WO2014103013A1 - Système de pompe à chaleur - Google Patents

Système de pompe à chaleur Download PDF

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Publication number
WO2014103013A1
WO2014103013A1 PCT/JP2012/084070 JP2012084070W WO2014103013A1 WO 2014103013 A1 WO2014103013 A1 WO 2014103013A1 JP 2012084070 W JP2012084070 W JP 2012084070W WO 2014103013 A1 WO2014103013 A1 WO 2014103013A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
hot water
heat exchanger
water supply
freezing
Prior art date
Application number
PCT/JP2012/084070
Other languages
English (en)
Japanese (ja)
Inventor
由之 渡辺
Original Assignee
三菱電機株式会社
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.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2012/084070 priority Critical patent/WO2014103013A1/fr
Publication of WO2014103013A1 publication Critical patent/WO2014103013A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
    • F24D19/1051—Arrangement or mounting of control or safety devices for water heating systems for domestic hot water
    • F24D19/1054—Arrangement or mounting of control or safety devices for water heating systems for domestic hot water the system uses a heat pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D11/00—Central heating systems using heat accumulated in storage masses
    • F24D11/02—Central heating systems using heat accumulated in storage masses using heat pumps
    • F24D11/0214—Central heating systems using heat accumulated in storage masses using heat pumps water heating system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F25B13/00—Compression machines, plants or systems, with 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • 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
    • F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost
    • 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
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • 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
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2700/11—Sensor to detect if defrost is necessary

Definitions

  • the present invention relates to a heat pump system including a plurality of utilization units including a hot water supply utilization unit that supplies cold water or hot water.
  • Patent Document 1 a heat pump water heater that heats or cools water using a heat pump cycle has been proposed (see, for example, Patent Document 1).
  • a heat pump water heater has a heat exchanger that performs heat exchange between a refrigerant and water, and water is heated by heat radiation from the refrigerant.
  • Patent Document 1 when it is determined that the flow path is blocked by freezing, the rotation speed of the compressor is reduced, the amount of air blown by the blower is decreased, the opening area of the throttle device is increased, or It has been proposed that the amount of water delivered be increased.
  • Patent Documents 2 and 3 disclose a heat pump system including a utilization unit that performs heat exchange between air and a refrigerant, and a utilization unit that performs heat exchange between water and a refrigerant.
  • a hot water supply device in a combined air conditioning hot water supply device having such an air conditioner and a hot water supply device, normally, when hot water is generated, water is circulated to the hot water supply device side of the heat exchanger, and hot water is not generated. In some cases, water does not circulate in the heat exchanger.
  • the hot water supply device may freeze. Therefore, in the combined systems shown in Patent Documents 2 and 3, when it is determined that freezing has occurred on the hot water supply apparatus side, it is conceivable to reduce the number of rotations of the compressor. However, if the operation of the compressor is changed, there is a problem that the operation of other utilization units is affected. In addition, when the hot water supply heat exchanger is damaged due to freezing, there is a problem that water on the water flow path side of the hot water supply heat exchanger flows into the refrigerant flow path side, which may cause a problem in the entire system.
  • the present invention has been made to solve the above-described problems, and it is possible to prevent the hot water heat exchanger from freezing and to prevent problems due to freezing from extending to the entire system.
  • the object is to provide a heat pump system.
  • a heat pump system includes a heat source side unit having a compressor and a heat source side heat exchanger, and a heat exchanger for hot water supply that is connected in parallel to the heat source side unit and performs heat exchange between water and a refrigerant.
  • a heat pump system comprising a compressor, a heat source side heat exchanger, and a refrigerant cycle circuit for circulating a refrigerant through the plurality of usage units.
  • a flow controller for controlling the flow of the refrigerant to the use unit, a freezing detection means for detecting the occurrence of freezing in the hot water supply heat exchanger, and a freezing in the hot water supply heat exchanger in the freezing detection means When judged, it is characterized by comprising a shutoff control means for controlling the flow controller so as to block the flow of the refrigerant to the hot water supply heat exchanger.
  • the flow of the refrigerant to the hot water supply heat exchanger is blocked by the flow controller, thereby In addition to preventing the heat exchanger from freezing, it is possible to prevent problems due to freezing from occurring to the entire system.
  • FIG. 1 is a refrigerant circuit diagram showing Embodiment 1 of the heat pump system of the present invention.
  • a heat pump system 100 in FIG. 1 is a system capable of both cooling operation and heating operation by switching a flow path using a refrigeration cycle circuit.
  • a plurality of use units (air-conditioning use units 30a to 30d, hot water supply use unit 40a) and control means 70 are provided.
  • the heat pump system 100 is a composite system including air-conditioning use units 30a to 30d as air conditioners and a hot-water supply use unit 40a as a hot water supply device.
  • refrigerant flowing through the refrigeration cycle circuit is natural refrigerants such as carbon dioxide, carbon, and helium, refrigerants that do not contain chlorine, such as alternative refrigerants such as HFC410A, HFC407C, and HFC404A, or fluorocarbons such as R22 and R134a. Any of the refrigerants may be used.
  • the heat source side unit 10 includes a compressor 11, a first flow path switch 12, a heat source side heat exchanger 13, an accumulator 14, check valves 15a to 15d, and the like.
  • the compressor 11 sucks and compresses the refrigerant to bring it into a high temperature / high pressure state.
  • the compressor 11 is driven by an inverter circuit, and the compressor rotational speed is controlled and the capacity is controlled by power source frequency conversion by the inverter circuit.
  • the compressor 11 may be of any type such as reciprocating, rotary, scroll, screw, etc., and may be a variable speed or a fixed speed.
  • the first flow path switch 12 switches between the heating flow path and the cooling flow path in accordance with switching of the operation mode of the cooling operation or the heating operation, and includes, for example, a four-way valve.
  • the first flow path switch 12 connects the heat source side heat exchanger 13 and the accumulator 14 and connects the discharge side of the compressor 11 and the check valve 15c. Let Then, the refrigerant discharged from the compressor 11 flows toward the use units 30a to 30d.
  • the first flow path switching unit 12 connects the check valve 15a and the accumulator 14, and the discharge side of the compressor 11 and the heat source side heat exchanger 13 Connect.
  • the refrigerant discharged from the compressor 11 flows to the heat source side heat exchanger 13 side.
  • a four-way valve is used as the 1st flow path switching device 12
  • the heat source side heat exchanger 13 performs heat exchange between the refrigerant and the air (outside air).
  • a heat transfer pipe that allows the refrigerant to pass therethrough, and a heat transfer area between the refrigerant that flows through the heat transfer pipe and the outside air. It has the structure provided with the fin for enlarging.
  • the heat source side heat exchanger 13 may be of any other system such as a water-cooled type, for example, as long as the refrigerant exchanges heat with another fluid.
  • the heat source side heat exchanger 13 is connected to the first flow path switch 12 and the check valves 15b and 15d, respectively.
  • the heat source side heat exchanger 13 functions as an evaporator that evaporates and vaporizes the refrigerant during the heating operation and the heating main operation, and functions as a condenser that condenses and liquefies the refrigerant during the cooling only operation and the cooling main operation. .
  • the accumulator 14 is provided on the suction side of the compressor 11 and stores refrigerant flowing in from the heat source side heat exchanger 13 or the relay machine 20.
  • the compressor 11 sucks and compresses the gas refrigerant among the refrigerant stored in the accumulator 14. Thereby, the liquid back of the refrigerant
  • a U-shaped tube is provided in the accumulator 14.
  • the liquid refrigerant accumulates in the lower part of the container, and the gas-rich refrigerant that has flowed in from the upper opening of the U-shaped tube is sucked into the compressor 11 from the accumulator 14.
  • the liquid back of the compressor 11 can be temporarily prevented until the transient liquid or the gas-liquid two-phase refrigerant is accumulated in the accumulator 14 and overflows. The effect of maintaining reliability can be obtained.
  • the check valves 15a to 15d are connected to the refrigerant path that flows out to the plurality of usage units 30a to 30d and the heat source side unit 10 in either case of the heating flow path or the cooling flow path switched by the first flow path switch 12.
  • the refrigerant path into which the refrigerant flows is set in a certain direction.
  • the check valve 15 a is located between the first flow path switch 12 and the low pressure pipe (liquid pipe) 3, and allows the refrigerant flow from the low pressure pipe 3 to the first flow path switch 12. Allow.
  • the check valve 15 b is located between the low pressure pipe 3 and the heat source side heat exchanger 13 and allows the refrigerant flow from the low pressure pipe 3 toward the heat source side heat exchanger 13.
  • the check valve 15 c is located between the first flow path switch 12 and the high pressure pipe (gas pipe) 2 and allows the refrigerant flow from the first flow path switch 12 to the high pressure pipe 2.
  • the check valve 15 d is located between the heat source side heat exchanger 13 and the high pressure pipe 2 and allows the refrigerant flow from the heat source side heat exchanger 13 toward the high pressure pipe 2.
  • the relay machine (diversion controller) 20 divides the refrigerant flowing out from the heat source side unit 10 into a plurality of utilization units 30a to 30d, 40a.
  • the heat source side unit 10 and the relay machine 20 are composed of the high-pressure pipe 2 and the low pressure. It is connected via a tube 3.
  • a high-pressure refrigerant flows in the high-pressure pipe 2 from the heat source side unit 10 side to the relay 20 side, and a low-pressure refrigerant in the low-pressure pipe 3 has a plurality of heat sources from the relay machine 20 side compared to the refrigerant flowing in the high-pressure pipe 2. It means flowing to the side unit 10 side.
  • the relay machine 20 and each of the usage units 30a to 30d, 40a are connected via a liquid pipe and a gas pipe, and the relay machine 20 changes the flow of the refrigerant according to the operation mode of each of the usage units 30a to 30d, 40a. It has a function to switch.
  • the relay machine 20 includes a gas-liquid separator 21, a second flow path switch 22, heat exchangers 26 and 27 between refrigerants, expansion devices 28 and 29, and the like.
  • the gas-liquid separator 21 separates the refrigerant flowing from the heat source side unit 10 via the high pressure pipe 2 into a gas refrigerant and a liquid refrigerant.
  • the gas phase part from which the gas refrigerant flows out of the gas-liquid separator 21 is connected to the second flow path switch 22.
  • the liquid phase part from which the liquid refrigerant flows out of the gas-liquid separator 21 is connected to the first inter-refrigerant heat exchanger 26.
  • the second flow path switch 22 switches the refrigerant flow by opening and closing according to the operation mode of each of the usage units 30a to 30d, 40a.
  • the second flow path switching unit 22 switches the first on-off valves 23a to 23e and the second on-off valves 24a to 24a. 24e.
  • the first on-off valves 23a to 23e have one end connected to the gas-liquid separator 21 and the other end connected to the refrigerant flow path side of each of the usage units 30a to 30d and 40a.
  • One end of each of the second on-off valves 24a to 24e is connected to the low-pressure pipe 3, and the other end is connected to one end side of the refrigerant flow path of each of the usage units 30a to 30d.
  • the opening and closing of the first on-off valves 23a to 23e and the second on-off valves 24a to 24e are independently controlled based on the operation modes of the usage units 30a to 30d and 40a. Specifically, during the heating operation of the usage units 30a to 30d and 40a, the first on / off valves 23a to 23e are opened and the second on / off valves 24a to 24e are closed. Then, the refrigerant flows from the gas-liquid separator 21 side to the use units 30a to 30d and 40a side via the first on-off valves 23a to 23e.
  • the first on / off valves 23a to 23e are closed and the second on / off valves 24a to 24e are opened. Then, the refrigerant flows from the use units 30a to 30d, 40a side to the low pressure pipe 3 side.
  • a three-way valve or the like may be used, for example.
  • the repeater 20 has check valves 25a and 25b connected to the other ends of the plurality of usage units 30a to 30d and 40a, respectively.
  • the check valves 25a and 25b ensure that the refrigerant flows in a predetermined direction when the refrigerant flow path is changed in accordance with the switching of the operation mode.
  • the check valves 25a and 25b may switch the flow path more reliably using valve means such as an electromagnetic valve, or the check valves 25a and 25b may not be provided.
  • the first inter-refrigerant heat exchanger 26 is provided in a connecting pipe between the gas-liquid separator 21 and the first expansion device 28, and the refrigerant flowing out of the gas-liquid separator 21 and the second inter-refrigerant heat exchange are exchanged. Heat exchange is performed with the refrigerant flowing out of the vessel 27.
  • the second inter-refrigerant heat exchanger 27 performs heat exchange between the refrigerant flowing out from the first expansion device 28 and the refrigerant flowing out from the second expansion device 29.
  • the first expansion device 28 is provided in a connecting pipe between the first inter-refrigerant heat exchanger 26 and the second inter-refrigerant heat exchanger 27, controls the opening degree based on the operation mode, and gas-liquid separation The flow rate of refrigerant flowing from the vessel 21 and the pressure of the refrigerant are adjusted.
  • the second expansion device 29 is provided in a bypass pipe on the upstream side of the second inter-refrigerant heat exchanger 27, and adjusts the refrigerant flow rate and the refrigerant pressure by controlling the opening degree.
  • the plurality of usage units 30a to 30d and 40a are air conditioning usage units 30a to 30d that harmonize air by heat exchange between air and refrigerant, and water cooling and heating by heat exchange between water (liquid medium) and refrigerant. And a hot water supply use unit 40a.
  • the air conditioning usage units 30a to 30d have air conditioning heat exchangers 31a to 31d and expansion devices 32a to 32d, respectively, and the hot water supply usage unit 40a has a hot water supply heat exchanger 41a and expansion device 42a. ing.
  • the air conditioner heat exchangers 31a to 31d exchange heat between the air in the air-conditioning target space and the refrigerant, and function as an evaporator that evaporates and vaporizes the refrigerant during the heating operation, and the refrigerant during the cooling operation. It functions as a condenser that condenses and liquefies.
  • the hot water supply heat exchanger 41a performs heat exchange between water and the refrigerant, and has a refrigerant flow path through which the refrigerant flows and a water side flow path through which the water flows.
  • the hot water supply heat exchanger 41a functions as an evaporator that evaporates and vaporizes the refrigerant when hot water is generated, and functions as a condenser that condenses and liquefies the refrigerant when generated cold water.
  • the expansion devices 32a to 32d and 42a are composed of, for example, electronic expansion valves that can change the opening, and are connected in series to the heat exchangers 31a to 31d and 41a, respectively.
  • the indoor unit side expansion devices 32a to 32d function as pressure reducing valves and expansion valves, and adjust the pressure of the refrigerant passing through the heat exchangers 31a to 31d and 41a.
  • flow controllers 43a and 44a for controlling the flow of the refrigerant are provided.
  • the flow controllers 43a and 44a are composed of, for example, on-off valves. When the flow controllers 43 and 44 are closed, the flow of the refrigerant to the hot water supply heat exchanger 41a is blocked.
  • the operations of the flow controllers 43a and 44a are controlled by the control means 70.
  • the distribution controllers 43a and 44a may be provided in the hot water supply use unit 40a, may be provided on the relay machine 20 side, or may be provided with the relay machine 20 and the hot water supply. It may be provided on a pipe connecting the use unit 40a.
  • the hot water supply use unit 40a is provided with a refrigerant inlet temperature detecting means 61a, a refrigerant outlet temperature detecting means 62a, a water inlet temperature detecting means 63a, a water outlet temperature detecting means 64a, and a water amount detecting means 65.
  • the refrigerant inlet temperature detection means 61a detects the temperature of the refrigerant flowing into the hot water supply heat exchanger 41a as the refrigerant inlet temperature TH11
  • the refrigerant outlet temperature detection means 62a is the temperature of the refrigerant flowing out of the hot water supply heat exchanger 41a. Is detected as the refrigerant outlet temperature TH12.
  • the water inlet temperature detecting means 63a detects the temperature of the water flowing into the hot water supply heat exchanger 41a as the water inlet temperature TH21, and the water inlet temperature detecting means 64a is the temperature of the water flowing out of the hot water supply heat exchanger 41a. Is detected as the water outlet temperature TH22.
  • the water amount detection means 65 is comprised, for example from the flowmeter provided in the water flow path side.
  • the water amount detecting means 65 may be any method as long as it detects the amount of water.
  • a pressure gauge is installed before and after the hot water supply heat exchanger 41a, and the flow rate is determined from the differential pressure before and after the hot water supply heat exchanger 41a. May be converted.
  • a flow switch or the like may be used in addition to the flow rate conversion from the differential pressure before and after the flow meter and the hot water supply heat exchanger 41a. Furthermore, the flow rate with respect to the operation state (capacity) of the circulation pump 52 may be measured in advance, and the flow rate may be measured from the operation state of the circulation pump 52.
  • FIG. 2 is a schematic diagram showing an example of the hot water supply load 50 of FIG.
  • the case where only the distribution controller 44b is provided in the heat exchanger 41a for hot water supply is illustrated.
  • 2 includes, for example, a water storage tank 51, a circulation pump 52, and a circulation pipe 53.
  • the water storage tank 51 stores hot water or cold water heat-exchanged in the hot water supply heat exchanger 41a, and is connected to the water flow path side of the hot water supply heat exchanger 41a by a circulation pipe 53.
  • a water distribution pipe (water supply pipe) (not shown) is connected to the lower part of the water storage tank 51.
  • the circulation pipe 53 is composed of this copper pipe, stainless steel pipe, steel pipe, vinyl chloride meter pipe, and the like.
  • water circulates and is stored in the water storage tank 51 is illustrated as the hot water supply load 50, for example, water flowing in the circulation pipe 53 is used as a heat medium as in a chiller device. Also good.
  • a heat exchanger that performs heat exchange between air and the heat medium (water) may be arranged.
  • water not only water but also antifreeze can be used as the heat medium.
  • each heat source side unit 10 is connected to the air conditioning use units 30a to 30d and the hot water supply use unit 40a via the high pressure pipe 2, the low pressure pipe 3, and the relay unit 20.
  • a refrigeration cycle circuit is configured.
  • the heat pump system 100 has a configuration that can be operated in four operation modes by switching the refrigerant flow paths of the first flow path switch 12 and the second flow path switch 22.
  • the heat pump system 100 includes a cooling only operation mode in which all of the usage units 30a to 30d perform a cooling operation, a heating only operation mode in which all of the usage units 30a to 30d perform a heating operation, and usage units 30a to 30d. Cooling operation or heating operation can be selected every 30d, cooling main operation mode with larger cooling load, cooling operation or heating operation can be selected for each usage unit 30a-30d, and heating main operation mode with larger heating load is there.
  • the first flow path switch 12 is switched so that the refrigerant discharged from the compressor 11 flows into the heat source side heat exchanger 13 side. Further, in the second flow path switch 22, the first on-off valves 23a to 23e are closed, and the second on-off valves 24a to 24e are opened.
  • the refrigerant sucked into the compressor 11 is compressed and discharged as a high-temperature and high-pressure gas refrigerant.
  • the gas refrigerant discharged from the compressor 11 flows into the heat source side heat exchanger 13 via the first flow path switch 12.
  • the gas refrigerant that has flowed into the heat source side heat exchanger 13 becomes low-temperature and high-pressure liquid refrigerant that is condensed and liquefied by exchanging heat with outdoor air in the heat source side heat exchanger 13. Thereafter, the liquid refrigerant passes through the check valve 15a and flows into the relay machine 20.
  • the liquid refrigerant that has flowed into the relay 20 is cooled by the first inter-refrigerant heat exchanger 26 via the gas-liquid separator 21 to increase the degree of supercooling, until the first expansion device 28 becomes an intermediate-pressure liquid refrigerant. Squeezed. Thereafter, the liquid refrigerant is distributed to the liquid refrigerant flowing to the liquid pipe side and the liquid refrigerant flowing to the second expansion device 29 side.
  • the liquid refrigerant flowing out of the second inter-refrigerant heat exchanger 27 is throttled to a low pressure by the check valve 25b throttling devices 32a to 32d and 42b and flows into the heat exchangers 31a to 31d and 41a, respectively.
  • the liquid refrigerant that has flowed into the air conditioner heat exchangers 31a to 31d exchanges heat with the air in the target space and is evaporated and gasified. At this time, the air-conditioning use units 30a to 30d are cooled. Similarly, the liquid refrigerant flowing into the hot water supply heat exchanger 41a exchanges heat with water circulating in the hot water supply load 50, and is evaporated and gasified. At this time, the water circulating through the hot water supply load 50 is cooled, and cold water is generated.
  • the refrigerant that has flowed out of each of the usage units 30a to 30d, 40a passes through the second on-off valves 24a, 24b and the low-pressure pipe 3 of the second flow path switch 22 and flows into the heat source side unit 10 side.
  • the liquid refrigerant distributed to the second expansion device 29 side in the second inter-refrigerant heat exchanger 27 is throttled to a low pressure in the second expansion device 29, and the second inter-refrigerant heat exchanger 27 and the first inter-refrigerant heat.
  • the exchanger 26 exchanges heat with the liquid refrigerant flowing from the gas-liquid separator 21 and is evaporated and gasified.
  • the refrigerant flowing out from the first inter-refrigerant heat exchanger 26 merges with the refrigerant flowing out from each of the usage units 30a to 30d, 40a, and flows into the heat source side unit 10 through the low-pressure pipe 3.
  • the gas refrigerant that has flowed into the heat source side unit 10 passes through the check valve 15 a and the first flow path switch 12, flows into the accumulator 14, and is sucked and compressed again by the compressor 11.
  • the hot water supply load 50 is controlled so that water is circulated and heat exchange is performed when a predetermined condition is reached. Therefore, when there is no need to generate cold water in the hot water supply load 50, the circulation pump 52 is stopped. For this reason, although the circulation pump 52 is moving, since the circulation pump 52 does not move when it is not used, water may stay. When the low-temperature refrigerant flows into the hot water supply heat exchanger 41a in a state where water is retained in the hot water supply heat exchanger 41a, the hot water supply heat exchanger 41a may be frozen. In view of this, the control means 70 shown below controls the refrigerant flow to the hot water supply use unit 40a when the occurrence of freezing is detected.
  • FIG. 3 is a functional block diagram showing an example of the control means 70.
  • the control means 70 is composed of, for example, a microcomputer, a DSP (digital signal processor) provided in the hot water supply utilization unit 40a.
  • the control means 70 of FIG. 3 controls the flow of the refrigerant to the hot water supply heat exchanger 41a when the freezing occurs in the hot water supply heat exchanger 41a.
  • Means 72 are provided.
  • the freezing detection means 71 detects that freezing has occurred in the hot water supply heat exchanger 41a using the refrigerant inlet temperature TH11 and the water inlet temperature TH21, and has a wall surface temperature calculation means 71a and a freezing determination means 71b. is doing.
  • the wall surface temperature calculating means 71a calculates the wall surface temperature Tw of the hot water supply heat exchanger 41a using the refrigerant inlet temperature TH11 and the water inlet temperature TH21.
  • various methods can be used as a method of detecting the wall surface temperature Tw.
  • the wall surface temperature Tw is calculated using the refrigerant inlet temperature TH11 at which the refrigerant temperature is lowest, but the refrigerant outlet temperature TH12 may be used.
  • the freezing determining means 71b determines whether or not freezing has occurred in the hot water supply heat exchanger 41a based on the wall surface temperature Tw detected by the wall surface temperature calculating means 71a. Specifically, the freezing determination means 71b determines that freezing has occurred when the wall surface temperature Tw is lower than a predetermined set temperature Tw0 (Tw ⁇ Tw0).
  • the set temperature Tw0 for the lowest flow rate assumed in the freezing determination means 71b may be set in advance.
  • the freezing determination means 71b has a predetermined value according to the water inlet temperature TH21 and the water amount V. It has a function of setting the set temperature Tw0.
  • FIG. 4 is a graph showing the relationship between the time at which water begins to freeze and the wall surface temperature (frozen wall surface temperature) Tw.
  • it means that freezing starts when the wall surface temperature Tw and time in the lower region of the curve are reached (in the case of the water inlet temperature TH21a, the hatched portion in FIG. 4),
  • the case where the flow velocity of the water is a predetermined flow velocity (flow rate) and the water inlet temperatures TH21a, TH21b, TH21c (TH21a> TH21b> TH21c) of three different waters is illustrated. As shown in FIG.
  • the freezing determination means 71b stores a table as shown in FIG. 4, and the freezing determination means 71b sets a predetermined set temperature Tw0 according to the water inlet temperature TH21.
  • the freezing determination means 71b has a function of setting the set temperature Tw0 by the amount of water V flowing into the hot water supply heat exchanger 41a detected by the water amount detection means 65. That is, the time and the frozen wall surface temperature shown in FIG. 4 vary depending on the amount of water, and the wall surface temperature at which freezing tends to decrease as the amount of water increases.
  • the table of different water inlet temperature TH21 like FIG. 4 is memorize
  • the preset temperature Tw0 is set by interpolating the data memorize
  • the freezing determination means 71b of FIG. 3 determines that freezing has occurred when the wall surface temperature Tw is lower than the predetermined set temperature Tw0 for a set period Tref or longer. Thereby, it is possible to prevent erroneous detection of freezing when the wall surface temperature Tw instantaneously becomes lower than the set temperature Tw0. Furthermore, the freezing determination means 71b has a function of setting the set period Tref according to the water amount V as with the set temperature Tw0 described above. Specifically, in the freezing determination means 71b, for example, the relationship between the water amount V and the setting period Tref that the setting period Tref becomes longer as the amount of water increases is stored in advance as a table. The set period Tref is set using the detected water amount V. In addition, you may make it determine the freezing determination means 71b by the integrated value (area of the oblique line in FIG. 4) of water inlet temperature TH21 and time.
  • the shutoff control means 72 controls the flow controllers 43a and 44a so as to shut off the flow of refrigerant to the hot water supply heat exchanger 41a. Control.
  • the flow of the refrigerant to the hot water supply heat exchanger 41a is stopped to exist on the water flow path side of the hot water supply heat exchanger 41a. Water freezing can be surely prevented. Even if the hot water supply heat exchanger 41a is damaged due to freezing or the like, the influence on the entire system can be minimized.
  • water does not always circulate on the water flow path side of the hot water supply heat exchanger 41a. For this reason, when water is not circulated during defrosting operation or the circulation rate is small, if a low-temperature refrigerant flows into the hot water supply heat exchanger 41a, the hot water supply heat exchanger 41a freezes and functions. No longer. Furthermore, when the hot water supply heat exchanger 41a is frozen, the hot water supply heat exchanger 41a or the expansion device 42a may be damaged, and water on the water flow path side may enter the refrigerant flow path side. Then, since water flows into the entire refrigerant circuit, when the system is restored, it is necessary to replace not only the hot water supply heat exchanger 41a but also the entire system.
  • the shutoff control means 72 closes the flow controllers 43a and 44a so as to shut off the flow of the refrigerant to the hot water supply heat exchanger 41a.
  • the occurrence of freezing in the hot water supply heat exchanger 41a can be reliably prevented.
  • the refrigerant staying in the hot water supply heat exchanger 41a that is not in operation is drawn by closing the flow controllers 43a and 44a.
  • the hot water supply heat exchanger 41a can be prevented from being damaged and water flowing into the refrigerant circuit, so that the hot water supply heat exchanger 41a can be damaged without replacing the entire system when the entire system is restored. The damage caused by can be minimized.
  • FIG. 5 is a flowchart showing an operation example of the heat pump system 100 of FIG. 1, and an operation example of the heat pump system 100 will be described with reference to FIGS.
  • the water inlet temperature TH21 is detected by the refrigerant inlet temperature detector 61a
  • the refrigerant inlet temperature TH11 is detected by the refrigerant inlet temperature detector 61a (step ST1).
  • the refrigerant inlet temperature TH11 is 0 ° C. or lower (step ST2)
  • the set temperature Tw0 is set according to the water inlet temperature TH21 and the water amount V, and it is determined whether or not the wall surface temperature Tw is higher than the set temperature Tw0 (step ST4).
  • step ST1 to step ST4 When the wall surface temperature Tw is higher than the set temperature Tw0 (Tw> Tw0), it is determined that freezing has not occurred in the hot water supply heat exchanger 41a (step ST1 to step ST4). On the other hand, when the wall surface temperature Tw is equal to or lower than the set temperature Tw0 (Tw ⁇ Tw0), it is determined that there is a risk of freezing, and a set period Tref corresponding to the water volume V is set and measurement of the elapsed time t is started. (Step ST5). Thereafter, the operation is continued until the elapsed time t reaches the set period Tref (step ST1 to step ST6). If there is no risk of freezing before the elapsed time t reaches the set period Tref (steps ST2 and ST4), the elapsed time t is reset and the operation continues (steps ST1 to ST6).
  • shutoff control means 72 causes the flow controllers 43a and 44a to The refrigerant is closed and the circulation of the refrigerant to the hot water supply heat exchanger 41a is stopped (step ST7). At this time, the supply of the refrigerant to the air conditioning use units 30a to 30d is not stopped and the operation is continued as it is.
  • FIG. FIG. 6 is a refrigerant circuit diagram showing Embodiment 2 of the heat pump system of the present invention.
  • the heat pump system 200 will be described with reference to FIG. In the heat pump system 200 of FIG. 6, parts having the same configuration as the heat pump system 100 of FIG.
  • the heat pump system 200 of FIG. 6 is different from the heat pump system 100 of FIG. 1 in that only the hot water supply heat exchangers 41a to 41c are connected as use units.
  • the plurality of hot water supply use units 40a to 40c includes hot water supply heat exchangers 41a to 41c and expansion devices 42a to 42c.
  • the inflow of the refrigerant into each of the hot water supply heat exchangers 41a to 41c is controlled independently of the second flow path switching unit 22.
  • the water flow path sides of the hot water supply heat exchangers 41a to 41c are connected in parallel.
  • distribution controllers 43a to 43c and 44a to 44c are arranged at both ends of each of the hot water supply heat exchangers 41a to 41c.
  • a control means 70 is provided for each of the plurality of hot water supply heat exchangers 41a to 41c, and each control means 70 detects the occurrence of freezing for each of the hot water supply heat exchangers 41a to 41c.
  • the distribution controllers 43a to 43c and 44a to 44c are controlled independently.
  • a plurality of hot water supply use units 40a to 40c may be collectively managed by one control means 70.
  • the occurrence of freezing is detected in any one of the hot water supply heat exchangers 41a to 41c, the other hot water supply heat exchangers 41b and 41c are also frozen. Since there is a possibility of the occurrence, all the flow controllers 43a to 43c and 44a to 44c may be controlled to be shut off.
  • FIG. 6 illustrates the case where each of the hot water supply use units 40a to 40c is provided with the second flow path switching device 22, the flow controllers 43a to 43c, and 44a to 43c, but as shown in FIG.
  • a plurality of hot water supply heat exchangers 41a to 41c may be connected in parallel using the common pipes 201 and 202 on the refrigerant flow path side.
  • the flow controllers 43 and 44 are provided on the common pipes 201 and 202, respectively, and when the occurrence of freezing is detected in any one of the hot water supply heat exchangers 41a, the flow controllers 43, 44 may be closed.
  • FIG. FIG. 8 is a refrigerant circuit diagram showing Embodiment 3 of the heat pump system of the present invention.
  • the heat pump system 300 will be described with reference to FIG.
  • symbol is attached
  • the heat pump system 300 in FIG. 8 is different from the heat pump system 100 in FIG. 1 in that the heat source side unit 10 and the use units 30a and 40b are connected to the refrigerant pipe 202 without using the relay unit 20 (second flow path switch 22). The point is that they are directly connected by 203.
  • the structure of the heat source side unit 310 is changed instead of the relay machine 20.
  • the oil separator 331 has a function of separating the refrigeration oil component from the refrigerant gas discharged from the compressor 11 and mixed with the refrigeration oil. Then, the refrigerant from which the refrigerator oil component is separated by the oil separator 311 is discharged to the first flow path switch 12 via the check valve 312.
  • An oil return bypass capillary 320 for adjusting the flow rate of the refrigerating machine oil returned to the compressor 11 and an oil return bypass solenoid valve 321 are connected to the lower portion of the oil separator 311. Further, the oil return bypass capillary 302a and the oil return bypass solenoid valve 302b are connected in parallel, and the flow rate of the refrigerating machine oil to be returned is adjusted by opening and closing the oil return bypass electromagnetic valve 302b. Thereby, the refrigeration oil which flows out of the heat source side unit 310 can be reduced, and the reliability of the compressor 11 can be improved.
  • the heat source side unit 310 is provided with an inter-refrigerant heat exchanger 330 on a liquid pipe between the heat source side heat exchanger 13 and the flow rate adjustment valve 331.
  • the inter-refrigerant heat exchanger 330 is a refrigerant that flows in / out to the heat source side heat exchanger 13, a refrigerant that flows through the bypass pipe 340, that is, a refrigerant that flows out to the use units 30a and 40a, and a refrigerant that flows from each of the use units 30a and 40a. Heat exchange.
  • the heat pump system 300 has a use unit 30a for air conditioning and a use unit 40a for hot water supply.
  • the air conditioning utilization unit 30a and the hot water supply utilization unit 40a are connected in parallel using common pipes 301 and 302.
  • the distribution controllers 43a and 44a are provided on the branch pipe branched from the common pipes 301 and 302 to the hot water supply heat exchanger 41a.
  • the heat pump system 300 shown in FIG. 8 is a composite apparatus having an air conditioning usage unit 30a and a hot water supply usage unit 40a, as shown in FIG. 6, the heat pump system 300 includes only a plurality of hot water supply usage units 40a and 40b. It may be.
  • the embodiment of the present invention is not limited to the above embodiment.
  • the heat pump systems 100 to 300 capable of both the cooling operation and the heating operation are illustrated, but the present invention can also be applied to a heat pump system that performs only the cooling operation.
  • the purpose is simply to prevent the low-temperature refrigerant from flowing, and when the low-temperature refrigerant flows from only one direction, only one valve needs to be installed, which improves the simplicity and reduces the cost.
  • the hot water heater can be reduced.
  • the number of use units 40a is not limited to the number illustrated in the first to third embodiments, and it is sufficient that at least one hot water use use unit 40a is provided in a plurality of use units. Further, although the use units 30a to 30d and the hot water supply use units 40a to 40c are illustrated as having the same configuration, the capacities may be different or the same.
  • each of the hot water supply use units 40a to 40c is shown as an example in which a control device is individually mounted. However, two or more hot water supply use units 40a to 40c are controlled by one control device. It may be.
  • the mutual control means 70 can communicate with each other by wire or wirelessly.
  • the control means 70 mounted on each of the hot water supply use units 40a to 40c may be capable of communicating with a control device (not shown) mounted on the heat source side unit 10 in a wired or wireless manner.
  • first throttle device 28, the second throttle device 29, the throttle devices 32a to 32d, 42a to 42c, etc. described above can perform either an inexpensive refrigerant flow rate adjusting means such as a capillary tube or precise flow rate control using an electromagnetic expansion valve. May be used.
  • the flow rate controllers 43 and 44 may be closed to block the inflow of the low-temperature refrigerant.
  • the freezing detection means 71 detects the occurrence of freezing when the hot water supply load 50 (circulation pump 52) is not operating, and detects the occurrence of freezing. You may control to close 43 and 44.
  • a hot water supply heat exchanger 41a In addition, during a cooling operation of a model capable of switching between a cooling operation and a heating operation, a heating operation of a model capable of simultaneous operation of the cooling operation and the heating operation, or a defrosting operation, a hot water supply heat exchanger 41a.
  • the front and rear flow controllers 43a to 43c and 44a to 44c may prevent the flow of low-temperature refrigerant. Thereby, freezing of the hot water supply heat exchangers 41a to 41c can be avoided.

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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)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

La présente invention concerne un système de pompe à chaleur qui possède une unité côté source de chaleur qui présente un compresseur et un échangeur thermique côté source de chaleur, ainsi que plusieurs unités d'utilisation, raccordées en parallèle à l'unité côté source de chaleur et qui comprennent une unité d'utilisation de l'apport d'eau chaude, équipée d'un échangeur thermique d'apport d'eau chaude, qui échange la chaleur entre l'eau et un réfrigérant, avec un circuit de cycle de réfrigération qui fait circuler le réfrigérant vers le compresseur, l'échangeur thermique côté source de chaleur et les multiples unités d'utilisation formées dans le système de pompe à chaleur. Le système de pompe à chaleur comprend : un dispositif de commande de circulation, qui commande la circulation du réfrigérant vers l'unité d'utilisation de l'apport d'eau chaude ; un moyen de détection de condensation, qui détecte une congélation dans l'échangeur thermique d'apport d'eau chaude ; et un moyen de commande d'arrêt, qui commande le dispositif de commande de circulation, de manière à arrêter la circulation du réfrigérant vers l'échangeur thermique d'apport d'eau chaude lorsque le moyen de détection de congélation détermine qu'une congélation s'est produite dans l'échangeur thermique d'apport d'eau chaude.
PCT/JP2012/084070 2012-12-28 2012-12-28 Système de pompe à chaleur WO2014103013A1 (fr)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3130868A1 (fr) * 2015-08-10 2017-02-15 Mitsubishi Heavy Industries, Ltd. Système de pompe à chaleur
JPWO2018066126A1 (ja) * 2016-10-07 2019-01-17 三菱電機株式会社 給湯機
WO2022123689A1 (fr) * 2020-12-09 2022-06-16 三菱電機株式会社 Dispositif de relais et dispositif de climatisation
EP3865779A4 (fr) * 2018-10-08 2022-07-06 Gree Electric Appliances, Inc. of Zhuhai Système de climatisation

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004132647A (ja) * 2002-10-11 2004-04-30 Daikin Ind Ltd 給湯装置、空調給湯システム、及び給湯システム
JP2009243828A (ja) * 2008-03-31 2009-10-22 Mitsubishi Electric Corp 冷却装置および冷却装置監視システム
JP2010196950A (ja) * 2009-02-24 2010-09-09 Daikin Ind Ltd ヒートポンプシステム
WO2011089637A1 (fr) * 2010-01-19 2011-07-28 三菱電機株式会社 Système combiné de climatisation et d'alimentation en eau chaude

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004132647A (ja) * 2002-10-11 2004-04-30 Daikin Ind Ltd 給湯装置、空調給湯システム、及び給湯システム
JP2009243828A (ja) * 2008-03-31 2009-10-22 Mitsubishi Electric Corp 冷却装置および冷却装置監視システム
JP2010196950A (ja) * 2009-02-24 2010-09-09 Daikin Ind Ltd ヒートポンプシステム
WO2011089637A1 (fr) * 2010-01-19 2011-07-28 三菱電機株式会社 Système combiné de climatisation et d'alimentation en eau chaude

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3130868A1 (fr) * 2015-08-10 2017-02-15 Mitsubishi Heavy Industries, Ltd. Système de pompe à chaleur
JPWO2018066126A1 (ja) * 2016-10-07 2019-01-17 三菱電機株式会社 給湯機
EP3865779A4 (fr) * 2018-10-08 2022-07-06 Gree Electric Appliances, Inc. of Zhuhai Système de climatisation
WO2022123689A1 (fr) * 2020-12-09 2022-06-16 三菱電機株式会社 Dispositif de relais et dispositif de climatisation

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