the ventilation heat exchanger 34 can be reduced to the extent that defrosting of the evaporator 14 can be realized. Can be raised.
  • Other operations are the same as those in the first embodiment.
  • the heating system 1 of the present embodiment it is determined that it is necessary to defrost the evaporator 14, and the amount of hot water Qt stored in the hot water storage tank 20 is equal to or greater than the reference amount of heat KQt.
  • the second defrosting operation mode is executed without executing the operation in the first defrosting operation mode. Can do.
  • the frequency at which the compressor 11 is operated when the evaporator 14 is defrosted can be reduced more than the control process described in the first embodiment, and the consumption of the compressor 11 can be further reduced. Power can be reduced.
  • a predetermined predetermined flow rate of the outflowing hot water may be allowed to flow into the low-temperature side heater core 44 side.
  • the hot water whose temperature has been lowered by the low temperature side heater core 44 can be guided to the hot water passage disposed below the hot water storage tank 20. .
  • the water-refrigerant heat exchanger 12 can reduce the temperature of hot water supply (heat medium) on the lower side of the hot water storage tank 20 that exchanges heat with the refrigerant flowing into the electric expansion valve 13.
  • the flow of hot water heated in the water passage 12b of the water-refrigerant heat exchanger 12 of the heat pump cycle 10 is branched, one of the branched hot water is stored in the hot water storage tank 20, and the other hot water is heated to a high temperature. It may be allowed to flow into the side heater core 35. In this case, since the heating capability of the supply air in the high-temperature side heater core 35 is reduced during the second defrosting operation mode, the operation in the second dehumidification operation mode is executed when the indoor temperature is sufficiently high. May be.
  • the ventilation path forming member is not limited to this.
  • a housing of the heat pump unit in which a ventilation hole for guiding the exhaust air flowing out from the ventilation heat exchanger 34 to the evaporator 14 side is formed. It functions as a ventilation path forming member.
  • the evaporator temperature Ts is ⁇ 10 ° C. or lower when determining whether or not it is necessary to perform the defrosting operation in the control step S1 constituting the defrosting necessity determining unit. When a predetermined time has elapsed, it is determined that the defrosting operation needs to be performed.
  • the defrost necessity determination unit of the above-described embodiment determines that it is necessary to perform a defrosting operation after frost formation has actually occurred in the evaporator 14.
  • the defrost necessity determination unit in the above-described embodiment may be configured with a frost determination unit that determines that frost formation has occurred in the evaporator 14.
  • the defrost necessity determination unit may determine that it is necessary to perform the defrosting operation before the evaporator 14 is layered. For example, when the evaporator temperature Ts becomes 0 ° C. or lower, it may be determined that it is necessary to perform the defrosting operation without waiting for the elapse of a predetermined time.
  • the defrost necessity determination unit may be configured with a frost condition determination unit that determines conditions under which frost formation may occur.
  • the circuit configuration of the second water circulation circuit 37 a circuit configuration in which the hot water outlet of the high temperature side heater core 35 is connected to the suction port of the second water circulation pump 39 is employed.
  • the circuit configuration of the second water circulation circuit 37 is not limited to this.
  • a heater that heats an object to be heated using hot water flowing out from the high temperature side heater core 35 as a heat source may be disposed between the hot water outlet of the high temperature side heater core 35 and the suction port of the second water circulation pump 39.
  • a heater that requires a heat source in a temperature range lower than that of the high-temperature side heater core 35 as such a heater.
  • a panel heater or a towel warmer that requires a heat source in a temperature range of about 20 ° C. to 40 ° C. can be employed.
  • a similar heater may be disposed on the downstream side of the high-temperature side heater core 35 and on the upstream side of the low-temperature side heater core 44.
  • the exhaust air blower fan 32 a is arranged on the most upstream side of the exhaust air flow path 32, and the supply air blower fan 33 a is arranged on the most upstream side of the supply air flow path 33.
  • the arrangement of the exhaust air blowing fan 32a and the supply air blowing fan 33a is not limited to this.
  • the exhaust air blower fan 32 a may be disposed on the most upstream side of the exhaust air flow path 32, and the supply air blower fan 33 a may be disposed on the most downstream side of the supply air flow path 33.
  • two ventilation fans can be arrange
  • the sensible heat exchanger configured by stacking a plurality of metal plates having excellent heat conductivity as the ventilation heat exchanger 34 and exchanging heat between the exhaust air and the supply air. What was configured as was adopted. However, you may employ
  • the heating capacity adjusting unit is not limited thereto.
  • the heating capacity adjusting unit may be configured using a normal two-type flow rate adjusting valve.
  • a hot water branching portion for branching the flow of hot water is disposed, and at least one of the hot water passage and the bypass passage 46 extending from the hot water branching portion to the low temperature side heater core 44 is provided.
  • the flow rate regulating valve may be arranged.
  • Steps S1-S10 and S61 in each of the above-described embodiments may be components such as a control unit that performs the function of each step.

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  • Combustion & Propulsion (AREA)
  • Steam Or Hot-Water Central Heating Systems (AREA)
  • Central Heating Systems (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
PCT/JP2014/000576 2013-02-08 2014-02-04 暖房システム WO2014122922A1 (ja)

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CN104879819A (zh) * 2015-06-02 2015-09-02 太原绿佳环保开发有限公司 一种利用直热式超导暖气片的空气能供暖***

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JP2016114319A (ja) * 2014-12-16 2016-06-23 株式会社デンソー 暖房システム
WO2017163337A1 (ja) 2016-03-23 2017-09-28 三菱電機株式会社 ヒートポンプ式暖房装置
DE102017107394A1 (de) * 2017-04-06 2018-10-11 Stiebel Eltron Gmbh & Co. Kg Wärmepumpenanlage
DE102017003355A1 (de) * 2017-04-06 2018-10-11 Stiebel Eltron Gmbh & Co. Kg Wärmepumpenanlage
WO2019064335A1 (ja) * 2017-09-26 2019-04-04 三菱電機株式会社 冷凍サイクル装置
WO2019155614A1 (ja) * 2018-02-09 2019-08-15 三菱電機株式会社 空気調和装置、空調システム及び熱交換ユニット
EP3757481B1 (de) * 2018-02-22 2024-06-26 Mitsubishi Electric Corporation Klimaanlage
CN115962575A (zh) * 2022-12-22 2023-04-14 珠海格力电器股份有限公司 一种多功能热水机防冻控制方法、装置及相关设备

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JPS6162743A (ja) * 1984-09-04 1986-03-31 Matsushita Seiko Co Ltd ヒ−タ付熱交換換気装置
JP3297657B2 (ja) * 1999-09-13 2002-07-02 株式会社デンソー ヒートポンプ式給湯器
JP2002317990A (ja) * 2001-04-18 2002-10-31 Daikin Ind Ltd 調湿換気装置
JP2010107059A (ja) * 2008-10-28 2010-05-13 Mitsubishi Electric Corp 冷凍空調装置
JP2011202899A (ja) * 2010-03-26 2011-10-13 Tokyo Electric Power Co Inc:The 除霜装置
JP2012225596A (ja) * 2011-04-21 2012-11-15 Panasonic Corp 暖房用ヒートポンプシステム

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JPS6162743A (ja) * 1984-09-04 1986-03-31 Matsushita Seiko Co Ltd ヒ−タ付熱交換換気装置
JP3297657B2 (ja) * 1999-09-13 2002-07-02 株式会社デンソー ヒートポンプ式給湯器
JP2002317990A (ja) * 2001-04-18 2002-10-31 Daikin Ind Ltd 調湿換気装置
JP2010107059A (ja) * 2008-10-28 2010-05-13 Mitsubishi Electric Corp 冷凍空調装置
JP2011202899A (ja) * 2010-03-26 2011-10-13 Tokyo Electric Power Co Inc:The 除霜装置
JP2012225596A (ja) * 2011-04-21 2012-11-15 Panasonic Corp 暖房用ヒートポンプシステム

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104879819A (zh) * 2015-06-02 2015-09-02 太原绿佳环保开发有限公司 一种利用直热式超导暖气片的空气能供暖***
CN104879819B (zh) * 2015-06-02 2018-10-30 太原绿佳环保开发有限公司 一种利用直热式超导暖气片的空气能供暖***

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JP5983451B2 (ja) 2016-08-31
JP2014152985A (ja) 2014-08-25

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