CN114364929B - Outdoor unit and refrigeration cycle device - Google Patents

Outdoor unit and refrigeration cycle device Download PDF

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Publication number
CN114364929B
CN114364929B CN201980099963.2A CN201980099963A CN114364929B CN 114364929 B CN114364929 B CN 114364929B CN 201980099963 A CN201980099963 A CN 201980099963A CN 114364929 B CN114364929 B CN 114364929B
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China
Prior art keywords
flow path
refrigerant
pressure
outdoor unit
compressor
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CN201980099963.2A
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Chinese (zh)
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CN114364929A (en
Inventor
石川智隆
有井悠介
早坂素
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2515—Flow 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2519—On-off valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

The outdoor unit (2) is provided with a 1 st flow path (F1), a 2 nd flow path (F2), a 3 rd flow path (F3), and an on-off valve (78). The 1 st flow path (F1) is a flow path from the refrigerant inlet port (PI 2) to the refrigerant outlet port (PO 2), and forms a circulation flow path for circulating the refrigerant together with the load device (3). The compressor (10), the condenser (20), and the 2 nd expansion device (40) are disposed in the 1 st flow path (F1). The 2 nd flow path (F2) is configured to branch from the 1 st flow path (F1) and return the refrigerant passing through the condenser (20) to the compressor (10). The 3 rd expansion device (71) and the liquid receiver (73) are disposed in the 2 nd flow path (F2) in this order from the branching point of the 2 nd flow path (F2) from the 1 st flow path (F1). The 3 rd flow path (F3) connects a portion between the 2 nd expansion device (40) and the refrigerant outlet port (PO 2) in the 1 st flow path (F1) and the refrigerant inlet of the receiver (73). The on-off valve (78) is disposed in the 3 rd flow path (F3).

Description

Outdoor unit and refrigeration cycle device
Technical Field
The present invention relates to an outdoor unit and a refrigeration cycle apparatus.
Background
Japanese patent application laid-open No. 2014-01917 (patent document 1) discloses a refrigerating apparatus having an intermediate injection flow path and a suction injection flow path. In the refrigeration apparatus, a part of the refrigerant flowing from the condenser to the evaporator can be merged into the medium-pressure refrigerant (intermediate pressure) of the compressor by using the intermediate injection flow path, or into the low-pressure refrigerant sucked into the compressor by using the suction injection flow path. Therefore, when the operation efficiency is deteriorated during the use of the intermediate injection flow path, the discharge temperature of the compressor can be lowered by using the suction injection flow path.
Prior art literature
Patent document 1: japanese patent application laid-open No. 2014-01917
Disclosure of Invention
In the refrigeration apparatus described in japanese patent application laid-open No. 2014-01917 (patent document 1), when the flow of refrigerant on the indoor unit side is cut off and the evacuation (pump down) operation is started on the load device side due to the load device being stopped or the like, the pressure of the liquid pipe of the outdoor unit increases. For example, when a supercritical CO2 refrigerant or the like is used, the discharge pressure of the compressor is high, and therefore, there is a possibility that the pressure of a part of the liquid pipe exceeds the design pressure.
The present invention aims to provide an outdoor unit and a refrigeration cycle device which are improved in a manner that pressure exceeding a design pressure is prevented from being applied to a pipe.
The present disclosure relates to an outdoor unit of a refrigeration cycle apparatus configured to be connected to a load apparatus including a 1 st expansion device and an evaporator. The outdoor unit is provided with: a refrigerant outlet port and a refrigerant inlet port for connection to a load device; the 1 st flow path is a flow path from the refrigerant inlet port to the refrigerant outlet port, and forms a circulation flow path for circulating the refrigerant together with the load device; a compressor, a condenser, and a 2 nd expansion device disposed in the 1 st flow path; a 2 nd flow path configured to branch from a portion between the condenser of the 1 st flow path and the 2 nd expansion device and return the refrigerant passing through the condenser to the compressor; a 3 rd expansion device and a liquid receiver, which are disposed in the 2 nd flow path in this order from a branching point of the 2 nd flow path from the 1 st flow path; a 3 rd flow path connecting the portion between the 2 nd expansion device and the refrigerant outlet port in the 1 st flow path and the refrigerant inlet of the receiver; and an on-off valve disposed in the 3 rd flow path.
According to the outdoor unit and the refrigeration cycle apparatus including the same of the present disclosure, even when the pressure increases sharply due to, for example, the flow of the refrigerant on the load device side being shut off, the pressure of the piping can be prevented from exceeding the design pressure.
Drawings
Fig. 1 is an overall configuration diagram of a refrigeration cycle apparatus according to the present embodiment.
Fig. 2 is a flowchart for explaining the control of the 3 rd expansion valve 71.
Fig. 3 is a flowchart for explaining the control of the flow rate adjustment valve 72.
Fig. 4 is a flowchart for explaining the control of the 2 nd expansion valve 40.
Fig. 5 is a flowchart for explaining the control of the opening/closing valve 78.
(symbol description)
1: a refrigeration cycle device; 2: an outdoor unit; 3: a load device; 10: a compressor; 20: a condenser; 22: a fan; 28. 75, 76, 78: an opening/closing valve; 30: a heat exchanger; 40: a 2 nd expansion valve; 50: a 1 st expansion valve; 60: an evaporator; 70: a throttle device; 71: a 3 rd expansion valve; 72: a flow rate adjusting valve; 73: a liquid receiver; 74: a flow path switching unit; 77: a pressure reducing device; 80-85, 88, 89, 91, 92, 94, 96-98: piping; 93: an exhaust pipe; 100: a control device; 104: a memory; 110 to 113: a pressure sensor; 120-122: a temperature sensor; f1: a 1 st flow path; f2: a 2 nd flow path; f3: a 3 rd flow path; g1: a suction port; and G2: a discharge port; and G3: a medium pressure port (intermediate pressure port); h1: a 1 st path; h2: a 2 nd passage; PI2, PI3: a refrigerant inlet port; PO2, PO3: a refrigerant outlet port.
Detailed Description
Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. The following description will be given of a plurality of embodiments, but it is expected from the beginning of the application that the configurations described in the embodiments can be appropriately combined. In the drawings, the same or corresponding portions are denoted by the same reference numerals, and description thereof will not be repeated.
Fig. 1 is an overall configuration diagram of a refrigeration cycle apparatus according to the present embodiment. In fig. 1, the connection relationship and arrangement structure of the respective devices in the refrigeration cycle apparatus are functionally shown, and the arrangement in the physical space is not necessarily shown.
Referring to fig. 1, the refrigeration cycle apparatus 1 includes an outdoor unit 2, a load device 3, and pipes 84 and 88. The outdoor unit 2 has a refrigerant outlet port PO2 for connection with the load device 3 and a refrigerant inlet port PI2. The load device 3 has a refrigerant outlet port PO3 for connection with the outdoor unit 2 and a refrigerant inlet port PI3. The piping 84 connects the refrigerant outlet port PO2 of the outdoor unit 2 and the refrigerant inlet port PI3 of the load device 3. The pipe 88 connects the refrigerant outlet port PO3 of the load device 3 and the refrigerant inlet port PI2 of the outdoor unit 2.
The outdoor unit 2 of the refrigeration cycle apparatus 1 is connected to the load device 3. The outdoor unit 2 includes: a compressor 10 having a suction port G1, a discharge port G2, and a medium pressure port G3, a condenser 20, a fan 22, a heat exchanger 30, a 2 nd expansion valve 40, and pipes 80 to 83 and 89. The heat exchanger 30 is configured to have a 1 st passage H1 and a 2 nd passage H2, and to exchange heat between the refrigerant flowing through the 1 st passage H1 and the refrigerant flowing through the 2 nd passage H2.
The load device 3 includes the 1 st expansion valve 50, the evaporator 60, the pipes 85, 86, 87, and the on-off valve 28. The evaporator 60 is configured to exchange heat between air and refrigerant. In the refrigeration cycle apparatus 1, the evaporator 60 evaporates the refrigerant by absorbing heat from the air in the cooling target space. The 1 st expansion valve 50 is, for example, a temperature expansion valve controlled independently of the outdoor unit 2. The 1 st expansion valve 50 may be an electronic expansion valve capable of decompressing the refrigerant. The opening/closing valve 28 is closed (closed) when the load device 3 stops operating, and cuts off the refrigerant.
The compressor 10 compresses the refrigerant sucked from the pipe 89 and discharges the refrigerant to the pipe 80. The compressor 10 can arbitrarily change the driving frequency by inverter control. The compressor 10 is provided with a medium pressure port G3, and the refrigerant from the medium pressure port G3 can flow into the intermediate portion of the compression process. The compressor 10 is configured to adjust the rotation speed in accordance with a control signal from the control device 100. The capacity of the refrigeration cycle apparatus 1 can be adjusted by adjusting the circulation amount of the refrigerant by adjusting the rotation speed of the compressor 10. Various types of compressors can be employed in the compressor 10, for example, a scroll type, a rotation type, a screw type, or the like can be employed.
The condenser 20 is configured to exchange heat (dissipate heat) between the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 and the outside air. By this heat exchange, the refrigerant is condensed and changes to a liquid phase. The refrigerant discharged from the compressor 10 to the pipe 80 is condensed and liquefied in the condenser 20, and flows out to the pipe 81. In order to improve the efficiency of heat exchange, a fan 22 for supplying outside air is installed in the condenser 20. The fan 22 supplies the external air, which exchanges heat with the refrigerant in the condenser 20, to the condenser 20. By adjusting the rotation speed of the fan 22, the refrigerant pressure on the discharge side (high-pressure side pressure) of the compressor 10 can be adjusted. The 2 nd expansion valve 40 is an electronic expansion valve capable of decompressing the refrigerant passing through the 1 st path H1 of the condenser 20 and the heat exchanger 30.
Here, the refrigerant used in the refrigerant circuit of the refrigeration cycle apparatus 1 is CO 2 However, in the case where a state where it is difficult to secure the supercooling degree occurs, other refrigerants may be used.
In the present specification, for ease of explanation, CO in a supercritical state is described as follows 2 Such a case where the refrigerant is cooled is also referred to as a condenser 20. In this specification, for ease of explanation, the amount of decrease from the reference temperature of the supercritical refrigerant is also referred to as the supercooling degree.
The 1 st flow path F1 from the refrigerant inlet port PI2 to the refrigerant outlet port PO2 through the 1 st flow path H1 and the 2 nd expansion valve 40 of the compressor 10, the condenser 20, and the heat exchanger 30 forms a circulation flow path for circulating the refrigerant together with the flow path of the load device 3 in which the 1 st expansion valve 50 and the evaporator 60 are disposed. Hereinafter, this circulation flow path is also referred to as a "main refrigerant circuit" of the refrigeration cycle.
The outdoor unit 2 further includes: tubing 91, 92, 94 for flowing the refrigerant from the portion between the outlet of the 1 st passage H1 and the 2 nd expansion valve 40 of the circulation passage to the inlet of the 2 nd passage H2; tubing 96 to 98 for flowing the refrigerant from the outlet of the 2 nd passage H2 to the suction port G1 or the intermediate pressure port G3 of the compressor 10; and a flow path switching unit 74 that can select either one of the suction port G1 and the intermediate pressure port G3 as a destination of the refrigerant flowing out from the outlet of the 2 nd flow path H2. Hereinafter, the 2 nd flow path F2, which branches from the main refrigerant circuit and feeds the refrigerant to the compressor 10 through the 2 nd flow path H2, is also referred to as an "injection flow path".
The outdoor unit 2 further includes a receiver (receiver) 73 disposed in the 2 nd flow path F2 and storing a refrigerant. The 3 rd expansion valve 71 is disposed between a pipe 91 branching from a portion between the outlet of the 1 st passage H1 of the circulation passage and the 2 nd expansion valve 40 and a pipe 92 connected to the inlet of the liquid receiver 73. The outdoor unit 2 further includes: an exhaust pipe 93 connecting the gas discharge port of the liquid receiver 73 and the 2 nd passage H2, and discharging the refrigerant gas in the liquid receiver 73; a throttle device 70 disposed between an exhaust pipe 93 and a pipe 94 leading to a 2 nd passage H2; and a flow rate adjustment valve 72 for adjusting the flow rate of the refrigerant in the pipe 94 connected to the liquid refrigerant discharge port of the receiver 73.
The pipe 91 branches from the main refrigerant circuit and flows the refrigerant into the receiver 73. The 3 rd expansion valve 71 is an electronic expansion valve capable of reducing the refrigerant in the high-pressure portion of the main refrigerant circuit to an intermediate pressure. The liquid receiver 73 is a container as follows: the gas phase and the liquid phase of the refrigerant which is depressurized and becomes two phases can be separated in the container, the refrigerant can be stored, and the circulation amount of the refrigerant in the main refrigerant circuit can be adjusted. The exhaust pipe 93 connected to the upper portion of the liquid receiver 73 and the pipe 94 connected to the lower portion of the liquid receiver 73 are pipes for taking out the refrigerant separated into the gas refrigerant and the liquid refrigerant in the liquid receiver 73 in a separated state. The flow rate adjustment valve 72 can adjust the amount of refrigerant in the receiver 73 by adjusting the circulation amount of the liquid refrigerant discharged from the pipe 94.
By providing the liquid receiver 73 in the injection flow path in this way, the degree of supercooling in the pipes 82 and 83 as liquid pipes can be easily ensured. This is because, in general, the liquid receiver 73 contains a gas refrigerant, and therefore, the refrigerant temperature becomes a saturation temperature, and if the liquid receiver 73 is disposed in the pipe 82, the supercooling degree cannot be ensured.
In addition, if the accumulator 73 is provided in the medium-pressure portion, even when the pressure of the high-pressure portion of the main refrigerant circuit is high and the refrigerant is in a supercritical state, the medium-pressure liquid refrigerant can be stored in the accumulator 73. Therefore, the design pressure of the container of the liquid receiver 73 can be made lower than that of the high-pressure portion, and the cost can be reduced by thinning the wall of the container.
The outdoor unit 2 further includes pressure sensors 110 to 112, temperature sensors 120 to 122, and a control device 100 for controlling the compressor 10, the 2 nd expansion valve 40, the 3 rd expansion valve 71, the flow rate adjustment valve 72, and the flow path switching unit 74.
The pressure sensor 110 detects the pressure PL of the suction port portion of the compressor 10, and outputs the detected value thereof to the control device 100. The pressure sensor 111 detects the discharge pressure PH of the compressor 10, and outputs the detected value to the control device 100. The pressure sensor 112 detects the pressure P1 of the pipe 83 at the outlet of the 2 nd expansion valve 40, and outputs the detected value to the control device 100.
The outdoor unit 2 can reduce the refrigerant pressure to a design pressure of the load device 3 (for example, 4 MPa) or less by providing the liquid pipe with the 2 nd expansion valve 40, and then send the refrigerant to the load device 3. Thus, even if CO is used 2 For example, a supercritical refrigerant may be used, and a general-purpose product having the same design pressure as that of the conventional one may be used as the load device 3.
The temperature sensor 120 detects the discharge temperature TH of the compressor 10, and outputs the detected value to the control device 100. The temperature sensor 121 detects the refrigerant temperature T1 of the pipe 81 at the outlet of the condenser 20, and outputs the detected value to the control device 100. The temperature sensor 122 detects the refrigerant temperature T2 at the outlet of the 1 st passage H1 on the cooled side of the heat exchanger 30, and outputs the detected value to the control device 100.
The flow path switching unit 74 includes: pipes 97 and 98 obtained by branching the pipe 96, the pressure reducing device 77 disposed between the pipes 97 and 98, and the opening/closing valves 75 and 76 disposed in the pipes 97 and 98, respectively.
The pipe 97 is connected between the pipe 96 and the medium pressure port G3, and the on-off valve 75 is provided in the pipe 97. The pressure reducing device 77 and the opening/closing valve 76 are disposed in series between the outlet of the 2 nd passage H2 and the suction port G1.
By the opening/closing valve 75 and the opening/closing valve 76, it is possible to switch whether the destination of the refrigerant in the 2 nd flow path F2 is the intermediate pressure port G3 or the suction port G1 of the compressor 10.
In the present embodiment, the 2 nd flow path F2 controls the discharge temperature TH of the compressor 10 by allowing the refrigerant, which has been depressurized into two phases, to flow into the compressor 10. The amount of refrigerant in the main refrigerant circuit can be adjusted by the receiver 73 provided in the 2 nd flow path F2. The 2 nd flow path F2 also ensures supercooling of the refrigerant in the main refrigerant circuit by heat exchange by the heat exchanger 30. The control device 100 switches the destination of the refrigerant by the on-off valve 75 and the on-off valve 76 so that each purpose can be performed under each operation condition.
The outdoor unit 2 further includes: a 3 rd flow path F3 connecting the piping 83 and the piping 92; and an opening/closing valve 78 provided in the 3 rd flow path F3. The opening/closing valve 78 is provided to avoid a sudden increase in the pressure P1 of the pipe 83 at the start of the evacuation operation described later.
The control device 100 includes a CPU (Central Processing Unit ) 102, a Memory 104 (ROM (Read Only Memory) and RAM (Random Access Memory), an input/output buffer (not shown) for inputting and outputting various signals, and the like. The CPU102 expands and executes programs stored in the ROM in the RAM or the like. The program stored in the ROM is a program describing the processing procedure of the control device 100. The control device 100 executes control of each device in the outdoor unit 2 in accordance with these programs. The control is not limited to a process performed by software, and may be performed by dedicated hardware (electronic circuit).
(control during normal operation of the refrigeration cycle apparatus)
The control device 100 feedback-controls the 3 rd expansion valve 71 so that the discharge temperature TH of the compressor 10 matches the target temperature.
Fig. 2 is a flowchart for explaining the control of the 3 rd expansion valve 71. When the discharge temperature TH of the compressor 10 is higher than the target temperature (yes in S21), the control device 100 increases the opening degree of the 3 rd expansion valve 71 (S22). Accordingly, the refrigerant flowing into the medium pressure port G3 or the suction port G1 through the liquid receiver 73 increases, and therefore the discharge temperature TH decreases.
On the other hand, when the discharge temperature TH of the compressor 10 is lower than the target temperature (no in S21 and yes in S23), the control device 100 decreases the opening degree of the 3 rd expansion valve 71 (S24). As a result, the refrigerant flowing into the medium pressure port G3 or the suction port G1 via the receiver 73 decreases, and the discharge temperature TH increases.
If discharge temperature th=target temperature (no in S21 and no in S23), control device 100 maintains the opening degree of 3 rd expansion valve 71 in the current state.
In this way, the control device 100 controls the opening degree of the 3 rd expansion valve 71 so that the discharge temperature TH of the compressor 10 approaches the target temperature.
In addition, the control device 100 performs feedback control of the flow rate adjustment valve 72 so that the temperature T1 of the refrigerant at the outlet of the condenser 20 matches the target temperature in order to ensure the supercooling degree SC of the refrigerant at the outlet of the condenser 20.
Fig. 3 is a flowchart for explaining the control of the flow rate adjustment valve 72. When the supercooling degree SC determined from the refrigerant temperature T1 at the outlet of the condenser 20 and the pressure (approximated by PH) of the condenser 20 is greater than the target value (yes in S31), the control device 100 decreases the opening degree of the flow rate adjustment valve 72 (S32). As a result, the amount of liquid refrigerant discharged from the liquid receiver 73 decreases, and the amount of liquid refrigerant in the liquid receiver 73 increases, so that the amount of refrigerant circulating in the main refrigerant circuit decreases, and the refrigerant temperature T1 increases, and the degree of supercooling SC decreases.
On the other hand, when the supercooling degree SC determined from the refrigerant temperature T1 at the outlet of the condenser 20 and the pressure of the condenser 20 (approximated by PH) is smaller than the target value (no in S31 and yes in S33), the control device 100 increases the opening degree of the flow rate adjustment valve 72 (S34). As a result, the amount of liquid refrigerant discharged from the receiver 73 increases, the amount of liquid refrigerant stored in the receiver 73 decreases, the amount of refrigerant circulating in the main refrigerant circuit increases, the refrigerant temperature T1 decreases, and the degree of supercooling SC increases.
If the supercooling degree sc=target value (no in S31 and no in S33), the control device 100 maintains the opening degree of the flow rate adjustment valve 72 in the current state.
In this way, the control device 100 controls the opening degree of the flow rate adjustment valve 72 so that the refrigerant temperature T1 at the outlet of the condenser 20 approaches the target temperature.
In addition, the control device 100 uses CO 2 In the case of the refrigerant, the control of the compressor 10 and the 2 nd expansion valve 40 is performed so as to use the supercritical region of the refrigerant. For example, when the outside air temperature is higher than the supercritical temperature of the refrigerant in summer or the like, the control device 100 increases the rotation speed of the compressor 10 to be higher than that in spring or autumn, and increases the pressure of the high-pressure portion of the main refrigerant circuit. The load device 3 can be shared with a device used under a normal refrigerant by performing decompression with the 2 nd expansion valve 40. At this time, the 2 nd expansion valve 40 is controlled as follows.
The control device 100 performs feedback control of the 2 nd expansion valve 40 so that the pressure P1 matches the target pressure. The target pressure is set to the same level as the pressure in the case where a normal refrigerant such as R410 is used.
Fig. 4 is a flowchart for explaining the control of the 2 nd expansion valve 40. When the pressure P1 is higher than the target pressure (yes in S41), the control device 100 decreases the opening degree of the 2 nd expansion valve 40 (S42). Accordingly, the pressure P1 decreases because the pressure reduction amount by the 2 nd expansion valve 40 increases.
On the other hand, when the pressure P1 is lower than the target pressure (no in S41 and yes in S43), the control device 100 increases the opening degree of the 2 nd expansion valve 40 (S44). Accordingly, the pressure P1 increases because the pressure reduction amount by the 2 nd expansion valve 40 decreases.
If the pressure p1=the target pressure (no in S41 and no in S43), the control device 100 maintains the opening degree of the 2 nd expansion valve 40 in the current state.
Since the pressure P1 is controlled in this way, the pressure in the load device 3 can be set to be equal to or lower than the design pressure of the device used under the normal refrigerant, and the load device can be shared with the load device of the conventional equipment using the refrigerant such as R410A.
(control of switching of injection flow paths)
When the temperature sensor 120 detects an excessive increase in the discharge temperature TH of the compressor 10, the control device 100 opens the on-off valve 75 and closes the on-off valve 76, thereby increasing the injection amount into the compressor 10 and preventing the discharge temperature from further increasing.
At this time, if the medium pressure PM increases with an increase in the evaporation temperature or the like in a state where the on-off valve 75 is opened, the saturation temperature of the refrigerant increases, so the temperature of the refrigerant passing through the 2 nd passage H2 of the heat exchanger 30 also increases, and cooling in the heat exchanger 30 becomes insufficient, so that the supercooling degree of the refrigerant in the 2 nd expansion valve 40 may not be ensured.
Therefore, the control device 100 monitors the refrigerant temperature T2 with the on-off valve 75 opened, and closes the on-off valve 75 and opens the on-off valve 76 when it is detected that the degree of supercooling of the refrigerant cannot be ensured. This allows the low-pressure side refrigerant and the refrigerant in the 2 nd flow path F2 to merge together, thereby reducing the medium-pressure PM and securing a temperature difference in the heat exchanger 30.
Since each device such as the receiver 73 disposed in the 2 nd flow path F2 is depressurized by the 3 rd expansion valve 71 for the main refrigerant circuit, the design pressure can be reduced, and thus the manufacturing cost can be reduced. Even when the design pressure is reduced, when the pressure sensor 113 detects an increase in the medium pressure PM during operation due to overfilling of the refrigerant, an increase in the outside air temperature, or the like, a safety measure can be taken to release the pressure to the low pressure side by opening the on-off valve 76.
(control during evacuation operation)
Next, control during the evacuation operation will be described. The evacuation operation is to provide an on-off valve 28 or the like to the pipe 85 through which the liquid refrigerant flows in the main refrigerant circuit, and to operate the compressor 10 while cutting off the pipe 85, thereby moving the refrigerant from the load device 3 to the outdoor unit 2 and storing the refrigerant. The evacuation operation is performed, for example, by closing the 2 nd expansion valve 40 before the stop operation or by closing the on-off valve 28 and then operating the compressor 10.
In general, a signal indicating the start of the evacuation operation is not particularly transmitted from the load device 3 side to the outdoor unit 2, and the evacuation operation is performed by continuing the normal operation in the outdoor unit 2.
The following structure is adopted in the evacuation operation: if the on-off valve 28 is closed and the pressure PL of the low pressure portion detected by the pressure sensor 110 decreases to the set value, the control device 100 stops the compressor 10 to stop the evacuation. The compressor 10 is configured not to pass the refrigerant in the stopped state, so that the refrigerant does not flow back to the load device 3.
However, if the 1 st expansion valve 50 is closed or the opening/closing valve 28 is closed in the normal operation, the pressure P1 of the pipes 83, 84, 85 increases rapidly. When the pressure P1 exceeds the design pressure of the piping 83, 84, 85 and the load device 3, there is a possibility that problems such as leakage of the refrigerant may occur, and the pressure P1 needs to be controlled so as not to exceed the design pressure range.
Accordingly, the control device 100 temporarily opens the opening/closing valve 78 to prevent the abrupt increase in the pressure P1.
Hereinafter, the control of the opening/closing valve 78 performed at the time of evacuation will be described. Fig. 5 is a flowchart for explaining the control of the opening/closing valve 78.
In step S51, the control device 100 determines whether or not the pressure P1 exceeds the design pressure. The design pressure here is a pressure that can be received if it is a short time, and may be set to be slightly lower than the actual design pressure.
In step S51, when the pressure P1 does not exceed the design pressure (no in S51), the control device 100 closes the on-off valve 78 in step S56 and advances the process to step S57, since the pressure P1 does not need to be reduced.
On the other hand, when it is detected in step S51 that the pressure P1 exceeds the design pressure (yes in S51), the control device 100 executes the processing in steps S52 to S55, and prevents the pressure P1 from rising sharply.
In step S52, the control device 100 determines whether or not the pressure P1 of the pipe 83 is higher than the pressure P2 of the pipe 92 of the injection flow path.
If P1> P2 (no in S52), the pressure P1 of the piping 83 does not decrease even if the on-off valve 78 is opened, so in step S53, the control device 100 opens the on-off valve 76 and closes the on-off valve 75 to decrease the pressure of the 2 nd flow path F2. Then, the process advances to step S54.
If P1> P2 (yes in S52), the pressure P1 of the piping 83 can be reduced when the on-off valve 78 is opened, so the process proceeds to step S54 without executing the process of step S53.
In addition, the pipe 96 and the intermediate pressure port G3 may be directly connected without the flow path switching unit 74, but in this case, the processing of steps S52 and S53 is not executed, and if yes is determined in step S51, the processing is quickly advanced to step S54.
In step S54, the control device 100 opens the on-off valve 78 and closes the flow rate adjustment valve 72, thereby introducing the medium pressure in the 2 nd flow path F2 to the pipe 83 and reducing the pressure P1. This can prevent the pressure P1 from exceeding the design pressure of the pipes 83 and 84 and the load device 3.
Although it is not necessarily required, it is preferable that the control device 100 further reduces the rotation speed of the compressor 10 in step S55 to suppress further increase of the pressure P1 of the piping 83. When the pressure P1 temporarily and rapidly increases, the process of step S55 may be performed, and then the process of step S56 may be performed after that when the pressure P1 decreases, in order to shorten the time of the evacuation operation, the process of returning the rotation speed of the compressor 10 to the original speed may be performed.
Then, in step S57, the process is temporarily returned to the main flow, and thereafter, the process of the flowchart of fig. 5 is repeatedly executed.
Finally, the present embodiment will be summarized again with reference to the drawings. As shown in fig. 1, the present disclosure relates to an outdoor unit 2 of a refrigeration cycle apparatus 1 configured to be connected to a load apparatus 3 including a 1 st expansion valve 50 corresponding to a "1 st expansion device" and an evaporator 60. The outdoor unit 2 includes: the refrigerant outlet port PO2 and the refrigerant inlet port PI2 connected to the load device 3, the 1 st flow path F1, the compressor 10, the condenser 20, the 2 nd expansion valve 40 corresponding to the "2 nd expansion device", the 2 nd flow path F2, the 3 rd expansion valve 71 corresponding to the "3 rd expansion device", the receiver 73, the 3 rd flow path F3, and the on-off valve 78. The 1 st flow path F1 is a flow path from the refrigerant inlet port PI2 to the refrigerant outlet port PO2, and forms a circulation flow path for circulating the refrigerant together with the load device 3. The compressor 10, the condenser 20, and the 2 nd expansion valve 40 are disposed in the 1 st flow path F1. The 2 nd flow path F2 is branched from a portion between the condenser 20 of the 1 st flow path F1 and the 2 nd expansion valve 40, and returns the refrigerant passing through the condenser 20 to the compressor 10. The 3 rd expansion valve 71 and the liquid receiver 73 are disposed in this order in the 2 nd flow path F2 from the branching point of the 2 nd flow path F2 from the 1 st flow path F1. The 3 rd flow path F3 connects the portion between the 2 nd expansion valve 40 and the refrigerant outlet port PO2 in the 1 st flow path F1 and the refrigerant inlet of the receiver 73. The on-off valve 78 is disposed in the 3 rd flow path F3.
As shown in fig. 5, the on-off valve 78 is configured to be opened when the pressure P1 at the portion between the 2 nd expansion valve 40 and the refrigerant outlet port PO2 in the 1 st flow path F1 exceeds a threshold value corresponding to the design pressure (yes in S51).
Since the 3 rd flow path F3 and the opening/closing valve 78 are provided in this way, even if the pressure P1 increases rapidly at the start of the evacuation operation, the pressure P1 can be reduced rapidly. Thus, CO using the supercritical region is used in the high-pressure portion 2 In the case of a refrigerant, for example, a low-pressure pipe and the load device 3 may be used.
In addition, by disposing the liquid receiver 73 in the 2 nd flow path F2, even if CO in the supercritical region is used 2 Such as refrigerant, may be stored in the liquid refrigerant state in the liquid receiver 73. In addition, it is possible to ensure supercooling of the piping portion through which the liquid refrigerant flows, and to improve the performance of the refrigeration cycle apparatus.
The outdoor unit 2 further includes a flow rate adjustment valve 72, and the flow rate adjustment valve 72 is configured to be disposed in the 2 nd flow path F2 and adjust the discharge flow rate of the liquid refrigerant from the receiver 73.
The outdoor unit 2 further includes a heat exchanger 30, and the heat exchanger 30 is configured to have a 1 st passage H1 and a 2 nd passage H2, and to exchange heat between the refrigerant flowing through the 1 st passage H1 and the refrigerant flowing through the 2 nd passage H2. The 1 st passage H1 of the heat exchanger 30 is disposed between the condenser 20 of the 1 st passage F1 and a branching point at which the pipe 91 branches from the pipe 82, and the 2 nd passage H2 of the heat exchanger 30 is disposed between the flow rate adjustment valve 72 of the 2 nd passage F2 and the compressor 10.
The compressor 10 has a discharge port G2, a suction port G1, and a medium pressure port G3. The outdoor unit 2 further includes a flow path switching unit 74, and the flow path switching unit 74 is configured to be able to switch the destination of the refrigerant passing through the 2 nd flow path F2 to either one of the medium pressure port G3 and the suction port G1. As shown in fig. 5, the flow path switching unit 74 is configured to select the suction port G1 as the destination when the pressure P1 in the portion downstream of the 2 nd expansion valve 40 in the 1 st flow path F1 is lower than the pressure P2 of the liquid receiver 73 (no in S52).
With such a configuration, the pressure of the liquid receiver 73 is reduced when the pressure of the liquid receiver 73 increases, so that an operation condition in which the pressure of the liquid receiver 73 increases can be allowed, and the operation range can be widened.
The outdoor unit 2 further includes: a pressure sensor 112 that detects a pressure P1 in a portion of the 1 st flow path F1 downstream of the 2 nd expansion valve 40; and a control device 100 for controlling the compressor 10 and the on-off valve 78. As shown in fig. 5, when the pressure P1 detected by the pressure sensor 112 changes from a state lower than the threshold value to a state higher than the threshold value (yes in S51), the control device 100 opens the on-off valve 78 (S54) and decreases the rotation speed of the compressor 10 (S55).
By thus linking the on-off valve 78 and the compressor 10, the pressure P1 can be quickly reduced even if the pressure P1 is suddenly increased.
While the present embodiment has been described above by way of example with respect to a refrigerating apparatus including the refrigeration cycle apparatus 1, the refrigeration cycle apparatus 1 may be used in an air conditioner or the like.
It should be understood that the embodiments disclosed herein are illustrative only and not limiting in all respects. The scope of the present invention is shown by the claims rather than the description of the above embodiments, and is intended to include meaning equivalent to the claims and all modifications within the scope.

Claims (6)

1. An outdoor unit of a refrigeration cycle apparatus configured to be connected to a load apparatus including a 1 st expansion device and an evaporator, the outdoor unit comprising:
a refrigerant outlet port and a refrigerant inlet port for connection with the load device;
a 1 st flow path that reaches from the refrigerant inlet port to the refrigerant outlet port, and forms a circulation flow path for circulating the refrigerant together with the load device;
a compressor, a condenser, and a 2 nd expansion device disposed in the 1 st flow path;
a 2 nd flow path configured to branch from a portion between the condenser and the 2 nd expansion device of the 1 st flow path and return the refrigerant passing through the condenser to the compressor;
a 3 rd expansion device and a liquid receiver which are disposed in the 2 nd flow path in this order from a branching point of the 2 nd flow path from the 1 st flow path;
a 3 rd flow path connecting a portion of the 1 st flow path between the 2 nd expansion device and the refrigerant outlet port with a refrigerant inlet of the receiver; and
an opening/closing valve disposed in the 3 rd flow path,
the opening/closing valve is configured to be opened when the pressure of a portion between the 2 nd expansion device and the refrigerant outlet port in the 1 st flow path exceeds a threshold value.
2. The outdoor unit of claim 1, wherein,
the outdoor unit further includes a flow rate adjustment valve configured to be disposed in the 2 nd flow path and to adjust a discharge flow rate of the liquid refrigerant from the receiver.
3. The outdoor unit of claim 2, wherein,
the outdoor unit further includes a heat exchanger having a 1 st passage and a 2 nd passage, and configured to exchange heat between the refrigerant flowing through the 1 st passage and the refrigerant flowing through the 2 nd passage,
the 1 st passage of the heat exchanger is arranged between the condenser of the 1 st passage and the branch point,
the 2 nd passage of the heat exchanger is disposed between the flow rate adjustment valve of the 2 nd passage and the compressor.
4. The outdoor unit of claim 1, wherein,
the compressor has:
a discharge port;
a suction port; and
a medium-pressure port,
the outdoor unit further includes a flow path switching unit configured to be able to switch a destination of the refrigerant passing through the 2 nd flow path to either one of the intermediate pressure port and the suction port,
the flow path switching unit is configured to select the suction port as the destination when the pressure of a portion of the 1 st flow path downstream of the 2 nd expansion device is lower than the pressure of the liquid receiver.
5. The outdoor unit of claim 1, wherein,
the outdoor unit further includes:
a pressure sensor that detects a pressure in a portion of the 1 st flow path downstream of the 2 nd expansion device; and
a control device for controlling the compressor and the on-off valve,
the control device is configured to open the on-off valve and reduce the rotation speed of the compressor when the detection value of the pressure sensor changes from a state lower than a threshold value to a state higher than the threshold value.
6. A refrigeration cycle device is provided with:
an outdoor unit according to any one of claims 1 to 5; and
the load device.
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