US20250003645A1 - Refrigeration cycle apparatus - Google Patents

Refrigeration cycle apparatus Download PDF

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Publication number
US20250003645A1
US20250003645A1 US18/697,230 US202118697230A US2025003645A1 US 20250003645 A1 US20250003645 A1 US 20250003645A1 US 202118697230 A US202118697230 A US 202118697230A US 2025003645 A1 US2025003645 A1 US 2025003645A1
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Prior art keywords
refrigerant
heat exchanger
connect
flow path
compressor
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English (en)
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Shunya GYOTOKU
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • 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
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/13—Economisers

Definitions

  • the present disclosure relates to a refrigeration cycle apparatus.
  • Japanese Patent Laying-Open No. 2020-186909 discloses an injection circuit that causes part of refrigerant flowing from a heat exchanger to an expansion mechanism to be supplied to a suction side of a compressor, in which the heat exchanger serves as a heat radiator among a heat source-side heat exchanger and a use-side heat exchanger.
  • the injection circuit disclosed in Japanese Patent Laying-Open No. 2020-186909 (PTL 1) is configured such that, in any of heating, cooling, and defrosting operations, part of liquid refrigerant before passing through the expansion mechanism is introduced into the injection circuit from a refrigerant outlet portion of a heat exchanger serving as a heat radiator.
  • performance improvement by the injection circuit can be expected in any of the heating, cooling and defrosting operations.
  • the present disclosure has been made in order to describe the embodiments that solve the above-described problems, and an object of the present disclosure is to provide a refrigeration cycle apparatus capable of improving the efficiency of a heat exchanger while improving the performance by an injection circuit.
  • the present disclosure relates to a refrigeration cycle apparatus.
  • the refrigeration cycle apparatus includes: a compressor; a first heat exchanger; a second heat exchanger; a third heat exchanger; a first expansion valve; a second expansion valve; and a flow path switching device.
  • the compressor, the first heat exchanger, the second heat exchanger, and the first expansion valve constitute a refrigerant circuit through which refrigerant circulates.
  • the second expansion valve forms a portion of an injection flow path, the injection flow path being configured to reduce pressure of the refrigerant before passing through the first expansion valve in the refrigerant circuit and return the refrigerant to the compressor.
  • the third heat exchanger includes a first flow path through which the refrigerant flows and a second flow path through which the refrigerant flows.
  • the third heat exchanger is configured to exchange heat between the refrigerant passing through the first flow path and the refrigerant passing through the second flow path.
  • the first flow path is disposed in the refrigerant circuit to cause the refrigerant to flow toward the first expansion valve.
  • the second flow path is disposed to return, to the compressor, the refrigerant that has passed through the second expansion valve.
  • the flow path switching device is configured to: connect a discharge port of the compressor to a refrigerant inlet of the first heat exchanger; connect a refrigerant outlet of the first heat exchanger to a refrigerant inlet of the first flow path; connect a refrigerant outlet of the first expansion valve to a refrigerant inlet of the second heat exchanger; and connect a refrigerant outlet of the second heat exchanger to a suction port of the compressor.
  • the flow path switching device is configured to: connect the discharge port of the compressor to the refrigerant inlet of the second heat exchanger; connect the refrigerant outlet of the second heat exchanger to the refrigerant inlet of the first flow path; connect the refrigerant outlet of the first expansion valve to the refrigerant inlet of the first heat exchanger; and connect the refrigerant outlet of the first heat exchanger to the suction port of the compressor.
  • the flow direction of the refrigerant does not change and a branch portion of the injection flow path is located on the inlet side of the first expansion valve, and thereby, the performance of the refrigeration cycle apparatus is improved in any of the plurality of operation modes.
  • FIG. 1 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to a first embodiment.
  • FIG. 2 is a diagram showing a refrigerant circuit and a flow of refrigerant during a heating operation of the refrigeration cycle apparatus according to the first embodiment.
  • FIG. 3 is a diagram showing an arrangement of various sensors when refrigerant having no temperature gradient is used.
  • FIG. 4 is a p-h diagram showing a change in the state of refrigerant when refrigerant having no temperature gradient is used.
  • FIG. 5 is a flowchart for illustrating control of a second expansion valve 72 when refrigerant having no temperature gradient is used.
  • FIG. 6 is a diagram for illustrating symbols of various parameters of a first expansion valve 30 .
  • FIG. 7 is a diagram for illustrating a process of deriving inlet portion pressure of first expansion valve 30 .
  • FIG. 8 is a diagram showing an arrangement of various sensors when non-azeotropic refrigerant is used.
  • FIG. 9 is a p-h diagram showing a change in the state of refrigerant when non-azeotropic refrigerant is used.
  • FIG. 10 is a flowchart for illustrating control of second expansion valve 72 when non-azeotropic refrigerant is used.
  • FIG. 11 is a diagram showing a refrigerant circuit and a flow of refrigerant during a cooling operation of a refrigeration cycle apparatus according to a second embodiment.
  • FIG. 12 is a diagram showing the refrigerant circuit and the flow of the refrigerant during a heating operation of the refrigeration cycle apparatus according to the second embodiment.
  • FIG. 13 is a diagram showing a refrigerant circuit and a flow of refrigerant during a cooling operation of a refrigeration cycle apparatus according to a third embodiment.
  • FIG. 14 is a diagram showing the refrigerant circuit and the flow of the refrigerant during a heating operation of the refrigeration cycle apparatus according to the third embodiment.
  • FIG. 15 is a diagram showing a refrigerant circuit and a flow of refrigerant during a cooling operation of a refrigeration cycle apparatus according to a fourth embodiment.
  • FIG. 16 is a diagram showing the refrigerant circuit and the flow of the refrigerant during a heating operation of the refrigeration cycle apparatus according to the fourth embodiment.
  • FIG. 17 is a diagram showing a refrigerant circuit and a flow of refrigerant during a cooling operation of a refrigeration cycle apparatus according to a fifth embodiment.
  • FIG. 18 is a diagram showing the state of an eight-way valve 50 B and the flow of the refrigerant in eight-way valve 50 B during the cooling operation according to the fifth embodiment.
  • FIG. 19 is a diagram showing the refrigerant circuit and the flow of the refrigerant during a heating operation of the refrigeration cycle apparatus according to the fifth embodiment.
  • FIG. 20 is a diagram showing the state of eight-way valve 50 B and the flow of the refrigerant in eight-way valve 50 B during the heating operation according to the fifth embodiment.
  • FIG. 1 is a refrigerant circuit diagram of a refrigeration cycle apparatus according to the first embodiment.
  • FIG. 1 shows a refrigerant circuit and a flow of refrigerant during a cooling operation.
  • the refrigerant circuit and the flow of refrigerant shown in FIG. 1 are also similarly applied in a defrosting operation performed during a heating operation.
  • a refrigeration cycle apparatus 1 includes a compressor 10 , a first heat exchanger 20 , a second heat exchanger 40 , a third heat exchanger 80 , a first expansion valve 30 , a second expansion valve 72 , and a flow path switching device 50 .
  • Compressor 10 first heat exchanger 20 , second heat exchanger 40 , first expansion valve 30 , and pipes 91 to 99 constitute a refrigerant circuit 90 through which refrigerant circulates.
  • First heat exchanger 20 is configured to exchange heat between the outdoor air blown by a fan 23 and the refrigerant.
  • Second heat exchanger 40 is configured to exchange heat between a heat medium circulating through the use-side circuit and the refrigerant.
  • Second heat exchanger 40 is a plate-type heat exchanger, for example.
  • the use-side circuit includes a pump WP, a use-side heat exchanger 123 , and pipes 121 , 122 , and 124 .
  • the heat medium circulating through the use-side circuit is, for example, water, brine, or the like.
  • Use-side heat exchanger 123 is, for example, a water heater, an air-conditioner for heating or cooling, or the like.
  • Second heat exchanger 40 includes flow paths 41 and 42 . Second heat exchanger 40 is configured to exchange heat between the refrigerant flowing through flow path 41 and the heat medium flowing through flow path 42 .
  • An injection flow path 70 includes pipes 71 and 73 and a second expansion valve 72 .
  • Injection flow path 70 reduces the pressure of the refrigerant before passing through first expansion valve 30 in refrigerant circuit 90 and returns the refrigerant to compressor 10 .
  • Third heat exchanger 80 includes a first flow path 81 and a second flow path 82 through which refrigerant flows. Third heat exchanger 80 is configured to exchange heat between the refrigerant passing through first flow path 81 and the refrigerant passing through second flow path 82 .
  • First flow path 81 is disposed in refrigerant circuit 90 to cause the refrigerant to flow toward first expansion valve 30 , and second flow path 82 is disposed to return, to compressor 10 , the refrigerant having passed through second expansion valve 72 .
  • flow path switching device 50 is configured to connect a discharge port of compressor 10 to a refrigerant inlet 21 of first heat exchanger 20 , connect a refrigerant outlet of first heat exchanger 20 to a refrigerant inlet of first flow path 81 , connect a refrigerant outlet of first expansion valve 30 to a refrigerant inlet of second heat exchanger 40 , and connect a refrigerant outlet of second heat exchanger 40 to a suction port of compressor 10 .
  • the first operation mode not only a defrosting operation during cooling but also a defrosting operation during heating may be performed.
  • flow path switching device 50 may have various configurations, but the first embodiment provides an example in which flow path switching device 50 includes a first four-way valve 51 and a second four-way valve 52 .
  • First four-way valve 51 has ports PA, PB, PC, and PD.
  • Second four-way valve 52 has ports PE, PF, PG, and PH.
  • Pipe 91 connects the discharge port of compressor 10 to port PA.
  • Pipe 92 connects port PB to refrigerant inlet 21 of first heat exchanger 20 .
  • Pipe 93 connects a refrigerant outlet 22 of first heat exchanger 20 to port PF.
  • Pipe 94 connects port PE to the refrigerant inlet of first flow path 81 .
  • Pipe 95 connects a refrigerant outlet of first flow path 81 to a refrigerant inlet of first expansion valve 30 .
  • Pipe 96 connects the refrigerant outlet of first expansion valve 30 to port PC.
  • Pipe 97 connects port PD to the refrigerant inlet of second heat exchanger 40 .
  • Pipe 98 connects the refrigerant outlet of second heat exchanger 40 to port PH.
  • Pipe 99 connects port PG to the suction port of compressor 10 .
  • Pipe 71 branches from pipe 95 and connects pipe 95 to a refrigerant inlet of second flow path 82 .
  • Second expansion valve 72 is disposed somewhere in the middle of pipe 71 .
  • Pipe 73 connects a refrigerant outlet of second flow path 82 to an intermediate pressure port of compressor 10 .
  • Refrigeration cycle apparatus 1 further includes a controller 100 that controls flow path switching device 50 .
  • Controller 100 is configured to include a central processing unit (CPU) 101 , a memory 102 (a read only memory (ROM)) and a random access memory (RAM)), an input/output buffer (not shown), and the like.
  • CPU 101 deploys a program stored in the ROM into the RAM or the like and executes the program.
  • the programs stored in the ROM describe the processing procedure for controller 100 .
  • Controller 100 controls each of devices in refrigeration cycle apparatus 1 according to these programs. Such control is not necessarily processed by software, but can also be processed by dedicated hardware (an electronic circuit).
  • control of flow path switching device 50 executed by controller 100 in response to switching of the operation mode is described.
  • first four-way valve 51 is set such that port PA communicates with port PB and port PC communicates with port PD.
  • first four-way valve 51 is set such that port PA does not communicate with port PD and port PB does not communicate with port PC.
  • first four-way valve 51 is configured to connect the discharge port of compressor 10 to refrigerant inlet 21 of first heat exchanger 20 and connect the refrigerant outlet of first expansion valve 30 to the refrigerant inlet of second heat exchanger 40 .
  • second four-way valve 52 In the first operation mode (cooling), as indicated by solid lines in FIG. 1 , second four-way valve 52 is set such that port PE communicates with port PF and port PG communicates with port PH. On the other hand, as indicated by broken lines in FIG. 1 , second four-way valve 52 is set such that port PE does not communicate with port PH and port PF does not communicate with port PG. In other words, in the first operation mode (cooling), second four-way valve 52 is configured to connect the refrigerant outlet of first heat exchanger 20 to the refrigerant inlet of first flow path 81 and connect the refrigerant outlet of second heat exchanger 40 to the suction port of compressor 10 .
  • FIG. 2 is a diagram showing the refrigerant circuit and the flow of the refrigerant during the heating operation of the refrigeration cycle apparatus according to the first embodiment.
  • flow path switching device 50 is configured to connect the discharge port of compressor 10 to the refrigerant inlet of second heat exchanger 40 , connect the refrigerant outlet of second heat exchanger 40 to the refrigerant inlet of first flow path 81 , connect the refrigerant outlet of first expansion valve 30 to refrigerant inlet 21 of first heat exchanger 20 , and connect refrigerant outlet 22 of first heat exchanger 20 to the suction port of compressor 10 .
  • the second operation mode not only a heating operation but also a warming operation to warm cold water by a water heater may be performed.
  • first four-way valve 51 is set such that port PA communicates with port PD and port PC communicates with port PB.
  • first four-way valve 51 is set such that port PA does not communicate with port PB and port PC does not communicate with port PD.
  • first four-way valve 51 is configured to connect the discharge port of compressor 10 to the refrigerant inlet of second heat exchanger 40 and connect the refrigerant outlet of first expansion valve 30 to the refrigerant inlet of first heat exchanger 20 .
  • second four-way valve 52 In the second operation mode (heating), second four-way valve 52 is set such that port PE communicates with port PH and port PG communicates with port PF. On the other hand, as indicated by broken lines in FIG. 2 , second four-way valve 52 is set such that port PE does not communicate with port PF and port PG does not communicate with port PH. In other words, in the second operation mode (heating), second four-way valve 52 is configured to connect the refrigerant outlet of second heat exchanger 40 to the refrigerant inlet of first flow path 81 and connect the refrigerant outlet of first heat exchanger 20 to the suction port of compressor 10 .
  • the heat exchange efficiency of the heat exchanger is higher in the relation in which the heat medium that exchanges heat flows as a counterflow than in the relation in which the heat medium flows as a parallel-flow.
  • the heat exchange efficiency in one of the two operation modes tends to deteriorate.
  • flow path switching device 50 is controlled to cause the refrigerant to flow in the same direction in any of the first operation mode (cooling) and the second operation mode (heating) in each of first heat exchanger 20 , second heat exchanger 40 , and third heat exchanger 80 .
  • Controller 100 calculates the degree of dryness of the refrigerant in pipe 95 on the inlet side of each of first expansion valve 30 and second expansion valve 72 , and controls second expansion valve 72 such that the degree of dryness reaches a target value. If the degree of dryness of the refrigerant in pipe 95 rises too high, the gas-phase refrigerant is mixed into the inlets of first expansion valve 30 and second expansion valve 72 , so that the pressure adjusting performance of the expansion valves decreases. Accordingly, when the degree of dryness rises too high, controller 100 controls the degree of opening of second expansion valve 72 to decrease the degree of dryness.
  • FIG. 3 is a diagram showing an arrangement of various sensors when refrigerant having no temperature gradient is used. Controller 100 controls the degree of opening of second expansion valve 72 based on the outputs from various sensors shown in FIG. 3 .
  • Refrigeration cycle apparatus 1 includes pressure sensors 110 and 116 , temperature sensors 112 , 114 , 115 , and 117 , and a flow rate sensor 113 .
  • Pressure sensor 110 detects a discharge pressure Pd[MPa] of compressor 10 .
  • Pressure sensor 116 detects a suction pressure P s [MPa] of compressor 10 .
  • Temperature sensor 112 detects a refrigerant inlet temperature T e,in [° C.] of second heat exchanger 40 .
  • Temperature sensor 117 detects a refrigerant suction temperature Ts[° C.] of compressor 10 .
  • Temperature sensor 115 detects an inlet water temperature T w,in [° C.] of second heat exchanger 40 .
  • Temperature sensor 114 detects an outlet water temperature T w,out [° C.] of second heat exchanger 40 .
  • Flow rate sensor 113 detects a flow rate V w [L/min] of water in second heat exchanger 40 .
  • FIG. 4 is a p-h diagram showing a change in the state of refrigerant when refrigerant having no temperature gradient is used.
  • the refrigerant discharged from compressor 10 flows through refrigerant circuit 90 , and the state of the refrigerant changes in order of states A, B, C, D, and E.
  • the refrigerant branched from the outlet portion of first flow path 81 of refrigerant circuit 90 flows through injection flow path 70 and the state of the refrigerant changes in order of states C, F, and G.
  • the refrigerant in state J compressed to intermediate pressure by compressor 10 merges with the refrigerant in state G supplied through injection flow path 70 , thus resulting in refrigerant in state K.
  • the refrigerant in state K is further compressed by compressor 10 , thus resulting in refrigerant in state A.
  • a target degree of dryness X tgt is set such that state C is not significantly apart from a liquidus line, and controller 100 controls the degree of opening of second expansion valve 72 to achieve the target degree of dryness X tgt .
  • FIG. 5 is a flowchart for illustrating control of second expansion valve 72 when refrigerant having no temperature gradient is used.
  • Cv main [mm 2 ] represents a Cv value of an expansion valve 30 .
  • C p,w [kJ/(kg ⁇ K)] represents a specific heat of water.
  • F comp [Hz] represents an operating frequency of compressor 10 .
  • Gr s [kg/h] represents a refrigerant circulation amount at the suction port of compressor 10 .
  • P d [MPa] represents pressure of the refrigerant discharged from compressor 10 .
  • P s [MPa] represents pressure of the refrigerant suctioned into compressor 10 .
  • T e,in [° C.] represents a temperature of the refrigerant at the inlet of the evaporator.
  • Ts[° C.] represents a temperature of the refrigerant suctioned into compressor 10 .
  • T w,in [° C.] represents a temperature of water at an inlet of a heat exchanger 40 .
  • T w,out [° C.] represents a temperature of water at an outlet of heat exchanger 40 .
  • V w [L/min] represents a flow rate of water in heat exchanger 40 .
  • V st [cc] represents a stroke volume of compressor 10 .
  • ⁇ v [ ⁇ ] represents volumetric efficiency of compressor 10 .
  • ⁇ LEV,in [kg/m] represents a refrigerant density at the inlet of expansion valve 30 .
  • ⁇ s [kg/m 3 ] represents a density of the refrigerant suctioned into compressor 10 .
  • h s represents an enthalpy at the suction port of compressor 10 .
  • fx(A,B) represents a function adopting A and B as inputs and x as an output, and this function is mapped in advance.
  • step S 1 controller 100 calculates a cooling capability Q e by the following equation (1).
  • controller 100 calculates a refrigerant circulation amount Gr s on the low pressure side by the following equation (2).
  • G ⁇ r s Fcomp ⁇ V s ⁇ t ⁇ f ⁇ ⁇ s ( P s , T s ) ⁇ ⁇ v ( 2 )
  • step S 3 controller 100 calculates an evaporator inlet enthalpy h e,in and an evaporator inlet pressure P e,in by the following equations (3) and (4), respectively.
  • controller 100 calculates a pressure P LEV,in and a degree of dryness X LEV,in of the refrigerant at the inlet portion of expansion valve 30 by the following equations (5) and (6), respectively.
  • P LEV , in f PLEV , in ( G ⁇ r s , P e , in , Cv main , f ⁇ ⁇ LEV , in ( P LEV , in , h e , in ) ) ( 5 )
  • X LEV , in f XLEV , in ( P LEV , in , h e , in ) ( 6 )
  • the degree of dryness X is defined such that 0 ⁇ X ⁇ 1 in the case of two-phase refrigerant, X ⁇ 0 in the case of liquid refrigerant (supercooled liquid), and X is negative in the case of supercooled liquid.
  • controller 100 calculates the target degree of dryness X tgt of the refrigerant at the inlet portion of expansion valve 30 by the following equation (7).
  • step S 6 controller 100 compares the target degree of dryness X tgt with the calculated current degree of dryness X LEV,in .
  • the degree of dryness X LEV,in is equal to or less than the target degree of dryness X tgt (YES in S6)
  • step S 7 controller 100 decreases the degree of opening of second expansion valve 72 disposed in injection flow path 70 .
  • step S 8 controller 100 increases the degree of opening of second expansion valve 72 disposed in injection flow path 70 .
  • controller 100 controls the degree of opening of second expansion valve 72 such that the degree of dryness X LEV,in of the refrigerant flowing into first expansion valve 30 from first flow path 81 of third heat exchanger 80 does not increase above the target degree of dryness X tgt .
  • FIG. 6 is a diagram for illustrating symbols of various parameters of first expansion valve 30 .
  • First expansion valve 30 includes a stator coil 31 and a rotor 32 of a pulse motor, a screw 33 , and a needle 34 .
  • rotor 32 rotates, the amount of needle 34 inserted into an orifice 35 by screw 33 is changed. Thereby, the degree of opening of expansion valve 30 can be changed.
  • P LEV,in , h LEV,in , and ⁇ LEV,in represent the refrigerant pressure, the enthalpy, and the refrigerant density, respectively, at the inlet portion of first expansion valve 30 .
  • Cv main [mm 2 ] represents the Cv value of expansion valve 30
  • Gr s [kg/h] represents the refrigerant circulation amount at the suction port of compressor 10
  • h LEV,in [kJ/kg] represents the enthalpy of the refrigerant at the inlet of expansion valve 30
  • P e,in [MPa] represents the pressure of the refrigerant at the inlet of expansion valve 30 .
  • FIG. 7 is a diagram for illustrating a process of deriving the inlet portion pressure of first expansion valve 30 .
  • controller 100 sets an assumed value P LEV,in1 of the inlet portion pressure of first expansion valve 30 .
  • controller 100 calculates a refrigerant density ⁇ LEV,in at the inlet portion of expansion valve 30 by applying assumed value P LEV,in1 to the following equation (8).
  • controller 100 calculates a refrigerant pressure P LEV,in2 at the inlet portion of expansion valve 30 by the following equation (9).
  • step S 14 controller 100 compares assumed value P LEV,in1 with the calculated refrigerant pressure P LEV,in2 , and determines whether or not these values are equal to each other.
  • P LEV,in1 P LEV,in2 represented in step S 14 means whether or not the convergence condition is satisfied, and the convergence condition includes a condition that the error between the two values to be compared falls within a certain value.
  • the process returns to step S 11 , and the assumed value is reset.
  • the assumed value may be reset by using Newton's Method, a binary method, or the like, each of which is generally used for convergence calculation.
  • the number of sensors can be reduced, and the degree of dryness X LEV,in of the refrigerant can be calculated in a simplified process.
  • FIG. 8 is a diagram showing an arrangement of various sensors when non-azeotropic refrigerant is used.
  • FIG. 8 is the same as FIG. 3 in that refrigeration cycle apparatus 1 includes pressure sensors 110 and 116 except that, in FIG. 8 , temperature sensor 111 and pressure sensor 118 are additionally provided but temperature sensors 112 , 114 , 115 , 117 , and flow rate sensor 113 are not provided.
  • FIG. 9 is a p-h diagram showing a change in the state of refrigerant when non-azeotropic refrigerant is used.
  • an isothermal line TL is not parallel to the horizontal axis in a two-phase region, and thus, condensing steps A to C show a temperature change.
  • a point C shifts in the direction approaching a point A, so that a temperature T LEV,in also rises.
  • the degree of dryness X LEV,in can be calculated from pressure P LEV,in and temperature T LEV,in also in the two-phase region.
  • FIG. 10 is a flowchart for illustrating control of second expansion valve 72 when non-azeotropic refrigerant is used.
  • controller 100 calculates the degree of dryness X LEV,in of the refrigerant at the inlet portion of expansion valve 30 by the following equation (10).
  • controller 100 calculates the target degree of dryness X tgt of the refrigerant at the inlet portion of expansion valve 30 by the following equation (11).
  • controller 100 changes the degree of opening of second expansion valve 72 such that X LEV,in becomes equal to X tgt .
  • controller 100 compares the target degree of dryness X tgt with the calculated current degree of dryness X LEV,in .
  • controller 100 decreases the degree of opening of second expansion valve 72 disposed in injection flow path 70 .
  • controller 100 increases the degree of opening of second expansion valve 72 disposed in injection flow path 70 .
  • the degree of opening of second expansion valve 72 is controlled such that the degree of dryness X LEV,in becomes equal to the target degree of dryness X tgt .
  • the following describes a study of comparison between a refrigeration cycle apparatus designed mainly for heating as a study example and the refrigeration cycle apparatus according to the first embodiment.
  • the refrigeration cycle apparatus according to the present embodiment is suitably used in a heat pump machine mainly for heating, such as a water heater or a circulation-type warmer.
  • a heat pump machine mainly for heating such as a water heater or a circulation-type warmer
  • the amount of refrigerant required during a heating operation is generally enclosed, and the amount of refrigerant becomes insufficient during a cooling operation.
  • an air heat exchanger larger in volume than a load-side heat exchanger serves as a condenser (high pressure), and thus, the amount of refrigerant required to fill the outlet of the condenser with liquid refrigerant increases.
  • the refrigerant at the inlet of the expansion valve becomes two-phase refrigerant and the refrigerant density decreases, which consequently decreases the pressure on the low pressure side due to insufficient degree of opening of the expansion valve.
  • the low pressure decreases, freezing occurs in the load-side heat exchanger, and when the load-side heat exchanger is damaged, there is a possibility that refrigerant may leak due to rupture.
  • the refrigerant and the heat medium are arranged to flow as counterflows to each other in the heat exchanger during a heating operation for the purpose of ensuring the performance during the heating operation.
  • the flow direction of the refrigerant in the heat exchanger is reversed and a parallel flow occurs, so that the performance decreases.
  • each refrigerant flowing into a respective one of three heat exchangers can be caused to flow in the same direction as a counterflow, and therefore, the performance is expected to be improved as compared with the conventional refrigeration cycle apparatus in which a parallel flow mixedly exists.
  • the internal heat exchange using third heat exchanger 80 and second expansion valve 72 disposed in injection flow path 70 can be used for the refrigerant at the outlet portion of the condenser, and therefore, the performance of the refrigeration cycle apparatus is expected to be improved by injection of the refrigerant.
  • suppressing a pressure decrease in the low pressure portion can avoid freezing in the load-side heat exchanger.
  • FIG. 11 is a diagram showing a refrigerant circuit and a flow of refrigerant during a cooling operation of a refrigeration cycle apparatus according to the second embodiment.
  • Flow path switching device 50 in a refrigeration cycle apparatus 201 shown in FIG. 11 includes a six-way valve 51 A and a four-way valve 52 .
  • Six-way valve 51 A includes ports PB 2 and PC 2 in addition to ports PA to PD. Ports PA to PD are connected to the respective pipes of the refrigerant circuit as in FIG. 1 . Ports PB 2 and PC 2 are connected by a pipe outside six-way valve 51 A.
  • six-way valve 51 A can be used for switching the connection similarly to four-way valve 51 shown in FIG. 1 .
  • a six-way valve has become produced, and if a six-way valve can be used in place of a four-way valve, it may be convenient, for example, in terms of inventory adjustment for raw materials.
  • six-way valve 51 A is configured to connect the discharge port of compressor 10 to refrigerant inlet 21 of first heat exchanger 20 and connect the refrigerant outlet of first expansion valve 30 to the refrigerant inlet of second heat exchanger 40 .
  • a flow path is formed inside six-way valve 51 A such that port PA communicates with port PB, port PC communicates with port PD, and port PB 2 communicates with port PC 2 .
  • four-way valve 52 is configured to connect refrigerant outlet 22 of first heat exchanger 20 to the refrigerant inlet of first flow path 81 and connect the refrigerant outlet of second heat exchanger 40 to the suction port of compressor 10 .
  • FIG. 12 is a diagram showing the refrigerant circuit and the flow of the refrigerant during a heating operation of the refrigeration cycle apparatus according to the second embodiment.
  • six-way valve 51 A is configured to connect the discharge port of compressor 10 to the refrigerant inlet of second heat exchanger 40 and connect the refrigerant outlet of first expansion valve 30 to refrigerant inlet 21 of first heat exchanger 20 .
  • a flow path is formed inside six-way valve 51 A such that port PA communicates with port PD, port PB communicates with port PB 2 , and port PC 2 communicates with port PC.
  • port PB communicates with port PC through an external pipe.
  • four-way valve 52 is configured to connect the refrigerant outlet of second heat exchanger 40 to the refrigerant inlet of first flow path 81 and connect refrigerant outlet 22 of first heat exchanger 20 to the suction port of compressor 10 .
  • refrigeration cycle apparatus 201 of the second embodiment configured as described above, the same effect as that in the first embodiment can be achieved.
  • FIG. 13 is a diagram showing a refrigerant circuit and a flow of refrigerant during a cooling operation of a refrigeration cycle apparatus according to the third embodiment.
  • Flow path switching device 50 of a refrigeration cycle apparatus 202 shown in FIG. 13 includes a four-way valve 51 and a six-way valve 52 A.
  • Six-way valve 52 A includes ports PG 2 and PH 2 in addition to ports PE to PH. Ports PE to PH are connected to the respective pipes of the refrigerant circuit as in FIG. 1 . Ports PG 2 and PH 2 are connected by a pipe outside six-way valve 52 A.
  • six-way valve 52 A can be used for switching the connection similarly to four-way valve 52 shown in FIG. 1 .
  • the four-way valve is configured to connect the discharge port of compressor 10 to refrigerant inlet 21 of first heat exchanger 20 and connect the refrigerant outlet of first expansion valve 30 to the refrigerant inlet of second heat exchanger 40 .
  • six-way valve 52 A is configured to connect refrigerant outlet 22 of first heat exchanger 20 to the refrigerant inlet of first flow path 81 and connect the refrigerant outlet of second heat exchanger 40 to the suction port of compressor 10 .
  • a flow path is formed inside six-way valve 52 A such that port PE communicates with port PF, port PG communicates with port PG 2 , and port PH 2 communicates with port PH.
  • ports PG and PH communicate with each other through an external pipe.
  • FIG. 14 is a diagram showing the refrigerant circuit and the flow of the refrigerant during a heating operation of the refrigeration cycle apparatus according to the third embodiment.
  • four-way valve 51 is configured to connect the discharge port of compressor 10 to the refrigerant inlet of second heat exchanger 40 and connect the refrigerant outlet of first expansion valve 30 to refrigerant inlet 21 of first heat exchanger 20 .
  • six-way valve 52 A is configured to connect the refrigerant outlet of second heat exchanger 40 to the refrigerant inlet of first flow path 81 and connect refrigerant outlet 22 of first heat exchanger 20 to the suction port of compressor 10 .
  • a flow path is formed inside six-way valve 52 A such that port PG communicates with port PF, port PE communicates with port PH, and port PG 2 communicates with port PH 2 .
  • refrigeration cycle apparatus 202 of the third embodiment configured as described above, the same effect as that in the first and second embodiments can also be achieved.
  • FIG. 15 is a diagram showing a refrigerant circuit and a flow of refrigerant during a cooling operation of a refrigeration cycle apparatus according to the fourth embodiment.
  • Flow path switching device 50 in a refrigeration cycle apparatus 203 shown in FIG. 15 includes a first six-way valve 51 A and a second six-way valve 52 A. Since first six-way valve 51 A is connected in the same way as that in the second embodiment and second six-way valve 52 A is connected in the same way as that in the third embodiment, the description thereof will not be repeated.
  • first six-way valve 51 A is configured to connect the discharge port of compressor 10 to refrigerant inlet 21 of first heat exchanger 20 and connect the refrigerant outlet of first expansion valve 30 to the refrigerant inlet of second heat exchanger 40 .
  • second six-way valve 52 A is configured to connect refrigerant outlet 22 of first heat exchanger 20 to the refrigerant inlet of first flow path 81 and connect the refrigerant outlet of second heat exchanger 40 to the suction port of compressor 10 .
  • FIG. 16 is a diagram showing the refrigerant circuit and the flow of the refrigerant during a heating operation of the refrigeration cycle apparatus according to the fourth embodiment.
  • first six-way valve 51 A is configured to connect the discharge port of compressor 10 to the refrigerant inlet of second heat exchanger 40 and connect the refrigerant outlet of first expansion valve 30 to refrigerant inlet 21 of first heat exchanger 20 .
  • second six-way valve 52 A is configured to connect the refrigerant outlet of second heat exchanger 40 to the refrigerant inlet of first flow path 81 and connect refrigerant outlet 22 of first heat exchanger 20 to the suction port of compressor 10 .
  • Flow path switching device 50 in a refrigeration cycle apparatus 204 includes an eight-way valve 50 B.
  • FIG. 17 is a diagram showing a refrigerant circuit and a flow of refrigerant during a cooling operation of a refrigeration cycle apparatus according to the fifth embodiment.
  • FIG. 18 is a diagram showing the state of eight-way valve 50 B and the flow of the refrigerant in eight-way valve 50 B during the cooling operation according to the fifth embodiment.
  • eight-way valve 50 B includes a cylindrical valve main body 308 .
  • Ports PA and PE are formed on one side in the circumferential direction of valve main body 308 while ports PB, PC, PD, PF, PG, and PH are formed on the other side thereof.
  • a piston 312 formed by connecting three pressure receiving slide members 310 A, 310 B, and 310 C to a connecting rod 311 is provided inside valve main body 308 of eight-way valve 50 B. Slide valve bodies 313 A and 313 B are fixed to connecting rod 311 .
  • slide valve body 313 A slides on a valve seat provided with ports PB, PC, and PD
  • slide valve body 313 B slides on a valve seat provided with ports PF, PG, and PH.
  • Piston 312 provides partitions between a first chamber R 1 , a second chamber R 2 , a third chamber R 3 , and a fourth chamber R 4 .
  • Eight-way valve 50 B further includes a pilot solenoid valve 514 for switching the slide valve body.
  • Pilot solenoid valve 514 includes a valve body 516 coupled to a plunger 515 , a solenoid coil 517 , and a coil spring 518 .
  • valve body 516 When the refrigeration cycle apparatus is started while solenoid coil 517 of pilot solenoid valve 514 is energized, plunger 515 is suctioned so that valve body 516 is moved to thereby: cause a low-pressure communication pipe 519 reaching a suction pipe of compressor 10 to communicate with a conduit 522 for fourth chamber R 4 ; and cause a high-pressure introduction pipe 521 to communicate with a conduit 520 for first chamber R 1 .
  • compressor 10 is started in this state, high pressure is introduced into first chamber R 1 , and piston 312 and slide valve bodies 313 A and 313 B are moved toward fourth chamber R 4 and fixed as shown in FIG. 18 .
  • Slide valve body 313 B is provided with two communication inner cavities through which two ports adjacent in phase between ports PF, PG, and PH communicate with each other.
  • the communication inner cavities allow communication between ports PG and PH, and port PE communicates with port PF through third chamber R 3 .
  • Valve body 516 biased by coil spring 518 when solenoid coil 517 is not energized causes low-pressure communication pipe 519 to communicate with conduit 520 for first chamber R 1 and causes high-pressure introduction pipe 521 to communicate with conduit 522 for fourth chamber R 4 .
  • high pressure is introduced into fourth chamber R 4 , so that piston 312 and slide valve bodies 313 A and 313 B move toward first chamber R 1 .
  • eight-way valve 50 B is arranged at the heating operation position in which refrigerant circulates through the path indicated by a solid line in FIG. 19 .
  • the same effect as that in the first to fourth embodiments can be achieved, and the number of components and the number of ports used in a substrate can be reduced.
  • a refrigeration cycle apparatus 1 shown in FIG. 1 includes a compressor 10 , a first heat exchanger 20 , a second heat exchanger 40 , a third heat exchanger 80 , a first expansion valve 30 , a second expansion valve 72 , and a flow path switching device 50 .
  • Compressor 10 , first heat exchanger 20 , second heat exchanger 40 , and first expansion valve 30 constitute a refrigerant circuit 90 through which refrigerant circulates.
  • Second expansion valve 72 forms a portion of injection flow path 70 , injection flow path 70 being configured to reduce pressure of the refrigerant before passing through first expansion valve 30 in refrigerant circuit 90 and return the refrigerant to compressor 10 .
  • Third heat exchanger 80 includes a first flow path 81 through which the refrigerant flows, and a second flow path 82 through which the refrigerant flows. Third heat exchanger 80 is configured to exchange heat between the refrigerant passing through first flow path 81 and the refrigerant passing through second flow path 82 .
  • First flow path 81 is disposed in refrigerant circuit 90 to cause the refrigerant to flow toward first expansion valve 30 .
  • Second flow path 82 is disposed to return, to compressor 10 , the refrigerant that has passed through second expansion valve 72 .
  • flow path switching device 50 is configured to connect the discharge port of compressor 10 to the refrigerant inlet of second heat exchanger 40 , connect the refrigerant outlet of second heat exchanger 40 to the refrigerant inlet of first flow path 81 , connect the refrigerant outlet of first expansion valve 30 to the refrigerant inlet of first heat exchanger 20 , and connect the refrigerant outlet of first heat exchanger 20 to the suction port of compressor 10 .
  • the refrigerant flows in the same direction in each of first heat exchanger 20 , second heat exchanger 40 , third heat exchanger 80 , first expansion valve 30 , and second expansion valve 72 .
  • first heat exchanger 20 , second heat exchanger 40 , and third heat exchanger 80 are configured to perform heat exchange in a relation in which a heat medium that exchanges heat flows as a counterflow in any of the first operation mode and the second operation mode.
  • the heat medium that exchanges heat with the refrigerant is air in first heat exchanger 20 , water or brine in second heat exchanger 40 , and refrigerant in third heat exchanger 80 .
  • flow path switching device 50 includes a first four-way valve 51 and a second four-way valve 52 .
  • first four-way valve 51 is configured to connect the discharge port of compressor 10 to the refrigerant inlet of first heat exchanger 20 and connect the refrigerant outlet of first expansion valve 30 to the refrigerant inlet of second heat exchanger 40
  • first four-way valve 51 is configured to connect the discharge port of compressor 10 to the refrigerant inlet of second heat exchanger 40 and connect the refrigerant outlet of first expansion valve 30 to the refrigerant inlet of first heat exchanger 20 .
  • second four-way valve 52 is configured to connect the refrigerant outlet of first heat exchanger 20 to the refrigerant inlet of first flow path 81 and connect the refrigerant outlet of second heat exchanger 40 to the suction port of compressor 10
  • second four-way valve 52 is configured to connect the refrigerant outlet of second heat exchanger 40 to the refrigerant inlet of first flow path 81 and connect the refrigerant outlet of first heat exchanger 20 to the suction port of compressor 10 .
  • flow path switching device 50 includes a six-way valve 51 A and a four-way valve 52 .
  • six-way valve 51 A is configured to connect the discharge port of compressor 10 to the refrigerant inlet of first heat exchanger 20 and connect the refrigerant outlet of first expansion valve 30 to the refrigerant inlet of second heat exchanger 40
  • six-way valve 51 A is configured to connect the discharge port of compressor 10 to the refrigerant inlet of second heat exchanger 40 and connect the refrigerant outlet of first expansion valve 30 to the refrigerant inlet of first heat exchanger 20 .
  • four-way valve 52 is configured to connect the refrigerant outlet of first heat exchanger 20 to the refrigerant inlet of first flow path 81 and connect the refrigerant outlet of second heat exchanger 40 to the suction port of compressor 10
  • four-way valve 52 is configured to connect the refrigerant outlet of second heat exchanger 40 to the refrigerant inlet of first flow path 81 and connect the refrigerant outlet of first heat exchanger 20 to the suction port of compressor 10 .
  • six-way valve 52 A is configured to connect the refrigerant outlet of first heat exchanger 20 to the refrigerant inlet of first flow path 81 and connect the refrigerant outlet of second heat exchanger 40 to the suction port of compressor 10
  • six-way valve 52 A is configured to connect the refrigerant outlet of second heat exchanger 40 to the refrigerant inlet of first flow path 81 and connect the refrigerant outlet of first heat exchanger 20 to the suction port of compressor 10 .
  • second six-way valve 52 A is configured to connect the refrigerant outlet of first heat exchanger 20 to the refrigerant inlet of first flow path 81 and connect the refrigerant outlet of second heat exchanger 40 to the suction port of compressor 10
  • second six-way valve 52 A is configured to connect the refrigerant outlet of second heat exchanger 40 to the refrigerant inlet of first flow path 81 and connect the refrigerant outlet of first heat exchanger 20 to the suction port of compressor 10 .
  • flow path switching device 50 includes an eight-way valve 50 B.
  • the refrigeration cycle apparatus further includes a controller 100 configured to control first expansion valve 30 and second expansion valve 72 .
  • Controller 100 is configured to control a degree of opening of second expansion valve 72 such that a degree of dryness of refrigerant flowing into first expansion valve 30 from first flow path 81 of third heat exchanger 80 does not increase above a target degree of dryness.

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  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
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