WO2013080297A1 - Système de climatisation et d'approvisionnement d'eau chaude - Google Patents

Système de climatisation et d'approvisionnement d'eau chaude Download PDF

Info

Publication number
WO2013080297A1
WO2013080297A1 PCT/JP2011/077531 JP2011077531W WO2013080297A1 WO 2013080297 A1 WO2013080297 A1 WO 2013080297A1 JP 2011077531 W JP2011077531 W JP 2011077531W WO 2013080297 A1 WO2013080297 A1 WO 2013080297A1
Authority
WO
WIPO (PCT)
Prior art keywords
water supply
hot water
air conditioning
refrigerant
heat exchanger
Prior art date
Application number
PCT/JP2011/077531
Other languages
English (en)
Japanese (ja)
Inventor
小谷　正直
陽子 國眼
Original Assignee
株式会社日立製作所
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 株式会社日立製作所 filed Critical 株式会社日立製作所
Priority to PCT/JP2011/077531 priority Critical patent/WO2013080297A1/fr
Priority to JP2013546876A priority patent/JP5788526B2/ja
Priority to EP11876541.1A priority patent/EP2787304A4/fr
Publication of WO2013080297A1 publication Critical patent/WO2013080297A1/fr

Links

Images

Classifications

    • 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
    • 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
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0254—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series 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
    • F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-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
    • F25B2313/029—Control issues
    • F25B2313/0292—Control issues related to reversing 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers

Definitions

  • the present invention relates to an air conditioning and hot water supply system that performs air conditioning and hot water supply.
  • Patent Document 1 describes an air conditioner (air conditioning hot water supply system) in which a refrigerant circuit is configured by connecting a main cycle and a sub cycle with a cascade condenser (intermediate heat exchanger).
  • the main cycle is configured by connecting a first compressor, a first four-way valve, an outdoor heat exchanger, a first electronic expansion valve, and an indoor heat exchanger, and the subcycle Connects the second compressor, the second four-way valve and the third four-way valve, the hot water heat exchanger, the auxiliary heat exchanger, the second electronic expansion valve and the third electronic expansion valve. It is constituted by.
  • the primary side (main cycle side) of the cascade condenser functions as a condenser during cooling operation
  • the secondary side Function as an evaporator
  • the air conditioning apparatus air conditioning and hot water supply system
  • the air conditioning apparatus allows the main cycle responsible for the air conditioning operation and the subcycle responsible for the hot water supply operation to function independently during the heating operation, and the cascade condenser (intermediate heat exchanger) ) Is not exchanging heat. Therefore, for example, when the room air to be air-conditioned is close to the set temperature during the heating operation, the intermittent operation is performed in the main cycle, and there is a problem that the efficiency of the entire system is deteriorated.
  • an object of the present invention is to provide an air conditioning and hot water supply system that can improve the efficiency of the entire air conditioning and hot water supply system.
  • the present invention is an air-conditioning hot-water supply system comprising an air-conditioning refrigerant circuit in which a first refrigerant circulates and a hot-water supply refrigerant circuit in which a second refrigerant circulates, wherein the air-conditioning refrigerant circuit Includes an air conditioning compressor that compresses the first refrigerant, an air conditioning heat source side heat exchanger that can exchange heat with the air conditioning heat source, an intermediate heat exchanger that exchanges heat between the first refrigerant and the second refrigerant, An air-conditioning decompression device that decompresses the refrigerant, an air-conditioning use-side heat exchanger that functions as an evaporator during cooling operation, and that functions as a condenser during heating operation, and the air-conditioning use-side heat exchanger in cooling operation and heating operation.
  • the air-conditioning refrigerant circuit Includes an air conditioning compressor that compresses the first refrigerant, an air conditioning heat source side heat exchanger that can exchange heat with the air
  • First switching means for switching the direction of the first refrigerant flowing therethrough, and second switching means connected to the first switching means, wherein the second switching means is on the side of the air conditioning heat source according to the operation mode.
  • the direction of the first refrigerant flowing through the heat exchanger and the intermediate heat exchanger By switching the, characterized in that to function the intermediate heat exchanger as a condenser for the first refrigerant.
  • an air conditioning and hot water supply system that can improve the efficiency of the entire air conditioning and hot water supply system.
  • FIG. 1 is a system diagram of a hot water supply air conditioning system according to the present embodiment.
  • the air conditioning and hot water supply system S includes a heat pump unit 1 installed outside the room (outside the air-conditioned space), an indoor unit 2 installed inside the room (in the air-conditioned space), and a hot water tank unit 3.
  • the control device 4 is provided.
  • the air conditioning and hot water supply system S heats the liquid to be heated (for example, water), “cooling operation” for cooling the room where the indoor unit 2 is installed, “heating operation” for heating the room where the indoor unit 2 is installed, and A function of performing a “hot water supply operation” for supplying a high temperature heated liquid to the tank 52, a “cooling hot water supply operation” for performing a cooling operation and a hot water supply operation, and a “heating hot water supply operation” for performing a heating operation and a hot water supply operation. have.
  • a hot water supply operation for supplying a high temperature heated liquid to the tank 52
  • a “cooling hot water supply operation” for performing a cooling operation and a hot water supply operation
  • a “heating hot water supply operation” for performing a heating operation and a hot water supply operation.
  • the air conditioning and hot water supply system S includes an air conditioning refrigerant circuit 10 through which a first refrigerant circulates, a hot water supply refrigerant circuit 30 through which a second refrigerant circulates, an air conditioning heat transfer medium circulation circuit 40 through which a heat transfer medium circulates, A hot water supply circuit 50 through which the liquid to be heated flows.
  • the air conditioning refrigerant circuit 10 provided in the heat pump unit 1 includes an air conditioning compressor 11, a first four-way valve 12, a second four-way valve 14, an air conditioning heat source side heat exchanger 15, and an air conditioning second.
  • the expansion valve 16, the primary heat transfer pipe 21 a of the intermediate heat exchanger 21, the air conditioning first expansion valve 18, and the secondary heat transfer pipe 19 b of the air conditioning utilization side heat exchanger 19 are annularly connected by piping. ing.
  • the upper port on the page is “upper port” and the right port on the page is “right port”.
  • the port on the lower side of the page may be referred to as “lower port”, and the port on the left side of the page may be referred to as “left port”.
  • the right port of the first four-way valve 12 is connected to the discharge side of the compressor 11, and the upper port is connected to the upper port of the second four-way valve 14 via a pipe 13a. Is connected to the suction side of the compressor, and the lower port is connected to the secondary heat transfer pipe 19b of the air-conditioning utilization side heat exchanger 19 via a pipe 12a.
  • the right port of the second four-way valve 14 is connected to the primary heat transfer pipe 21a of the intermediate heat exchanger 21 via the pipe 14a, and the lower port is connected to the air conditioning first expansion valve 18 via the pipe 17a.
  • the left port is connected to the air conditioning heat source side heat exchanger 15 via a pipe 15a.
  • the air conditioning compressor 11 is a compressor that compresses the first refrigerant into a high-temperature and high-pressure refrigerant.
  • the first four-way valve 12 is a four-way valve that switches the direction of the first refrigerant flowing through the secondary side heat transfer pipe 19b of the air conditioning utilization side heat exchanger 19 between the cooling operation and the heating operation. That is, by switching the first four-way valve 12, the low temperature and low pressure first refrigerant expanded by the air conditioning first expansion valve 18 flows into the secondary side heat transfer pipe 19 b of the air conditioning utilization side heat exchanger 19 during the cooling operation. It is like that. Further, during the heating operation, the high-temperature and high-pressure first refrigerant compressed by the air-conditioning compressor 11 flows into the secondary-side heat transfer tube 19 b of the air-conditioning use side heat exchanger 19.
  • the second four-way valve 14 is a four-way valve that switches the direction of the first refrigerant flowing through the air conditioning heat source side heat exchanger 15 and the intermediate heat exchanger 21 according to the operation mode. Details of the operation mode will be described later.
  • the air conditioning heat source side heat exchanger 15 is a heat exchanger that performs heat exchange between the air (outdoor air) sent from the air conditioning fan 15f and the first refrigerant.
  • the air conditioning first expansion valve 18 and the air conditioning second expansion valve 16 function as a decompression device that decompresses the first refrigerant according to the operation mode.
  • one of the air conditioning first expansion valve 18 and the air conditioning second expansion valve 16 functions as a decompression device that decompresses the first refrigerant.
  • the air-conditioning utilization side heat exchanger 19 is a heat exchanger that performs heat exchange between the heat transfer medium that flows through the primary side heat transfer tube 19a and the first refrigerant that flows through the secondary side heat transfer tube 19b.
  • the intermediate heat exchanger 21 is a heat exchanger that performs heat exchange between the first refrigerant flowing through the primary heat transfer tube 21a and the second refrigerant flowing through the secondary heat transfer tube 21b.
  • the first refrigerant HFC, HFO-1234yf, HFO-1234ze, natural refrigerant (for example, CO 2 refrigerant), or the like can be used.
  • the hot water supply refrigerant circuit 30 provided in the heat pump unit 1 includes a hot water supply compressor 31, a hot water use side heat exchanger 32, a primary heat transfer pipe 32 a, a hot water supply first expansion valve 33, and a hot water supply three-way valve 34.
  • a hot water supply heat source side heat exchanger 35, a hot water supply second expansion valve 36, a secondary heat transfer pipe 21b of the intermediate heat exchanger 21, and a hot water supply three-way valve 37 are connected in an annular shape by piping. .
  • the hot water supply three-way valve 34 and the hot water supply three-way valve 37 are connected to each other via a pipe 38a.
  • the hot water supply refrigerant circuit 30 includes a hot water supply refrigerant control valve 39.
  • One end of the hot water supply refrigerant control valve 39 is connected to a pipe branched from the pipe 35a, and the other end is connected to a pipe branched from the pipe 38a.
  • the hot water supply compressor 11 is a compressor that compresses the second refrigerant into a high-temperature and high-pressure refrigerant.
  • the hot water supply side heat exchanger 32 is a heat exchanger that performs heat exchange between the second refrigerant flowing through the primary side heat transfer tube 32a and the heated liquid flowing through the secondary side heat transfer tube 32b.
  • the first hot water supply expansion valve 33 and the second hot water supply expansion valve 36 function as a decompression device that decompresses the second refrigerant in accordance with the operation mode.
  • one of the hot water supply first expansion valve 33 and the hot water supply second expansion valve 36 functions as a pressure reducing device that depressurizes the second refrigerant.
  • the hot water supply heat source side heat exchanger 35 is a heat exchanger that performs heat exchange between the air (outdoor air) sent from the hot water supply fan 35f and the second refrigerant.
  • the hot water supply three-way valves 34 and 37 are three-way valves configured to be capable of adjusting the flow rate ratio of the second refrigerant flowing therethrough.
  • the hot water supply refrigerant control valve 39 is an open / close valve configured to be openable / closable.
  • the second refrigerant HFC, HFO-1234yf, HFO-1234ze, natural refrigerant (for example, CO 2 refrigerant), or the like can be used.
  • the second refrigerant is preferably a refrigerant having a higher critical point (temperature, pressure) than the first refrigerant.
  • An air conditioning heat transfer medium circulation circuit 40 provided from the heat pump unit 1 to the indoor unit 2 includes a first pump 41, a heat transfer medium four-way valve 42, and a primary side heat transfer tube 19a of the air conditioning utilization side heat exchanger 19. And the indoor heat exchanger 43 are annularly connected by piping.
  • the first pump 41 is a pump that pumps the heat transfer medium flowing in from the indoor heat exchanger 43 toward the heat transfer medium four-way valve 42.
  • the heat transfer medium flowing through the primary heat transfer pipe 19a of the air conditioning utilization side heat exchanger 19 and the first refrigerant flowing through the secondary heat transfer pipe 19b are opposed to each other.
  • the four-way valve switches the flow direction of the heat transfer medium between the cooling operation and the heating operation.
  • the indoor heat exchanger 43 is a heat exchanger that performs heat exchange between the air (indoor air) sent from the indoor fan 43f and the heat transfer medium.
  • brine (antifreeze) such as ethylene glycol, water, or the like can be used as the heat transfer medium.
  • a hot water supply circuit 50 provided from the heat pump unit 1 to the hot water supply tank unit 3 includes a second pump 51, a secondary heat transfer pipe 32 b of the hot water supply side heat exchanger 32, and a tank 52 in a ring shape. Connected and configured.
  • the second pump 51 is a pump that pumps up the liquid to be heated from the tank 52 and pumps it toward the secondary heat transfer pipe 32 b of the hot water supply side heat exchanger 32.
  • the tank 52 stores the liquid to be heated and is covered with a heat insulating material (not shown). In the following description, it is assumed that the liquid to be heated uses water.
  • the hot water supply tank unit 3 includes a water supply fitting 53, a hot water supply fitting 55, and three-way valves 54 and 56.
  • One end of the water supply fitting 53 is connected to the three-way valve 54, and the other end is connected to a water supply terminal (not shown).
  • the hot water supply terminal not shown
  • the liquid to be heated flows into the lower portion of the tank 52 via the water supply fitting 53 due to the pressure from the water supply source. Yes.
  • the three-way valves 54 and 56 are three-way valves configured to be able to adjust the flow rate ratio of the liquid to be heated to flow therethrough, and are connected to each other via a pipe 57a. Then, the heated liquid (water) having a flow rate corresponding to the opening degree of each of the three-way valves 54 and 56 is caused to flow through the pipe 57a, thereby adjusting the high-temperature heated liquid supplied from the tank 52 to an appropriate temperature. It is supposed to be.
  • One end of the hot water metal fitting 55 is connected to the three-way valve 56 and the other end is connected to a hot water supply terminal (not shown). When the user opens the hot water supply terminal, the heated liquid (hot water) whose temperature has been adjusted is supplied to the hot water supply terminal via the hot water supply fitting 55.
  • the air conditioning and hot water supply system S includes a control device 4.
  • the control device 4 determines the operation mode of the air conditioning and hot water supply system S, and according to the determined operation mode, various valves (first four-way valve 12, second four-way valve 14, first expansion valve 18 for air conditioning, second air conditioning system).
  • Expansion valve 16 hot water supply first expansion valve 33, hot water supply three-way valves 34, 37, hot water supply second expansion valve 36, hot water supply refrigerant control valve 39, three-way valves 54, 56) (opening), compressor Rotational speed of (air conditioning compressor 11, hot water supply compressor 31), rotational speed of fans (air conditioning fan 15f, hot water supply fan 35f, indoor fan 43f) of each heat exchanger, pump (first pump 41, second The rotational speed of the two pumps 51) is controlled to control various operations of the air conditioning and hot water supply system S.
  • FIG.2 and FIG.3 is a flowchart which shows the procedure of the determination process of the operation mode of the air-conditioning hot-water supply system S which concerns on this embodiment.
  • the control device 4 determines whether there is an air conditioning cycle operation request.
  • the air-conditioning cycle operation request is an operation request for air-conditioning (cooling / heating) the room (air-conditioned space) in which the indoor unit 2 is installed.
  • the air conditioning cycle operation request may be input to the control device 4 by a user operating a remote controller (not shown) installed in the room, for example, and an indoor temperature detector (not shown) that detects the room temperature. May be determined based on the detected temperature (room temperature) and the indoor set temperature. If there is an air conditioning cycle operation request (S101 ⁇ Yes), the process of the control device 4 proceeds to step S105. If there is no air conditioning cycle operation request (S101 ⁇ No), the process of the control device 4 proceeds to step S102.
  • control device 4 determines whether or not there is a hot water supply cycle operation request.
  • the hot water supply cycle operation request is a request to execute the hot water supply operation of the air conditioning hot water supply system S.
  • the hot water supply cycle operation request may be input to the control device 4 by a user operating a remote controller (not shown) installed in the room, for example, or the high temperature stored in the tank 52 of the hot water supply tank unit 3.
  • a “hot water supply cycle operation request” may be made when the amount of liquid to be heated is equal to or less than a predetermined amount, and a “hot water supply cycle operation request” may be made when a predetermined time zone is reached.
  • S102 ⁇ Yes the process of the control device 4 proceeds to step S104.
  • the process of the control device 4 proceeds to step S103.
  • step S103 the control device 4 determines the operation mode of the air conditioning and hot water supply system S to be “standby mode”.
  • the standby mode is a mode in which the air-conditioning operation (cooling operation / heating operation) and the hot-water supply operation of the air-conditioning hot-water supply system S are stopped and an operation command is waited for.
  • step S104 the control device 4 determines the operation mode of the air conditioning and hot water supply system S as the “hot water supply operation mode”.
  • the hot water supply operation mode is a mode in which the hot water supply operation of the air conditioning hot water supply system S is executed. The operation of the air conditioning and hot water supply system S (heat pump unit 1) in this operation mode will be described later with reference to FIG.
  • step S105 control device 4 determines whether or not there is a hot water supply cycle operation request.
  • the hot water supply cycle operation request in step S105 is the same as the hot water supply cycle operation request in step S102, and a description thereof will be omitted.
  • S105 ⁇ Yes the process of the control device 4 proceeds to step S111.
  • S105 ⁇ No the process of the control device 4 proceeds to step S106.
  • step S ⁇ b> 106 the control device 4 determines whether or not the air conditioning cycle operation request is “cooling operation”. When the air conditioning cycle operation request is “cooling operation” (S106 ⁇ Yes), the process of the control device 4 proceeds to step S107. When the air conditioning cycle operation request is not “cooling operation” (S106 ⁇ No), the process of the control device 4 proceeds to step S110.
  • step S107 the control device 4 determines whether or not the air conditioning load Qac is greater than or equal to a predetermined threshold value Q1.
  • the air conditioning load Qac is estimated based on the outdoor temperature Tao, the indoor temperature Tai, the indoor set temperature Tac_set, and the indoor air volume Vac_set.
  • the threshold value Q1 is a threshold value for determining whether or not the air conditioning load is overloaded, and is determined in advance by experiments or simulations and stored in the control device 4.
  • step S107 when the air conditioning load Qac is equal to or greater than the threshold value Q1 (S107 ⁇ Yes), the process of the control device 4 proceeds to step S108.
  • the process of the control device 4 proceeds to step S109.
  • step S108 the control device 4 determines the operation mode of the air conditioning and hot water supply system S as the “cooling operation (normal) mode”.
  • the cooling operation (normal) mode is a mode in which the cooling operation of the air conditioning and hot water supply system S is executed, and is a mode in which natural circulation is not performed in the hot water supply refrigerant circuit 30.
  • the operation of the air conditioning and hot water supply system S (heat pump unit 1) in this operation mode will be described later with reference to FIG.
  • step S109 the control device 4 determines the operation mode of the air conditioning and hot water supply system S as the “cooling operation (natural circulation) mode”.
  • the cooling operation (natural circulation) mode is a mode in which the cooling operation of the air conditioning and hot water supply system S is executed, and is a mode in which natural circulation is performed in the hot water supply refrigerant circuit 30.
  • the operation of the air conditioning and hot water supply system S (heat pump unit 1) in this operation mode will be described later with reference to FIG.
  • step S110 the control device 4 determines the operation mode of the air conditioning and hot water supply system S as the “heating operation mode”.
  • the heating operation mode is a mode in which the heating operation of the air conditioning and hot water supply system S is executed.
  • the operation of the air conditioning and hot water supply system S (heat pump unit 1) in this operation mode will be described later with reference to FIG.
  • step S111 the control device 4 determines whether or not the air-conditioning cycle operation request is “cooling operation”.
  • the air conditioning cycle operation request is “cooling operation” (S111 ⁇ Yes)
  • the process of the control device 4 proceeds to step S112.
  • the air conditioning cycle operation request is not “cooling operation” (S111 ⁇ No)
  • the processing of the control device 4 proceeds to step S201 in FIG.
  • step S112 the control device 4 estimates the air conditioning exhaust heat amount Qac_ex and the hot water supply heat absorption amount Qec_ex.
  • the air conditioning exhaust heat amount Qac_ex is the amount of exhaust heat to the heat source required for the cooling operation when the air conditioning refrigerant circuit 10 and the hot water supply refrigerant circuit 30 are independently operated.
  • the hot water supply heat absorption amount Qec_ex is the heat supply amount from the heat source required for the hot water supply operation when the air conditioning refrigerant circuit 10 and the hot water supply refrigerant circuit 30 are operated independently.
  • step S113 the control device 4 determines whether or not the air conditioning exhaust heat amount Qac_ex is larger than the hot water supply heat absorption amount Qec_ex.
  • the process of the control device 4 proceeds to step S114.
  • the air conditioning exhaust heat amount Qac_ex is equal to or less than the hot water supply heat absorption amount Qec_ex (S113 ⁇ No)
  • the process of the control device 4 proceeds to Step S115.
  • step S114 the control device 4 determines the operation mode of the air conditioning and hot water supply system S as the “cooling hot water supply operation (exhaust heat recovery A) mode”.
  • the cooling hot water supply operation (exhaust heat recovery A) mode is a kind of mode for performing the cooling operation and the hot water supply operation of the air conditioning hot water supply system S, and the exhaust heat of the air conditioning refrigerant circuit 10 is recovered by the hot water supply refrigerant circuit 30. Drive.
  • the operation of the air conditioning and hot water supply system S (heat pump unit 1) in this operation mode will be described later with reference to FIG.
  • step S115 the control device 4 determines whether or not the air conditioning exhaust heat amount Qac_ex is equal to the hot water supply heat absorption amount Qec_ex.
  • the process of the control device 4 proceeds to step S116.
  • the process of the control device 4 proceeds to step S117.
  • step S116 the control device 4 determines the operation mode of the air conditioning and hot water supply system S as the “cooling hot water supply operation (exhaust heat recovery B) mode”.
  • the cooling hot water supply operation (exhaust heat recovery B) mode is a kind of mode for performing the cooling operation and the hot water supply operation of the air conditioning hot water supply system S, and the exhaust heat of the air conditioning refrigerant circuit 10 is recovered by the hot water supply refrigerant circuit 30. Drive.
  • the operation of the air conditioning and hot water supply system S (heat pump unit 1) in this operation mode will be described later with reference to FIG.
  • step S117 the control device 4 determines the operation mode of the air conditioning and hot water supply system S as the “cooling hot water supply operation (exhaust heat recovery C) mode”.
  • the cooling / hot water supply operation (exhaust heat recovery C) mode is a kind of mode for performing the cooling operation and the hot water supply operation of the air conditioning and hot water supply system S, and the exhaust heat of the air conditioning refrigerant circuit 10 is recovered by the hot water supply refrigerant circuit 30. Drive.
  • the operation of the air conditioning and hot water supply system S (heat pump unit 1) in this operation mode will be described later with reference to FIG.
  • step S111 the case where the air-conditioning cycle operation request is not “cooling operation” in step S111 (S111 ⁇ No) will be described with reference to FIG. That is, a case where there is a hot water supply cycle operation request (see S105 ⁇ Yes) and the air conditioning cycle operation request is “heating operation” will be described.
  • step S201 the control device 4 estimates the single total power consumption Wsys1 and the surplus heat operation power consumption Wsys2.
  • the single total power consumption Wsys1 is the estimated power consumption when the air conditioning and hot water supply system S is operated in the heating and hot water supply operation (independent) mode (see FIG. 13 to be described later).
  • the surplus heat operation power consumption Wsys2 is the estimated power consumption when the air conditioning hot water supply system S is operated in the heating hot water supply operation (air conditioning surplus heating) mode (see FIG. 14 described later). Note that the process of estimating the single total power consumption Wsys1 and the surplus heat operation power consumption Wsys2 will be described later with reference to FIG.
  • step S202 the control device 4 determines whether or not the single total power consumption Wsys1 is equal to or less than the surplus heat operation power consumption Wsys2.
  • the process of the control device 4 proceeds to step S203.
  • the processing of the control device 4 proceeds to step S204.
  • step S203 the control device 4 determines the operation mode of the air conditioning and hot water supply system S as the “heating and hot water supply operation (independent) mode”.
  • the heating and hot water supply operation (independent) mode is a type of mode for performing the heating operation and the hot water supply operation of the air conditioning and hot water supply system S.
  • the air conditioning refrigerant circuit 10 and the hot water supply refrigerant circuit 30 are operated independently, The intermediate heat exchanger 21 is not used.
  • the operation of the air conditioning and hot water supply system S (heat pump unit 1) in this operation mode will be described later with reference to FIG.
  • step S204 the control device 4 determines the operation mode of the air conditioning and hot water supply system S as the “heating and hot water supply operation (air conditioning surplus heating) mode”.
  • the heating hot water supply operation (air conditioning surplus heating) mode is a mode in which the heating operation of the air conditioning hot water supply system S is executed, and the surplus heat of the air conditioning refrigerant circuit 10 is collected by the hot water supply refrigerant circuit 30 to perform the hot water supply operation.
  • the operation of the air conditioning and hot water supply system S (heat pump unit 1) in this operation mode will be described later with reference to FIG.
  • FIG. 4 is a flowchart showing a procedure for estimating the air conditioning exhaust heat amount Qac_ex and the hot water supply heat absorption amount Qec_ex in step S112 of FIG.
  • the control device 4 estimates the air conditioning load Qac.
  • the air conditioning load Qac is estimated based on the outdoor temperature Tao, the indoor temperature Tai, the indoor set temperature Tac_set, and the indoor air volume Vac_set.
  • the outdoor temperature Tao is detected by, for example, a temperature sensor (not shown) provided at the outside air intake port of the air conditioning fan 15f or the hot water supply fan 35f of the heat pump unit 1.
  • the indoor temperature Tai is detected by, for example, a temperature sensor (not shown) provided at the indoor air intake port of the indoor fan 43f of the indoor unit 2.
  • the indoor air volume Vac_set for example, the air volume (air flow rate) is calculated by detecting the rotational speed of the indoor fan 43f. Alternatively, it is calculated from the set air volume set by the user with a remote controller (not shown) installed in the room.
  • the indoor set temperature Tac_set is input to the control device 4 when the user operates a remote controller (not shown) installed indoors, for example.
  • step S302 the control device 4 estimates the air conditioning power consumption Wac.
  • the air conditioning power consumption Wac is estimated based on the air conditioning load Qac, the outdoor temperature Tao, and the indoor set temperature Tac_set estimated in step S301.
  • step S303 the control device 4 estimates the air conditioning exhaust heat quantity Qac_ex.
  • the air conditioning exhaust heat quantity Qac_ex is estimated based on the air conditioning load Qac estimated in step S301 and the air conditioning power consumption Wac estimated in step S302.
  • step S304 the control device 4 estimates the hot water supply load Qec.
  • the hot water supply load Qec is estimated based on the outdoor temperature Tao, the water supply temperature Twi, the hot water supply temperature Two, and the water supply flow rate Vw.
  • the feed water temperature Twi is detected by, for example, a temperature sensor (not shown) provided on the inlet side of the secondary heat transfer tube 32b of the hot water use side heat exchanger 32 of the heat pump unit 1.
  • the hot water supply temperature Two is a set temperature of hot water (liquid to be heated) boiled by the heat pump unit 1, and is input to the control device 4 when the user operates a remote controller (not shown) installed indoors, for example. Is done.
  • the feed water flow rate Vw is calculated by detecting the rotational speed of the second pump 51 of the heat pump unit 1, for example.
  • control device 4 estimates hot water supply power consumption Wec.
  • Hot water supply power consumption Wec is estimated based on hot water supply load Qec, outdoor temperature Tao, and hot water supply temperature Two estimated in step S304.
  • the control device 4 estimates the hot water supply heat absorption amount Qec_ex.
  • the hot water supply heat absorption amount Qec_ex is estimated based on the hot water supply load Qec estimated in step S304 and the hot water supply power consumption Wec estimated in step S305.
  • control device 4 estimates the air conditioning exhaust heat quantity Qac_ex (see S303), estimates the hot water supply heat absorption quantity Qec_ex (see S306), ends the process of step S112 in FIG. 2, and proceeds to step S113.
  • FIG. 5 is a flowchart showing a procedure for estimating the single total power consumption Wsys1 and the surplus heat operation power consumption Wsys2 in step S201 of FIG.
  • the control device 4 estimates the air conditioning load Qac.
  • the air conditioning load Qac is estimated based on the outdoor temperature Tao, the indoor temperature Tai, the indoor set temperature Tac_set, and the indoor air volume Vac_set.
  • step S402 the control device 4 estimates the air conditioning compressor target rotational speed Ncp_ac.
  • the air conditioning compressor target rotational speed Ncp_ac is estimated based on the air conditioning load Qac, the outdoor temperature Tao, the indoor set temperature Tac_set, and the indoor air volume Vac_set estimated in step S401.
  • step S403 the control device 4 determines whether or not the air conditioning compressor target rotational speed Ncp_ac estimated in step S402 is equal to or higher than the air conditioning compressor minimum rotational speed Ncp_acmin.
  • the minimum rotation speed Ncp_acmin of the air conditioning compressor is the lower limit of the rotation speed at which the air conditioning compressor 11 of the air conditioning refrigerant circuit 10 can be controlled.
  • step S404 If the air conditioning compressor target rotational speed Ncp_ac is equal to or higher than the air conditioning compressor minimum rotational speed Ncp_acmin (S403 ⁇ Yes), the process of the control device 4 proceeds to step S404.
  • the air conditioning compressor target rotation speed Ncp_ac is less than the air conditioning compressor minimum rotation speed Ncp_acmin (S403 ⁇ No)
  • the process of the control device 4 proceeds to step S409.
  • step S404 the control device 4 estimates the air conditioning power consumption Wac.
  • the air conditioning power consumption Wac is estimated based on the air conditioning load Qac, the outdoor temperature Tao, and the indoor set temperature Tac_set estimated in step S401.
  • step S405 the control device 4 estimates the hot water supply load Qec.
  • the hot water supply load Qec is estimated based on the outdoor temperature Tao, the water supply temperature Twi, the hot water supply temperature Two, and the water supply flow rate Vw.
  • control device 4 estimates hot water supply power consumption Wec.
  • Hot water supply power consumption Wec is estimated based on hot water supply load Qec, outdoor temperature Tao, and hot water supply temperature Two estimated in step S405.
  • the control device 4 estimates the single total power consumption Wsys1.
  • the air conditioning compressor rotation speed Ncp_ac is less than the air conditioning compressor minimum rotation speed Ncp_acmin in step S403 of FIG. 5 (S403 ⁇ No)
  • the air conditioning compressor target rotational speed Ncp_ac estimated from the air conditioning load Qac is the minimum air conditioning compressor rotational speed.
  • the compressor rotation speed is Ncp_acmin.
  • the control device 4 since the air-conditioning capability actually output becomes larger than the air-conditioning load Qac by Ncp_acmin / Ncp_ac, the control device 4 performs intermittent operation in which the operation and stop of the air-conditioning compressor 11 are repeated. Therefore, in this case, the efficiency of the air conditioning and hot water supply system S deteriorates.
  • step S409 the control device 4 estimates the air-conditioning power consumption deterioration rate ⁇ during intermittent operation. And air-conditioning power consumption Wac1 which considered intermittent operation is estimated.
  • the air conditioning power consumption deterioration rate ⁇ is estimated based on the air conditioning compressor target rotation speed Ncp_ac and the air conditioning compressor minimum rotation speed Ncp_acmin.
  • the air-conditioning power consumption Wac1 considering the intermittent operation is estimated based on the air-conditioning load Qac, the outdoor temperature Tao, the indoor set temperature Tac_set, and the air-conditioning power consumption deterioration rate ⁇ estimated in step S401.
  • control device 4 estimates hot water supply load Qec.
  • the hot water supply load Qec is estimated based on the outdoor temperature Tao, the water supply temperature Twi, the hot water supply temperature Two, and the water supply flow rate Vw.
  • control device 4 estimates hot water supply power consumption Wec. Hot water supply power consumption Wec is estimated based on hot water supply load Qec, outdoor temperature Tao, and hot water supply temperature Two estimated in step S304.
  • step S412 the control device 4 estimates the single total power consumption Wsys1.
  • step S413 the control device 4 estimates the air conditioning pseudo load Qac_ec.
  • the air conditioning pseudo load Qac_ec is estimated based on the outdoor temperature Tao, the feed water temperature Twi, the hot water supply temperature Two, and the feed water flow rate Vw.
  • the air conditioning use side heat exchanger 19 of the air conditioning refrigerant circuit 10 functions as a condenser
  • the intermediate heat exchanger 21 of the air conditioning refrigerant circuit 10 is also caused to function as a condenser. Therefore, the air conditioning pseudo load Qac_ec is estimated using the hot water supply heat absorption amount in the intermediate heat exchanger 21 of the hot water supply refrigerant circuit 30 as the air conditioning pseudo load in the intermediate heat exchanger 21 of the air conditioning refrigerant circuit 10.
  • step S414 the control device 4 estimates the air conditioning load Qac2 in consideration of the air conditioning pseudo load Qac_ec.
  • step S415 the control device 4 estimates the air conditioning power consumption Wac2 in consideration of the pseudo load.
  • the air conditioning power consumption Wac2 is estimated based on the air conditioning load Qac2, the outdoor temperature Tao, and the indoor set temperature Tac_set estimated in step S414.
  • step S416 the control device 4 estimates the hot water supply power consumption Wec2 in consideration of the air conditioning pseudo load Qac_ec.
  • Hot water supply power consumption Wec2 is estimated based on air conditioning load Qac2 estimated in step S414, hot water supply load Qec estimated in step S410, outdoor temperature Tao, hot water supply temperature Two, and indoor set temperature Tac_set.
  • step S417 the control device 4 estimates surplus heat operation power consumption Wsys2.
  • control device 4 estimates the single total power consumption Wsys1 (see S407 and S412), estimates the surplus heat operation power consumption Wsys2 (see S408 and S417), and ends the process of step S201 in FIG. Then, the process proceeds to step S202.
  • each operation mode of the air conditioning and hot water supply system S executed by the control device 4 determines the operation mode of the air conditioning and hot water supply system S (see FIGS. 2 and 3), and controls the air conditioning and hot water supply system S according to the determined operation mode to perform various operations.
  • a pipe through which the first refrigerant, the second refrigerant, the heat transfer medium, and the liquid to be heated flow is indicated by a bold line, and the flow direction is indicated by an arrow.
  • various valves three-way valves for hot water supply 34 and 37, a second hot water supply expansion valve 36, and a hot water supply refrigerant control valve 39
  • the side where the flow is closed is shown in black.
  • Step S103 In this mode, the air conditioning refrigerant circuit 10, the hot water supply refrigerant circuit 30, the air conditioning heat transfer medium circulation circuit 40, and the hot water supply circuit 50 are stopped.
  • the control device 4 waits for an input of an operation command.
  • the operation mode of the air conditioning and hot water supply system S is determined (see FIGS. 2 and 3).
  • FIG. 6 is a system diagram showing the flow of the refrigerant and the liquid to be heated in the heat pump unit 1 in the hot water supply operation mode.
  • the air conditioning refrigerant circuit 10 and the air conditioning heat transfer medium circulation circuit 40 are stopped. Further, the flow of the refrigerant to the intermediate heat exchanger 21 is closed in the hot water supply refrigerant circuit 30.
  • the hot water supply refrigerant circuit 30 will be described.
  • the control device 4 fully opens the hot water supply refrigerant control valve 39 so that the refrigerant in the hot water supply refrigerant circuit 30 flows through the hot water supply heat source side heat exchanger 35 and bypasses the intermediate heat exchanger 21.
  • the hot water supply second expansion valve 36 is closed, and the hot water supply three-way valves 34 and 37 are controlled.
  • the control apparatus 4 controls the opening degree (throttle) of the 1st expansion valve 33 for hot water supply. Further, the control device 4 controls the rotation speeds of the hot water supply compressor 31 and the hot water supply fan 35f.
  • the high-temperature and high-pressure second refrigerant discharged from the hot water supply compressor 31 flows into the primary side heat transfer tube 32a of the hot water supply side heat exchanger 32 that functions as a condenser.
  • the second refrigerant flowing through the primary side heat transfer pipe 32a of the hot water supply side heat exchanger 32 exchanges heat with the heated liquid flowing through the secondary side heat transfer pipe 32b of the hot water supply side heat exchanger 32.
  • the medium-temperature and high-pressure second refrigerant that has flowed out of the primary-side heat transfer pipe 32a of the hot-water use side heat exchanger 32 is depressurized by the hot-water supply first expansion valve 33, and becomes a low-temperature and low-pressure second refrigerant.
  • the low-temperature and low-pressure second refrigerant flows into the hot water supply heat source side heat exchanger 35 functioning as an evaporator via the hot water supply three-way valve 34.
  • the second refrigerant flowing through the hot water supply heat source side heat exchanger 35 exchanges heat with the air (outdoor air) sent by the hot water supply fan 35f, thereby pumping up heat (absorbing heat) from the air.
  • the absorbed second refrigerant is sent from the hot water supply heat source side heat exchanger 35 to the hot water supply compressor 31 through the hot water supply refrigerant control valve 39 and the hot water supply three-way valve 37 and circulates in the hot water supply refrigerant circuit 30.
  • the control device 4 controls the rotation speed of the second pump 51.
  • the liquid to be heated that has flowed out from the lower portion of the tank 52 flows into the secondary heat transfer pipe 32 b of the hot water supply side heat exchanger 32.
  • the liquid to be heated that flows through the secondary heat transfer pipe 32b of the hot water use side heat exchanger 32 absorbs heat by exchanging heat with the second refrigerant that flows through the primary side heat transfer pipe 32a of the hot water use side heat exchanger 32. Thus, it becomes a high-temperature liquid to be heated.
  • the hot liquid to be heated is returned to the upper part of the tank 52 from the secondary heat transfer tube 32b of the hot water supply side heat exchanger 32 and stored.
  • FIG. 7 is a system diagram showing the flow of the refrigerant and heat transfer medium of the heat pump unit 1 in the cooling operation (normal) mode.
  • the hot water supply refrigerant circuit 30 and the hot water supply circuit 50 are stopped. Further, the flow of the refrigerant to the intermediate heat exchanger 21 is closed in the hot water supply refrigerant circuit 30.
  • the control device 4 controls the switching means (not shown) in the first four-way valve 12 and the second four-way valve 14 to be in the cooling operation position. That is, the control device 4 controls the first four-way valve 12 so that the first refrigerant flowing out from the secondary side heat transfer pipe 19b of the air conditioning utilization side heat exchanger 19 flows into the air conditioning compressor 11, and the air conditioning The second four-way valve 14 is controlled so that the first refrigerant discharged from the compressor 11 flows into the air conditioning heat source side heat exchanger 15.
  • control device 4 controls the second expansion valve 16 for air conditioning to be fully opened, and controls the opening degree (throttle) of the first expansion valve 18 for air conditioning. Further, the control device 4 controls the rotational speeds of the air conditioning compressor 11 and the air conditioning fan 15f. As shown in FIG. 7, by controlling the second four-way valve 14, the high-temperature and high-pressure first refrigerant discharged from the air-conditioning compressor 11 is supplied to the air-conditioning heat source side heat exchanger before the intermediate heat exchanger 21. 15 can be introduced. Incidentally, in the opposite case (when the first refrigerant flows into the intermediate heat exchanger 21 before the air conditioning heat source side heat exchanger 15), the high temperature and high pressure discharged from the air conditioning compressor 11 is used.
  • the first refrigerant flowing through the air-conditioning heat source side heat exchanger 15 dissipates heat (exhaust heat) by exchanging heat with the air (outdoor air) sent by the air-conditioning fan 15f.
  • the medium-temperature and high-pressure first refrigerant flowing out of the air-conditioning heat source side heat exchanger 15 passes through the air conditioning second expansion valve 16, the intermediate heat exchanger 21, the primary side heat transfer pipe 21 a, and the second four-way valve 14. It flows into one expansion valve 18.
  • the medium-temperature and high-pressure first refrigerant is reduced in pressure by the air conditioning first expansion valve 18, becomes a low-temperature and low-pressure first refrigerant, and flows into the secondary-side heat transfer tube 19b of the air-conditioning use side heat exchanger 19 functioning as an evaporator. .
  • the first refrigerant flowing through the secondary side heat transfer tube 19b of the air conditioning use side heat exchanger 19 exchanges heat with the heat transfer medium flowing through the primary side heat transfer tube 19a of the air conditioning use side heat exchanger 19, Pumps heat from the heat transfer medium (absorbs heat). Then, the absorbed first refrigerant is sent from the air-conditioning utilization side heat exchanger 19 to the air-conditioning compressor 11 via the first four-way valve 12 and circulates through the air-conditioning refrigerant circuit 10.
  • the control device 4 controls the rotation speeds of the first pump 41 and the indoor fan 43f.
  • the control device 4 includes a heat transfer medium that flows through the primary side heat transfer pipe 19a of the air conditioning utilization side heat exchanger 19 and a first refrigerant that flows through the secondary side heat transfer pipe 19b of the air conditioning utilization side heat exchanger 19.
  • the heat transfer medium four-way valve 42 is controlled so that becomes a counter flow.
  • the heat transfer medium flows into the secondary side heat transfer tube 19 b of the air conditioning utilization side heat exchanger 19.
  • the heat transfer medium flowing through the secondary side heat transfer pipe 19b of the air conditioning use side heat exchanger 19 exchanges heat with the first refrigerant flowing through the secondary side heat transfer pipe 19b of the air conditioning use side heat exchanger 19. It dissipates heat (exhaust heat) and becomes a low-temperature heat transfer medium.
  • the low-temperature heat transfer medium flows into the indoor heat exchanger 43 of the indoor unit 2.
  • the heat transfer medium flowing through the indoor heat exchanger 43 absorbs heat by exchanging heat with the air (indoor air) sent by the indoor fan 43f.
  • the heat transfer medium that has absorbed heat is sent from the indoor heat exchanger 43 to the first pump 42 and circulates through the heat transfer medium circulation circuit 40 for air conditioning. As described above, the heat transfer medium absorbs heat in the indoor heat exchanger 43 of the indoor unit 2, thereby cooling the air (room air) and cooling the room (air-conditioned space).
  • FIG. 8 is a system diagram showing the flow of the refrigerant and heat transfer medium of the heat pump unit 1 in the cooling operation (natural circulation) mode.
  • the cooling operation (natural circulation) mode is an operation mode when the air conditioning load at the time of performing the cooling operation is an overload.
  • the heat of the first refrigerant flowing through the primary side heat transfer tube 21a is radiated (exhaust heat) to the second refrigerant flowing through the secondary side heat transfer tube 21b.
  • the first refrigerant is further condensed.
  • the intermediate heat exchanger 21 that functions as a condenser replaces the amount of heat released from the first refrigerant in the air conditioning heat source side heat exchanger 15. It is different from the cooling operation (normal) mode (see FIG. 7) in that it is compensated by radiating heat.
  • the cooling operation (normal) mode see FIG. 7
  • the second refrigerant that has radiated heat in the hot water supply heat source side heat exchanger 35 functioning as a condenser and has become a liquid state flows into the intermediate heat exchanger 21 by gravity.
  • the hot water supply circuit 50 is stopped.
  • the air-conditioning heat transfer medium circulation circuit 40 is the same as the above-described cooling operation (normal) mode, and thus the description thereof is omitted.
  • the air conditioning refrigerant circuit 10 is the same as that in the cooling operation (normal mode) described above except that the intermediate heat exchanger 21 functions as a condenser in addition to the air conditioning heat source side heat exchanger 15. Since there is, explanation is omitted.
  • the hot water supply refrigerant circuit 30 will be described.
  • the control device 4 an annular circuit is formed by the hot water supply heat source side heat exchanger 35, the pipe 35a, the second hot water supply expansion valve 36, the secondary heat transfer pipe 21b of the intermediate heat exchanger 21, and the pipes 37a and 38a. Then, the hot water supply refrigerant control valve 39 is closed, the hot water supply three-way valves 34 and 37 are controlled, and the hot water supply second expansion valve 36 is fully opened.
  • the control device 4 controls the rotational speed of the hot water supply fan 35f.
  • the second refrigerant flows into the secondary heat transfer tube 21b of the intermediate heat exchanger 21 functioning as an evaporator in a low-temperature liquid state.
  • the second refrigerant absorbs heat from the first refrigerant flowing through the primary heat transfer tube 21a of the intermediate heat exchanger 21.
  • the second refrigerant evaporates, becomes an upward flow, flows through the pipes 37a and 38a, and flows into the hot water supply heat source side heat exchanger 35 functioning as a condenser.
  • the medium-temperature second refrigerant in the gaseous state dissipates heat by exchanging heat with the air (outdoor air) sent by the hot-water supply fan 35f when flowing through the hot-water supply heat source side heat exchanger 35, and the low-temperature liquid It becomes a state. Then, the low-temperature liquid second refrigerant descends in the pipe 35 a due to gravity, flows into the secondary heat transfer pipe 21 b of the intermediate heat exchanger 21 via the hot water supply second expansion valve 36, and is supplied with the hot water supply refrigerant circuit 30. Circulate.
  • FIG. 9 is a system diagram illustrating the flow of the refrigerant and the heat transfer medium of the heat pump unit 1 in the heating operation mode.
  • the hot water supply refrigerant circuit 30 and the hot water supply circuit 50 are stopped. Further, the flow of the refrigerant to the intermediate heat exchanger 21 is closed in the hot water supply refrigerant circuit 30.
  • the control device 4 controls the switching means (not shown) in the first four-way valve 12 and the second four-way valve 14 to be in the heating operation mode position. That is, the control device 4 controls the first four-way valve 12 so that the first refrigerant discharged from the air conditioning compressor 11 flows into the secondary side heat transfer pipe 19b of the air conditioning utilization side heat exchanger 19, The second four-way valve 14 is controlled so that the first refrigerant flowing out from the intermediate heat exchanger 21 flows into the air conditioning compressor 11.
  • the control device 4 fully opens the air conditioning second expansion valve 16 and controls the opening (throttle) of the air conditioning first expansion valve 18. Further, the control device 4 controls the rotational speeds of the air conditioning compressor 11 and the air conditioning fan 15f.
  • the low-temperature and low-pressure first refrigerant that has flowed out of the air conditioning first expansion valve 18 is subjected to heat exchange on the air conditioning heat source side before the intermediate heat exchanger 21. Can flow into the vessel 15. In this case, the temperature of the first refrigerant that has exchanged heat with the air (outdoor air) sent by the air conditioning fan 15f does not become higher than the temperature of the air. The first refrigerant does not radiate heat in the heat pipe 21a.
  • the low temperature and low pressure discharged from the air conditioning first expansion valve 18 is used.
  • the first refrigerant absorbs heat in the intermediate heat exchanger 21, and the dryness of the first refrigerant increases.
  • the temperature difference between the temperature of the first refrigerant and the outdoor air temperature cannot be maintained, and the heat absorption amount of the first refrigerant decreases. Therefore, since it is necessary to supplement the heat absorption amount by the compressor 11, the load on the compressor 11 increases.
  • the first refrigerant flowing through the secondary side heat transfer tube 19b of the air conditioning use side heat exchanger 19 radiates heat by exchanging heat with the heat transfer medium flowing through the primary side heat transfer tube 19a of the air conditioning use side heat exchanger 19. Thus, it becomes a medium temperature and high pressure first refrigerant.
  • the medium-temperature and high-pressure first refrigerant flowing out of the air-conditioning utilization side heat exchanger 19 is decompressed by the air-conditioning first expansion valve 18 and becomes a low-temperature and low-pressure first refrigerant.
  • the low-temperature and low-pressure first refrigerant flows into the air-conditioning heat source side heat exchanger 15 functioning as an evaporator.
  • the first refrigerant flowing through the air conditioning heat source side heat exchanger 15 heats up (absorbs) heat from the air by exchanging heat with the air (outdoor air) sent by the air conditioning fan 15f.
  • the absorbed first refrigerant is supplied from the air-conditioning heat source side heat exchanger 15 through the second air-conditioning expansion valve 16, the intermediate heat exchanger 21, the second four-way valve 14, and the first four-way valve 12. It is sent to the compressor 11 and circulates through the air conditioning refrigerant circuit 10.
  • the control device 4 controls the rotation speeds of the first pump 41 and the indoor fan 43f.
  • the heat transfer medium flows into the primary side heat transfer tube 19 a of the air conditioning use side heat exchanger 19.
  • the heat transfer medium flowing through the primary side heat transfer pipe 19a of the air conditioning use side heat exchanger 19 absorbs heat by exchanging heat with the first refrigerant flowing through the secondary side heat transfer pipe 19b of the air conditioning use side heat exchanger 19.
  • a high-temperature heat transfer medium is obtained.
  • the high-temperature heat transfer medium flows into the indoor heat exchanger 43 of the indoor unit 2.
  • the heat transfer medium flowing through the indoor heat exchanger 43 dissipates heat by exchanging heat with the air (indoor air) sent by the indoor fan 43f.
  • the radiated heat transfer medium is sent from the indoor heat exchanger 43 to the first pump 41 and circulates in the heat transfer medium circulation circuit 40 for air conditioning. In this way, the heat transfer medium dissipates heat in the indoor heat exchanger 43 of the indoor unit 2, so that air (room air) is heated and the room (air-conditioned space) is heated.
  • FIG. 10 is a system diagram showing the flow of the refrigerant, heat transfer medium, and heated liquid in the heat pump unit 1 in the cooling hot water supply operation (exhaust heat recovery A) mode.
  • the exhaust heat recovery A is a case of “air conditioning exhaust heat> hot water supply endotherm”, and the exhaust heat of the air conditioning refrigerant circuit 10 is recovered by the hot water supply refrigerant circuit 30 via the intermediate heat exchanger 21, and excess air conditioning is performed. Exhaust heat is exhausted to outdoor air.
  • the operation of the hot water supply circuit 50 is the same as in the hot water supply operation mode shown in FIG.
  • the operation of the air-conditioning heat transfer medium circulation circuit 40 is the same as that in the cooling operation (normal) mode shown in FIG.
  • the air conditioning refrigerant circuit 10 will be described.
  • the difference between the air conditioning refrigerant circuit 10 in the cooling operation (normal) mode (see FIG. 7) and the air conditioning refrigerant circuit 10 in the cooling hot water supply operation (exhaust heat recovery A) mode (see FIG. 10) is the cooling operation (normal).
  • ) Mode only the air conditioner heat source side heat exchanger 15 functions as a condenser, whereas in the cooling hot water supply operation (exhaust heat recovery A) mode, in addition to the air conditioner heat source side heat exchanger 15, an intermediate heat exchanger is provided. 21 also functions as a condenser.
  • the second refrigerant 14 is controlled so that the first refrigerant discharged from the air conditioning compressor 11 flows into the air conditioning heat source side heat exchanger 15.
  • the cooling hot water supply operation (exhaust heat recovery A) mode is different in that the second four-way valve 14 is controlled so that the first refrigerant discharged from the air conditioning compressor 11 flows into the intermediate heat exchanger 21.
  • the high-temperature and high-pressure first refrigerant discharged from the air-conditioning compressor 11 passes through the first four-way valve 12 and the second four-way valve 14, and the primary heat transfer tube 21a of the intermediate heat exchanger 21 that functions as a condenser. Flow into.
  • the high-temperature and high-pressure first refrigerant flowing through the primary heat transfer tube 21a of the intermediate heat exchanger 21 exchanges heat with the low-temperature and low-pressure second refrigerant flowing through the secondary heat transfer tube 21b of the intermediate heat exchanger 21. Radiates heat (exhaust heat).
  • the first refrigerant flows into the air conditioning heat source side heat exchanger 15 functioning as a condenser via the air conditioning second expansion valve 16.
  • the first refrigerant flowing through the air-conditioning heat source side heat exchanger 15 further dissipates heat (exhaust heat) by exchanging heat with the air (outdoor air) sent by the air-conditioning fan 15f. It becomes.
  • the medium temperature and high pressure first refrigerant flowing out of the air conditioning heat source side heat exchanger 15 flows into the air conditioning first expansion valve 18 via the second four-way valve 14 and is decompressed by the air conditioning first expansion valve 18 to be low temperature. It becomes a low-pressure first refrigerant.
  • the low-temperature and low-pressure first refrigerant flows into the primary side heat transfer tube 19a of the air conditioning use side heat exchanger 19 functioning as an evaporator.
  • the first refrigerant flowing through the primary side heat transfer pipe 19a of the air-conditioning use side heat exchanger 19 exchanges heat with the heat transfer medium flowing through the secondary side heat transfer pipe 19b of the air-conditioning use side heat exchanger 19; Pumps heat from the heat transfer medium (absorbs heat).
  • the first refrigerant that has absorbed heat is sent from the air conditioning utilization side heat exchanger 19 to the air conditioning compressor 11 and circulates through the air conditioning refrigerant circuit 10.
  • the high-temperature and high-pressure first refrigerant discharged from the compressor 11 flows into the intermediate heat exchanger 21 before the air-conditioning heat source side heat exchanger 15. Can be made.
  • coolant which flows the secondary side heat exchanger tube 21b of the intermediate heat exchanger 21 can be made into a counterflow. . Therefore, the amount of heat radiated from the first refrigerant to the second refrigerant in the intermediate heat exchanger 21 can be increased.
  • the difference between the hot water supply refrigerant circuit 30 in the hot water supply operation mode (see FIG. 6) and the hot water supply refrigerant circuit 30 in the cooling hot water supply operation (exhaust heat recovery A) mode (see FIG. 10) is that the second refrigerant in the hot water supply operation mode. Flows through the hot water supply heat source side heat exchanger 35, whereas the second refrigerant does not flow through the hot water supply heat source side heat exchanger 35 in the cooling hot water supply operation (exhaust heat recovery A) mode. Further, the second refrigerant does not flow through the intermediate heat exchanger 21 in the hot water supply operation mode, whereas the second refrigerant flows through the intermediate heat exchanger 21 in the cooling hot water supply operation (exhaust heat recovery A) mode. .
  • the control device 4 has an annular shape with a hot water supply compressor 31, a hot water supply side heat exchanger 32, a hot water supply first expansion valve 33, a pipe 35a, a hot water supply second expansion valve 36, an intermediate heat exchanger 21, and a pipe 37a.
  • the hot water supply refrigerant control valve 39 and the hot water supply second expansion valve 36 are fully opened to control the hot water supply three-way valves 34 and 37 so that a circuit is formed.
  • the control device 4 controls the opening degree (throttle) of the first hot water supply expansion valve 33 to stop the hot water supply fan 35f.
  • the high-temperature and high-pressure second refrigerant discharged from the hot water supply compressor 31 flows into the primary side heat transfer tube 32a of the hot water supply side heat exchanger 32 that functions as a condenser.
  • the second refrigerant flowing through the primary side heat transfer pipe 32a of the hot water supply side heat exchanger 32 exchanges heat with the heated liquid flowing through the secondary side heat transfer pipe 32b of the hot water supply side heat exchanger 32.
  • the medium-temperature and high-pressure second refrigerant that has flowed out of the primary-side heat transfer pipe 32a of the hot-water use side heat exchanger 32 is depressurized by the hot-water supply first expansion valve 33, and becomes a low-temperature and low-pressure second refrigerant.
  • the low-temperature and low-pressure second refrigerant passes through the three-way valve 34, the hot water supply refrigerant control valve 39, the pipe 35 a, and the hot water supply second expansion valve 36 on the secondary side of the intermediate heat exchanger 21 that functions as an evaporator. It flows into the heat transfer tube 21b.
  • the second refrigerant flowing through the secondary heat transfer tube 21b of the intermediate heat exchanger 21 is heated from the first refrigerant by exchanging heat with the first refrigerant flowing through the primary heat transfer tube 21a of the intermediate heat exchanger 21. Pumps up (absorbs heat). Then, the absorbed second refrigerant is sent from the secondary heat transfer tube 21 b of the intermediate heat exchanger 21 to the hot water supply compressor 31 and circulates in the hot water supply refrigerant circuit 30.
  • FIG. 11 is a system diagram showing the flow of the refrigerant, heat transfer medium, and heated liquid in the heat pump unit 1 in the cooling hot water supply operation (exhaust heat recovery B) mode.
  • the operation of the hot water supply circuit 50 is the same as that in the hot water supply operation mode (see FIG. 6), and the operation of the heat transfer medium circulation circuit 40 for air conditioning is the same as that in the cooling operation (normal) mode (see FIG. 7). Since the operation of 30 is the same as that in the cooling hot water supply operation (exhaust heat recovery A) mode (see FIG. 10), the description is omitted.
  • the air conditioning refrigerant circuit 10 will be described.
  • the difference between the air conditioning refrigerant circuit 10 in the cooling hot water supply operation (exhaust heat recovery A) mode (see FIG. 10) and the air conditioning refrigerant circuit 10 in the cooling hot water supply operation (exhaust heat recovery B) mode (see FIG. 11) is In the cooling hot water supply operation (exhaust heat recovery A) mode, the control device 4 rotates the air conditioning fan 15f, whereas in the cooling hot water supply operation (exhaust heat recovery B) mode, the control device 4 stops the rotation of the air conditioning fan 15f. Is a point.
  • the other control is the same as that of the air conditioning refrigerant circuit 10 in the cooling hot water supply operation (exhaust heat recovery A) mode, and thus the description thereof is omitted.
  • FIG. 12 is a system diagram showing the flow of the refrigerant, heat transfer medium, and heated liquid in the heat pump unit 1 in the cooling hot water supply operation (exhaust heat recovery C) mode.
  • the exhaust heat recovery C is the case of “air conditioning exhaust heat ⁇ hot water supply heat absorption”
  • the exhaust heat of the air conditioning refrigerant circuit 10 is recovered by the hot water supply refrigerant circuit 30 via the intermediate heat exchanger 21 and is necessary for hot water supply. Heat is absorbed from the outdoor air.
  • the operation of the hot water supply circuit 50 is the same as that in the hot water supply operation mode (see FIG.
  • the hot water supply refrigerant circuit 30 will be described.
  • the second refrigerant bypasses the hot water supply heat source side heat exchanger 35, whereas in the exhaust heat recovery C mode, the second refrigerant does not bypass the hot water supply heat source side heat exchanger 35, and does not bypass the hot water supply heat source side. This is a point through which the secondary heat transfer tubes 21b of the heat exchanger 35 and the intermediate heat exchanger 21 flow.
  • control device 4 controls the hot water supply three-way valves 34 and 37 so that the second refrigerant can flow through the hot water supply heat source side heat exchanger 19 and the intermediate heat exchanger 21, and the hot water supply refrigerant control valve. 39 is closed. Further, the control device 4 controls the opening (throttle) of the first hot water supply expansion valve 33 to fully open the second hot water supply expansion valve 36. Further, the control device 4 controls the rotation speeds of the hot water supply compressor 31 and the hot water supply fan 35f.
  • the high-temperature and high-pressure second refrigerant discharged from the hot water supply compressor 31 flows into the primary side heat transfer tube 32a of the hot water supply side heat exchanger 32 that functions as a condenser.
  • the second refrigerant flowing through the primary side heat transfer pipe 32a of the hot water supply side heat exchanger 32 exchanges heat with the heated liquid flowing through the secondary side heat transfer pipe 32b of the hot water supply side heat exchanger 32. (Exhaust heat) to become a medium temperature and high pressure second refrigerant.
  • the medium-temperature and high-pressure second refrigerant that has flowed out of the primary-side heat transfer pipe 32a of the hot-water use side heat exchanger 32 is depressurized by the hot-water supply first expansion valve 33, and becomes a low-temperature and low-pressure second refrigerant.
  • the low-temperature and low-pressure second refrigerant flows into the hot water supply heat source side heat exchanger 35 functioning as an evaporator via the hot water supply three-way valve 34.
  • the second refrigerant flowing through the hot water supply heat source side heat exchanger 35 exchanges heat with the air (outdoor air) sent by the hot water supply fan 35f, thereby drawing up heat (absorbing heat) from the air.
  • coolant which flowed out from the hot water supply heat source side heat exchanger 35 flows in into the secondary side heat exchanger tube 21b of the intermediate heat exchanger 12 which functions as an evaporator.
  • the second refrigerant flowing through the secondary heat transfer tube 21b of the intermediate heat exchanger 21 exchanges heat with the first refrigerant flowing through the primary heat transfer tube 21a of the intermediate heat exchanger 21, and heat is transferred from the first refrigerant. Pump up (absorb heat).
  • the second refrigerant flowing out of the secondary heat transfer tube 21b of the intermediate heat exchanger 21 is sent to the hot water supply compressor 31 through the hot water supply three-way valve 37 and circulates in the hot water supply refrigerant circuit 30.
  • FIG. 13 is a system diagram showing the flow of the refrigerant, the heat transfer medium, and the liquid to be heated in the heat pump unit 1 in the heating / hot water supply operation (independent) mode.
  • the flow of the refrigerant to the intermediate heat exchanger 21 is closed in the hot water supply refrigerant circuit 30.
  • the operations of the hot water supply refrigerant circuit 30 and the hot water supply circuit 50 are the same as in the hot water supply operation mode (see FIG. 6), and the operations of the air conditioning refrigerant circuit 10 and the air conditioning heat transfer medium circulation circuit 40 are in the heating operation mode (see FIG. 9). Since it is the same as that of FIG.
  • FIG. 14 is a system diagram showing the flow of the refrigerant, heat transfer medium, and heated liquid in the heat pump unit 1 in the heating hot water supply operation (air conditioning surplus heating) mode. This mode is executed when the air conditioning load (heating load) is small, and surplus heat of the air conditioning refrigerant circuit 10 is recovered by the hot water supply refrigerant circuit 30 via the intermediate heat exchanger 21.
  • the operation of the hot water supply circuit 50 is the same as that in the hot water supply operation mode (see FIG. 6), the operation of the heat transfer medium circulation circuit 40 for air conditioning is the same as that in the heating operation mode (see FIG. 9), and the operation of the refrigerant circuit 30 for hot water supply. Is the same as in the cooling hot water supply operation (exhaust heat recovery A) mode (see FIG. 10), and the description thereof is omitted.
  • the air conditioning refrigerant circuit 10 will be described.
  • the difference between the air conditioning refrigerant circuit 10 in the heating operation (mode (see FIG. 9)) and the air conditioning refrigerant circuit 10 in the heating hot water supply operation (air conditioning surplus heating) mode (see FIG. 14) is that intermediate heat exchange is performed in the heating operation mode.
  • the condenser 21 did not function as a condenser
  • the intermediate heat exchanger 21 functions as a condenser in the heating hot water supply operation (air conditioning surplus heating) mode.
  • the control device 4 controls the switching means (not shown) in the first four-way valve 12 and the second four-way valve 14 to be in the heating / hot water supply operation (air conditioning surplus heating) mode position. That is, the control device 4 controls the first four-way valve 12 so that the first refrigerant discharged from the air conditioning compressor 11 flows into the air conditioning utilization side heat exchanger 19. Further, the control device 4 controls the second four-way valve 14 so that the first refrigerant flowing out from the air conditioning heat source side heat exchanger 15 flows into the air conditioning compressor 11. Furthermore, the control device 4 controls the first expansion valve 18 for air conditioning to be fully opened, and controls the opening (throttle) of the second expansion valve 16 for air conditioning. Further, the control device 4 controls the rotational speeds of the air conditioning compressor 11 and the air conditioning fan 15f.
  • the high-temperature and high-pressure first refrigerant discharged from the air conditioning compressor 11 flows into the secondary side heat transfer pipe 19b of the air conditioning utilization side heat exchanger 19 functioning as a condenser via the first four-way valve 12.
  • the first refrigerant flowing through the secondary side heat transfer tube 19b of the air conditioning use side heat exchanger 19 radiates heat by exchanging heat with the heat transfer medium flowing through the primary side heat transfer tube 19a of the air conditioning use side heat exchanger 19. (Exhaust heat).
  • coolant flows in into the primary side heat exchanger tube 21a of the intermediate heat exchanger 21 which functions as a condenser via the 1st expansion valve 18 for air conditioning, and the 2nd four-way valve 14.
  • the first refrigerant flowing through the primary heat transfer tube 21a of the intermediate heat exchanger exchanges heat with the second refrigerant flowing through the secondary heat transfer tube 21b of the intermediate heat exchanger 21, and radiates heat (exhaust to the second refrigerant. Heat) to become a medium temperature and high pressure first refrigerant.
  • the medium-temperature and high-pressure first refrigerant is decompressed by the air conditioning second expansion valve 16 and becomes a low-temperature and low-pressure first refrigerant. Furthermore, the low-temperature and low-pressure first refrigerant flows into the air-conditioning heat source side heat exchanger 15 that functions as an evaporator. The first refrigerant flowing through the air conditioning heat source side heat exchanger 15 heats up (absorbs) heat from the air by exchanging heat with the air (outdoor air) sent by the air conditioning fan 15f. Then, the absorbed first refrigerant is sent from the air-conditioning heat source side heat exchanger 15 to the air-conditioning compressor 11 via the second four-way valve 14 and the first four-way valve 12, Circulate.
  • “hot water supply operation”, “cooling operation”, “cooling hot water operation”, “heating operation”, and “heating hot water supply operation” can be operated according to the user's request. It can be set as the air-conditioning hot-water supply system S.
  • the cooling hot water supply operation the cooling hot water supply operation (exhaust heat recovery A) mode, the cooling hot water supply operation (exhaust heat recovery B) mode, or the cooling hot water supply operation ( By executing the exhaust heat recovery C) mode (see FIG. 2), the exhaust heat of the air conditioning refrigerant circuit 10 can be efficiently used for heating hot water. Thereby, the whole efficiency of air-conditioning hot-water supply system S can be improved.
  • the air conditioner (air conditioning and hot water supply system) described in Patent Document 1 is a first compressor (this embodiment) of an air conditioning cycle (air conditioning refrigerant circuit 10) when the heating load is low during heating operation (heating and hot water supply operation).
  • the air conditioning compressor 11 is intermittently operated repeatedly between the operating state and the stopped state, so that there is a problem that the operation efficiency of the air conditioner (air conditioning hot water supply system) is lowered.
  • the primary heat transfer tube 21a (the air conditioning refrigerant circuit 10 side) of the intermediate heat exchanger 21 can be caused to function as a condenser even during a heating hot water supply operation (see FIG. 14).
  • the air conditioning hot water supply system S allows the air conditioning use side heat while the air conditioning compressor 11 remains in a continuous operation state even when the heating load is low during the heating hot water supply operation.
  • the heat is sent to the primary heat transfer tube 21a of the intermediate heat exchanger 21 (FIG. 14). reference).
  • surplus heat (the remaining portion of the high-temperature and high-pressure first refrigerant discharged from the air-conditioning compressor 11) is transferred to the primary side of the intermediate heat exchanger 21. It can be sent to the heat transfer tube 21a. As a result, the amount of heat necessary for air conditioning can be secured without complicated control, and surplus air conditioning heat can be supplied to the hot water supply refrigerant circuit 30 via the intermediate heat exchanger 21.
  • the air conditioning and hot water supply system S can cause the intermediate heat exchanger 21 to function as a condenser regardless of the cooling operation / heating operation.
  • heat exhaust heat, surplus heat
  • FIG. 15 is a graph showing the variation of the heating load on the days before and after the coldest day in Tokyo.
  • the vertical axis indicates the heating load [kW] (indicated by a solid line on the graph of FIG. 15), the outdoor air temperature [° C.] (indicated by the broken line on the graph of FIG. 15), and the amount of solar radiation [MJ] (FIG. 15).
  • the horizontal axis is time [day], the day before the coldest day (time 1.0 to 2.0 [day]) (time 0.0 to 1.0 [day]) ) To the next day (time 2.0 to 3.0 [day]).
  • the heating load was calculated
  • the air conditioning compressor 11 of the air conditioning refrigerant circuit 10 may be intermittently operated.
  • the heating load suddenly decreases during the day (in FIG. 15, from about 4.0 kW to about 0.6 kW).
  • the air conditioning compressor 11 of the air conditioning refrigerant circuit 10 is intermittently operated. Such intermittent operation is not desirable in terms of operation efficiency. In this way, the energy saving effect obtained when the air conditioning system (air conditioning hot water supply system) is actually operated is compared with the energy saving effect expected by reducing the heating load by increasing the heat insulation of the house. 11 was intermittent because of intermittent operation.
  • the air conditioning hot water supply system S can prevent intermittent operation of the air conditioning compressor 11 of the air conditioning refrigerant circuit 10 even when the heating load is low during the heating operation. it can.
  • the air conditioning and hot water supply system S according to the present embodiment can cause the primary heat transfer tube 21a of the intermediate heat exchanger 21 to function as a condenser even during heating operation, so that the excess heat of the air conditioning refrigerant circuit 10 is supplied with hot water. Therefore, the efficiency of the air conditioning hot water supply system S as a whole can be improved.
  • the air conditioning and hot water supply system S determines the operation mode according to environmental conditions, setting conditions input from a remote controller (not shown), and the like. And if the air-conditioning hot-water supply system S needs to supply the exhaust heat of the 1st refrigerant
  • the air conditioning and hot water supply system S performs the natural circulation in the hot water supply refrigerant circuit 30 even when the air conditioning load during the cooling operation is an overload, and the hot water supply refrigerant circuit 30 does not perform the intermediate heat exchanger 10.
  • an air conditioning heat source side heat exchanger 15, an air conditioning utilization side heat exchanger 19, and an intermediate heat exchanger 21 are connected in series via various valves in the refrigerant circuit 10 for air conditioning.
  • the hot water supply side heat exchanger 32, the hot water supply heat source side heat exchanger 35, and the intermediate heat exchanger 21 are connected in series via various valves. If the heat exchanger is connected in parallel in the air conditioning refrigerant circuit 10 or the hot water supply refrigerant circuit 30 and the opening / closing of various valves is controlled according to the operation mode, depending on the refrigerant distribution in the pipe, Excess refrigerant may be generated. In this case, it is necessary to first adjust the refrigerant distribution state in the circuit before starting the operation.
  • the air conditioning and hot water supply system S since the heat exchangers are connected in series in each circuit as described above, it is not necessary to adjust the distribution of the refrigerant in the circuit. This is because the refrigerant circulates in the air conditioning refrigerant circuit 10 and the hot water supply refrigerant circuit 30 without being diverted. Therefore, in the air conditioning and hot water supply system S according to this embodiment, the operation can be started smoothly when the operation mode is switched, and the processing load on the control device 4 can be reduced.
  • the first refrigerant is caused to flow by fully opening the air conditioning first expansion valve 18 in the air conditioning refrigerant circuit 10, but the present invention is not limited thereto.
  • a bypass pipe having one end connected to the lower port of the second four-way valve 14 and the other end connected to the air conditioning first expansion valve 18 may be provided, and the two-way valve may be installed in the bypass pipe.
  • the control device 4 closes the two-way valve and controls the opening (throttle) of the air conditioning first expansion valve 18.
  • the control device 4 performs control to open the two-way valve and close the first expansion valve 18 for air conditioning. The same applies to the second expansion valve 16 for air conditioning.
  • the expansion valve (the first expansion valve 18 and the second expansion valve 16) has a higher pressure loss when fully opened than the two-way valve, and therefore the refrigerant passes through the intermediate heat exchanger without reducing pressure. In addition, when the refrigerant passes through the expansion valve, the amount of exchange heat decreases due to pressure loss.
  • pressure loss when each expansion valve is not used as a decompression device is reduced. be able to. Thereby, the efficiency of the entire air conditioning and hot water supply system S can be further improved.
  • the first expansion valve 18 and the second expansion valve 16 have been described as variable throttles capable of continuously increasing or decreasing the throttle amount (opening degree), but the present invention is not limited to this. That is, a fixed-throttle valve that switches between two patterns (large and small) as the throttle amount, and a low pressure loss valve may be adopted as the first expansion valve 18 and the second expansion valve 16. In this case, as described above, the pressure loss in each expansion valve can be reduced without installing bypass piping and on-off valves in the air conditioning first expansion valve 18 and / or the air conditioning second expansion valve 16. it can. Thus, the efficiency of the entire air conditioning and hot water supply system S can be improved, and the manufacturing cost can be reduced.
  • the 1st expansion valve 18 for air conditioning was used as a decompression device, it is not restricted to this. .
  • the air conditioning second expansion valve 16 may be used as a pressure reducing device.
  • the first refrigerant flowing out from the second heat transfer pipe 19 b of the air conditioning utilization side heat exchanger 19 flows into the intermediate heat exchanger 21 via the air conditioning first expansion valve 18, and the air conditioning heat source side Switching means (not shown) for the second four-way valve 14 so that the first refrigerant flowing out of the heat exchanger 15 flows into the air conditioning compressor 11 via the second four-way valve 14 and the first four-way valve 12.
  • Control The control device 4 fully opens the air conditioning first expansion valve 18 and controls the opening (throttle) of the air conditioning second expansion valve 16.
  • the air conditioning first expansion valve 18 functions as a pressure reducing device
  • the heating operation In Step S110 of FIG. 2 and Steps S203 and S204 of FIG. 3, the air conditioning second expansion valve 16 functions as a pressure reducing device.
  • the heat transfer medium is heated (or cooled) by the air conditioning utilization side heat exchanger 19 in the heat pump unit 1, supplied to the indoor unit 2, and heated by the indoor heat exchanger 43 of the indoor unit 2.
  • the present invention is not limited to this. That is, the heat transfer medium circulation circuit 40 for air conditioning is omitted, the air conditioning utilization side heat exchanger 19 is installed in the indoor unit 2, and the space between the first refrigerant flowing through the air conditioning utilization side heat exchanger 19 and the room air. It is good also as a structure which heats (or cools) by exchanging heat with.
  • a to-be-heated liquid is water
  • a high temperature to-be-heated liquid (hot water) is stored in the tank 52
  • the high-temperature to-be-heated liquid (hot water) stored in the tank 52 is a hot water supply terminal (FIG.
  • the present invention is not limited to this. That is, a heat exchanger (not shown) capable of exchanging heat between the hot heated liquid stored in the tank 52 and the feed water supplied to the hot water supply terminal (not shown) is further provided.
  • the structure which heats water supply with the heated high temperature heated liquid, and supplies hot water to a hot-water supply terminal (not shown) may be sufficient.
  • the liquid to be heated is not limited to water.
  • the hot water supply three-way valve 34 is used to pass the first refrigerant flowing from the hot water supply first expansion valve 33 to the hot water supply heat source side heat exchanger 35 or the hot water supply refrigerant control valve 39. Not limited to this. That is, even if it has a configuration in which two flow rate control valves are provided so that the first refrigerant flowing from the first hot water supply expansion valve 33 flows through the first hot water supply expansion valve 33 or the hot water supply heat source side heat exchanger 35. Good. The same applies to the three-way valve 37 for hot water supply.
  • S air-conditioning hot water supply system 10 air-conditioning refrigerant circuit 11 air-conditioning compressor 12 first four-way valve (first switching means) 14 Second four-way valve (second switching means) 15 Air Conditioning Heat Source Side Heat Exchanger 16 Air Conditioning Second Expansion Valve (Air Conditioning Pressure Reduction Device, Air Conditioning Second Pressure Reduction Device) 18 First expansion valve for air conditioning (pressure reducing device for air conditioning, first pressure reducing device for air conditioning) DESCRIPTION OF SYMBOLS 19 Air-conditioning use side heat exchanger 21 Intermediate heat exchanger 30 Hot-water supply refrigerant circuit 31 Hot-water supply compressor 32 Hot-water supply-side heat exchanger 33 Hot-water supply first expansion valve (hot-water supply decompression device) 34,37 Three-way valve for hot water supply (switching means) 35 Hot water supply heat source side heat exchanger 36 Second expansion valve for hot water supply (pressure reducing device for hot water supply) 39 Refrigerant control valve for hot water supply (switching means)

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

L'invention porte sur un système de climatisation/approvisionnement d'eau chaude qui donne la possibilité d'améliorer le rendement global d'un système de climatisation/approvisionnement d'eau chaude. Le système de climatisation/approvisionnement d'eau chaude comprend un compresseur de climatisation (11), un échangeur de chaleur côté source de chaleur de climatisation (15), un échangeur de chaleur intermédiaire (21), un dispositif de décompression de climatisation (17, 18), un échangeur de chaleur côté utilisation de la climatisation (19), un premier moyen de commutation (12) et un second moyen de commutation (14). Le premier moyen de commutation (12) commute la direction d'un premier fluide frigorigène qui circule dans l'échangeur de chaleur côté utilisation de la climatisation (19) pendant une opération de refroidissement et une opération de chauffage. Le second moyen de commutation (14) fait fonctionner l'échangeur de chaleur intermédiaire (21) comme condenseur pour le premier fluide frigorigène par commutation, en fonction du mode de fonctionnement, de la direction du premier fluide frigorigène qui circule dans l'échangeur de chaleur côté source de chaleur de climatisation (15) et dans l'échangeur de chaleur intermédiaire (21).
PCT/JP2011/077531 2011-11-29 2011-11-29 Système de climatisation et d'approvisionnement d'eau chaude WO2013080297A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PCT/JP2011/077531 WO2013080297A1 (fr) 2011-11-29 2011-11-29 Système de climatisation et d'approvisionnement d'eau chaude
JP2013546876A JP5788526B2 (ja) 2011-11-29 2011-11-29 空調給湯システム
EP11876541.1A EP2787304A4 (fr) 2011-11-29 2011-11-29 Système de climatisation et d'approvisionnement d'eau chaude

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2011/077531 WO2013080297A1 (fr) 2011-11-29 2011-11-29 Système de climatisation et d'approvisionnement d'eau chaude

Publications (1)

Publication Number Publication Date
WO2013080297A1 true WO2013080297A1 (fr) 2013-06-06

Family

ID=48534823

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2011/077531 WO2013080297A1 (fr) 2011-11-29 2011-11-29 Système de climatisation et d'approvisionnement d'eau chaude

Country Status (3)

Country Link
EP (1) EP2787304A4 (fr)
JP (1) JP5788526B2 (fr)
WO (1) WO2013080297A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11067315B2 (en) * 2018-11-07 2021-07-20 Shinwa Controls Co., Ltd Temperature control system
US20220333843A1 (en) * 2021-04-16 2022-10-20 Guangdong Giwee Technology Co. Ltd. Three-pipe multi-split air conditioning system and control method thereof

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108885031B (zh) * 2016-04-21 2020-06-19 三菱电机株式会社 排热回收式空气调和装置
CN106288562B (zh) * 2016-08-16 2019-01-04 东北电力大学 一种空气源热泵系统的除霜控制装置及其方法
CN106288484B (zh) * 2016-08-16 2019-01-04 东北电力大学 一种空气源热泵系统及其除霜控制方法
EP4063762A1 (fr) * 2021-03-26 2022-09-28 Mitsubishi Electric R&D Centre Europe B.V. Système de pompe à chaleur en cascade à refrigérant à faible effet de serre

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58136959A (ja) * 1982-02-05 1983-08-15 三菱電機株式会社 ヒ−トポンプ暖房・給湯装置
JPS5921959A (ja) * 1982-07-28 1984-02-04 ミサワホ−ム株式会社 熱源ユニツト
JPH04143559A (ja) * 1990-10-02 1992-05-18 Matsushita Electric Ind Co Ltd 熱ポンプ装置
JP2005257231A (ja) * 2004-03-15 2005-09-22 Fujitsu General Ltd ヒートポンプ給湯エアコン
JP2005299935A (ja) 2004-04-06 2005-10-27 Fujitsu General Ltd 空気調和装置
WO2011104834A1 (fr) * 2010-02-24 2011-09-01 株式会社 日立製作所 Dispositif de conditionnement d'air

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5026205Y1 (fr) * 1969-12-29 1975-08-05
JPS6152564A (ja) * 1984-08-22 1986-03-15 株式会社日立製作所 冷暖房給湯装置
JP2005249319A (ja) * 2004-03-05 2005-09-15 Fujitsu General Ltd ヒートポンプ給湯エアコン
JP4811167B2 (ja) * 2006-07-24 2011-11-09 ダイキン工業株式会社 空気調和システム
WO2011108068A1 (fr) * 2010-03-01 2011-09-09 株式会社 日立製作所 Système de climatisation et de fourniture d'eau chaude
WO2012114461A1 (fr) * 2011-02-22 2012-08-30 株式会社日立製作所 Système de conditionnement d'air/d'alimentation en eau chaude et procédé de commande d'un tel système
JP5492346B2 (ja) * 2011-02-22 2014-05-14 株式会社日立製作所 空調給湯システム
WO2013061473A1 (fr) * 2011-10-28 2013-05-02 株式会社日立製作所 Dispositif de distribution d'eau chaude et de climatisation

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58136959A (ja) * 1982-02-05 1983-08-15 三菱電機株式会社 ヒ−トポンプ暖房・給湯装置
JPS5921959A (ja) * 1982-07-28 1984-02-04 ミサワホ−ム株式会社 熱源ユニツト
JPH04143559A (ja) * 1990-10-02 1992-05-18 Matsushita Electric Ind Co Ltd 熱ポンプ装置
JP2005257231A (ja) * 2004-03-15 2005-09-22 Fujitsu General Ltd ヒートポンプ給湯エアコン
JP2005299935A (ja) 2004-04-06 2005-10-27 Fujitsu General Ltd 空気調和装置
WO2011104834A1 (fr) * 2010-02-24 2011-09-01 株式会社 日立製作所 Dispositif de conditionnement d'air

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2787304A4 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11067315B2 (en) * 2018-11-07 2021-07-20 Shinwa Controls Co., Ltd Temperature control system
US20220333843A1 (en) * 2021-04-16 2022-10-20 Guangdong Giwee Technology Co. Ltd. Three-pipe multi-split air conditioning system and control method thereof

Also Published As

Publication number Publication date
EP2787304A4 (fr) 2015-09-16
JPWO2013080297A1 (ja) 2015-04-27
JP5788526B2 (ja) 2015-09-30
EP2787304A1 (fr) 2014-10-08

Similar Documents

Publication Publication Date Title
JP5492346B2 (ja) 空調給湯システム
KR101623746B1 (ko) 지열 에너지를 활용한 2단 가열식 지열 시스템
JP5788526B2 (ja) 空調給湯システム
US20130167559A1 (en) Heat pump and control method thereof
US20110138839A1 (en) Water circulation apparatus associated with refrigerant system
JP5920251B2 (ja) 暖房給湯装置
WO2018116410A1 (fr) Climatiseur
KR101341533B1 (ko) 가스히트펌프 시스템 및 이의 제어방법
JPWO2013161011A1 (ja) 空調給湯システム
EP3690356A1 (fr) Dispositif à cycle frigorifique
JP5629280B2 (ja) 排熱回収システムおよびその運転方法
JP5681787B2 (ja) ２元冷凍サイクル装置
EP2607809B1 (fr) Chauffage hydronique
WO2013061473A1 (fr) Dispositif de distribution d'eau chaude et de climatisation
CN105890225A (zh) 一种部分热回收型空调冷热水及生活热水联合供应系统
KR101497210B1 (ko) 하이브리드 냉난방시스템 및 장치
KR101647285B1 (ko) 단일의 열교환기를 이용하여 축냉 및 방냉 또는 축열 및 방열을 순차 또는 동시에 수행하는 수축열 냉난방장치 및 이의 제어방법
JP2012013350A (ja) 温水暖房装置
EP2339267B1 (fr) Appareil à cycle de réfrigération, climatiseur d'air alimenté en eau chaude de type pompe à chaleur et unité d'extérieur correspondante
JP5150300B2 (ja) ヒートポンプ式給湯装置
US10465935B2 (en) Air-conditioning apparatus
KR101166858B1 (ko) 지열원 냉난방 히트펌프용 냉난방 및 급탕 시스템
JP6143682B2 (ja) 複合熱源ヒートポンプ装置
KR101461599B1 (ko) 제상 및 압축효율이 개선되는 공기조화기
JP2012215353A (ja) 二元冷凍サイクル装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 11876541

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2013546876

Country of ref document: JP

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: 2011876541

Country of ref document: EP

NENP Non-entry into the national phase

Ref country code: DE