WO2018011841A1 - Appareil de réfrigération et climatisation - Google Patents

Appareil de réfrigération et climatisation Download PDF

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Publication number
WO2018011841A1
WO2018011841A1 PCT/JP2016/070375 JP2016070375W WO2018011841A1 WO 2018011841 A1 WO2018011841 A1 WO 2018011841A1 JP 2016070375 W JP2016070375 W JP 2016070375W WO 2018011841 A1 WO2018011841 A1 WO 2018011841A1
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Prior art keywords
solenoid valve
compressor
expansion mechanism
refrigerant
refrigerating
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PCT/JP2016/070375
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English (en)
Japanese (ja)
Inventor
慎一 浅井
光史 新海
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三菱電機株式会社
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2016/070375 priority Critical patent/WO2018011841A1/fr
Publication of WO2018011841A1 publication Critical patent/WO2018011841A1/fr

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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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle

Definitions

  • the present invention relates to a refrigeration air conditioner that suppresses the liquid hammer phenomenon that occurs when the compressor is restarted after the pump is stopped.
  • the refrigeration air conditioner includes a refrigeration cycle circuit in which a compressor, a condenser, an expansion mechanism, and an evaporator are sequentially connected by piping, and the refrigerant flows in this order.
  • a conventional refrigeration air conditioner is known in which an electromagnetic valve is provided on the upstream side of the expansion mechanism.
  • a conventional refrigeration air conditioner equipped with such a solenoid valve is pump-down when stopping the compressor, such as when stopping the operation of the apparatus, or when stopping the circulation of the refrigerant in the refrigeration cycle circuit during the operation. Do the driving.
  • the pump-down operation means that the electromagnetic valve is closed before the compressor is stopped, and the refrigerant pressure from the downstream side of the electromagnetic valve to the compressor in the refrigeration cycle circuit becomes a predetermined pressure (for example, about atmospheric pressure).
  • the operation of the compressor is stopped. That is, in the pump down operation, the refrigerant from the downstream side of the solenoid valve in the refrigeration cycle circuit to the compressor is sent to the range from the compressor in the refrigeration cycle circuit to the upstream side of the solenoid valve, and then the compressor is Stop. Thereby, effects such as prevention of liquid back to the compressor when the compressor is restarted can be obtained.
  • the conventional refrigeration and air-conditioning apparatus is provided with a downstream side of the condenser for the purpose of improving the performance and suppressing the discharge superheat degree of the compressor, and the like.
  • a cooler and an injection circuit for injecting the liquid refrigerant flowing out of the supercooler into the compression chamber of the compressor are provided.
  • the injection circuit includes an injection pipe that connects the downstream side of the subcooler and the compression chamber of the compressor, and an expansion mechanism that is provided in the injection pipe and adjusts the amount of refrigerant flowing through the injection pipe (that is, the injection amount). And comprising.
  • the conventional refrigerating and air-conditioning apparatus having a supercooler and an injection circuit and performing a pump-down operation opens the liquid hammer even in the expansion mechanism of the injection circuit when the electromagnetic valve of the injection circuit is opened when the compressor is restarted.
  • the phenomenon occurs.
  • the refrigerant that has flowed out of the supercooler has a high degree of supercooling and a high liquid density. For this reason, the impact force to the expansion mechanism of the injection circuit is further increased.
  • a conventional refrigeration / air-conditioning apparatus has not been proposed that includes means for suppressing the liquid hammer phenomenon in the expansion mechanism of the injection circuit. For this reason, the conventional refrigerating and air-conditioning apparatus has a problem that the liquid hammer phenomenon in the expansion mechanism of the injection circuit cannot be suppressed, and the expansion mechanism of the injection circuit may be damaged.
  • the present invention has been made to solve the above-described problems, and provides a refrigeration air conditioner that can suppress the liquid hammer phenomenon with an expansion mechanism of an injection circuit and prevent damage to the expansion mechanism of the injection circuit. With the goal.
  • a refrigerating and air-conditioning apparatus is provided in a refrigeration cycle circuit in which a compressor, a condenser, a first expansion mechanism and an evaporator are connected by piping, and a pipe between the condenser and the first expansion mechanism.
  • An injection pipe connected between the other end and communicating with the compression chamber of the compressor; a second electromagnetic valve provided in the injection pipe; and the second electromagnetic valve and the compressor in the injection pipe
  • a second expansion mechanism provided at an intermediate position, a first end connected between the condenser and the second electromagnetic valve, and a second end connected to the second electromagnetic valve and the second expansion.
  • Bypass piping connected between the mechanism and the bypass piping And when the third solenoid valve is opened with the second solenoid valve closed, the second solenoid valve flows into the second expansion mechanism when the second solenoid valve is opened.
  • a smaller amount of liquid refrigerant than the liquid refrigerant that flows is configured to flow into the second expansion mechanism.
  • the refrigerating and air-conditioning apparatus opens the third solenoid valve before opening the second solenoid valve, which is the solenoid valve of the injection circuit, when the compressor is restarted after the pump down operation.
  • the amount of the liquid refrigerant flowing into the second expansion mechanism can be reduced. For this reason, the refrigerating and air-conditioning apparatus according to the present invention can suppress the liquid hammer phenomenon in the second expansion mechanism, and can prevent the second expansion mechanism from being damaged.
  • FIG. 2 is a ph diagram showing a refrigeration cycle of the refrigeration air-conditioning apparatus according to Embodiment 1 of the present invention.
  • the refrigerating air conditioner concerning Embodiment 1 of this invention, it is explanatory drawing for demonstrating the operation
  • FIG. 1 is a refrigerant circuit diagram of a refrigerating and air-conditioning apparatus according to Embodiment 1 of the present invention.
  • a refrigerating and air-conditioning apparatus 100 according to Embodiment 1 includes a refrigerating cycle circuit 1 in which a compressor 2 and a condenser 3, for example, an expansion mechanism 6 that is an expansion valve and an evaporator 4 are connected by piping.
  • the refrigerant in the refrigeration cycle circuit 1 flows in the order of the compressor 2, the condenser 3, the expansion mechanism 6 and the evaporator 4, and circulates in the refrigeration cycle circuit 1.
  • the refrigerating and air-conditioning apparatus 100 according to Embodiment 1 performs a pump-down operation when the compressor 2 is stopped.
  • the refrigerating and air-conditioning apparatus 100 includes an electromagnetic valve 7 in a pipe between the condenser 3 and the expansion mechanism 6.
  • the expansion mechanism 6 corresponds to the first expansion mechanism of the present invention.
  • the solenoid valve 7 corresponds to the first solenoid valve of the present invention.
  • the refrigeration air conditioner 100 flows out of the supercooler 5 and the supercooler 5 for the purpose of improving the performance and suppressing the discharge superheat degree of the compressor 2.
  • an injection circuit 8 for injecting the liquid refrigerant into the compressor 2.
  • the subcooler 5 is provided on the downstream side of the condenser 3, that is, between the condenser 3 and the electromagnetic valve 7.
  • the subcooler 5 cools the refrigerant that has flowed out of the condenser 3 and puts the refrigerant into a supercooled state.
  • the refrigerant that has flowed out of the condenser 3 is cooled by the refrigerant that flows through the injection circuit 8.
  • the injection circuit 8 includes an injection pipe 11, for example, an expansion mechanism 9 that is an expansion valve, and an electromagnetic valve 10.
  • One end of the injection pipe 11 is connected between the subcooler 5 and the electromagnetic valve 7, and the other end communicates with the compression chamber of the compressor 2.
  • the solenoid valve 10 is provided in the injection pipe 11 and is closed during the pump-down operation, and closes the flow path in the injection pipe 11.
  • the expansion mechanism 9 is provided at a position between the electromagnetic valve 10 and the compressor 2 in the injection pipe 11.
  • the expansion mechanism 9 adjusts the amount of refrigerant flowing through the injection pipe 11, that is, the amount of refrigerant injected into the compression chamber of the compressor 2 (injection amount).
  • a portion of the injection pipe 11 on the downstream side of the expansion mechanism 9 passes through the supercooler 5.
  • the solenoid valve 10 corresponds to a second solenoid valve of the present invention.
  • the expansion mechanism 9 corresponds to the second expansion mechanism of the present invention.
  • the refrigerating and air-conditioning apparatus 100 includes a bypass circuit 12 in order to suppress the liquid hammer phenomenon in the expansion mechanism 9.
  • the bypass circuit 12 includes a bypass pipe 16 and an electromagnetic valve 13 provided in the bypass pipe 16.
  • the bypass pipe 16 has a first end 16 a connected between the condenser 3 and the electromagnetic valve 10. More specifically, the first end 16 a of the bypass pipe 16 is connected between the supercooler 5 and the electromagnetic valve 10. In FIG. 1, the first end 16 a of the bypass pipe 16 is connected to the injection pipe 11. However, even if the first end 16 a is connected to the pipe connecting the subcooler 5 and the electromagnetic valve 7. Good.
  • the second end portion 16 b of the bypass pipe 16 is connected to the injection pipe 11 portion between the electromagnetic valve 10 and the expansion mechanism 9.
  • the electromagnetic valve 13 is closed during the pump-down operation and closes the flow path in the bypass pipe 16.
  • the solenoid valve 13 corresponds to a third solenoid valve of the present invention.
  • the compressor 2 when the compressor 2 is restarted after the pump-down operation, the refrigerant flowing through the bypass pipe 16 is supplied to the upstream side of the expansion mechanism 9 of the injection circuit 8 with the solenoid valve 10 of the injection circuit 8 closed. Then, the liquid hammer phenomenon in the expansion mechanism 9 is suppressed.
  • the electromagnetic valve 13 when the electromagnetic valve 13 is opened with the electromagnetic valve 10 closed, a smaller amount of liquid refrigerant flows into the expansion mechanism 9 than the liquid refrigerant that flows into the expansion mechanism 9 when the electromagnetic valve 10 is opened. There is a need. Thereby, the impact force when the liquid refrigerant flows into the expansion mechanism 9 can be suppressed, and the liquid hammer phenomenon in the expansion mechanism 9 can be suppressed.
  • the inner diameter of the bypass pipe 16 is made smaller than the inner diameter of the portion of the injection pipe 11 closer to the electromagnetic valve 10 than the expansion mechanism 9.
  • the refrigerating and air-conditioning apparatus 100 includes a plurality of sensors and a control device 50 that controls each component of the refrigerating and air-conditioning apparatus 100 based on detection values of these sensors.
  • the injection pipe 11 is provided with a pressure sensor 14 on the upstream side of the electromagnetic valve 10.
  • the pressure sensor 14 detects the refrigerant pressure between the subcooler 5 and the electromagnetic valve 10. For this reason, you may provide the pressure sensor 14 in piping which connects the subcooler 5 and the solenoid valve 7.
  • FIG. The injection pipe 11 is provided with a pressure sensor 15 between the electromagnetic valve 10 and the expansion mechanism 9.
  • the pressure sensor 15 detects the pressure of the refrigerant flowing between the electromagnetic valve 10 and the expansion mechanism 9, in other words, the pressure of the refrigerant flowing into the expansion mechanism 9.
  • the pressure sensor 15 is provided in the injection piping 11 part upstream from the connection location with the 2nd end part 16b of the bypass piping 16, with the 2nd end part 16b of the bypass piping 16 You may provide the pressure sensor 15 in the injection piping 11 part downstream from a connection location.
  • the pressure sensor 14 corresponds to the first pressure sensor of the present invention
  • the pressure sensor 15 corresponds to the second pressure sensor of the present invention.
  • the control device 50 is configured by dedicated hardware or a CPU (Central Processing Unit, central processing unit, processing unit, arithmetic unit, microprocessor, microcomputer, processor) that executes a program stored in a memory. .
  • a CPU Central Processing Unit, central processing unit, processing unit, arithmetic unit, microprocessor, microcomputer, processor
  • control device 50 When the control device 50 is dedicated hardware, the control device 50 may be, for example, a single circuit, a composite circuit, an ASIC (application specific integrated circuit), an FPGA (field-programmable gate array), or a combination of these. Applicable. Each functional unit realized by the control device 50 may be realized by individual hardware, or each functional unit may be realized by one piece of hardware.
  • ASIC application specific integrated circuit
  • FPGA field-programmable gate array
  • each function executed by the control device 50 is realized by software, firmware, or a combination of software and firmware.
  • Software and firmware are described as programs and stored in a memory.
  • the CPU implements each function of the control device 50 by reading and executing a program stored in the memory.
  • the memory is a nonvolatile or volatile semiconductor memory such as a RAM, a ROM, a flash memory, an EPROM, or an EEPROM.
  • control device 50 may be realized by dedicated hardware, and a part may be realized by software or firmware.
  • the control device 50 includes a time measuring unit 51, a comparison unit 52, and a control unit 53 as functional units.
  • the timer 51 measures the time since the compressor 2 was started.
  • the comparison unit 52 serves as an index as to whether or not to open the electromagnetic valve 10 of the injection circuit 8, so that the value of the pressure sensor 14, 15 or the timing unit is compared with the comparison value Are compared.
  • the control unit 53 controls the start, operation, and stop of the compressor 2.
  • the control unit 53 controls opening / closing of the electromagnetic valves 7, 10, 13, opening degrees of the expansion mechanisms 6, 9, and the like.
  • the control unit 53 of the control device 50 opens the electromagnetic valves 7 and 10 and continues the operation of the compressor 2.
  • the control unit 53 controls the expansion mechanisms 6 and 9 to an arbitrary opening degree.
  • the electromagnetic valve 13 of the bypass circuit 12 may be in a closed state or an open state.
  • the solenoid valve 13 of the bypass circuit 12 is opened and operated so as to ensure a large amount of refrigerant to be injected.
  • the gaseous refrigerant sucked into the compressor 2 is compressed to a high-temperature and high-pressure gaseous refrigerant.
  • This high-temperature and high-pressure gaseous refrigerant is discharged from the compressor 2, flows into the condenser 3, condenses by exchanging heat and dissipating heat, and flows out as a gas-liquid two-phase or liquid refrigerant.
  • This refrigerant flows into the supercooler 5 and is cooled to the supercooled state by the refrigerant flowing through the injection pipe 11.
  • the refrigerant flowing out of the supercooler 5 in the supercooled state is branched into the evaporator 4 side and the injection circuit 8.
  • the liquid refrigerant on the evaporator 4 side is decompressed and expanded by the expansion mechanism 6, flows into the evaporator 4, evaporates by exchanging heat and absorbing heat, and becomes superheated gas and is sucked into the compressor 2.
  • the liquid refrigerant in the injection circuit 8 is decompressed and expanded by the expansion mechanism 9, cools the refrigerant flowing through the subcooler 5, and is then injected into the compression chamber of the compressor 2.
  • control method of the opening degree of the expansion mechanisms 6 and 9 by the control unit 53 is arbitrary, and various known methods may be used.
  • the opening degree of the expansion mechanism 6 may be controlled so that the degree of superheat of the refrigerant flowing out of the evaporator 4 becomes a specified value.
  • the opening degree of the expansion mechanism 9 may be controlled so that the degree of superheat of the gaseous refrigerant flowing through the injection pipe 11 after flowing out of the supercooler 5 becomes a specified value.
  • the opening degree of the expansion mechanism 9 may be controlled based on the discharge temperature of the compressor 2.
  • the control unit 53 of the control device 50 closes the electromagnetic valves 7, 10, and 13. And the control part 53 stops the compressor 2 after continuing the driving
  • the operation of the compressor 2 is continued until, for example, the pressure on the upstream side (that is, the suction side) of the compressor 2 is reduced to a predetermined pressure.
  • the operation of the compressor 2 is continued for a specified time. Thereby, the refrigerant existing on the upstream side (that is, the suction side) of the compressor 2 is sent out to the downstream side (that is, the discharge side) of the compressor 2 by the compressor 2.
  • the refrigerant existing on the upstream side (that is, the suction side) of the compressor 2 is the refrigerant existing from the solenoid valve 7 to the suction side of the compressor 2 and the injection pipe 11 between the solenoid valve 10 and the compressor 2.
  • the downstream side (that is, the discharge side) of the compressor 2 is the refrigeration cycle circuit 1 part from the discharge side of the compressor 2 to the electromagnetic valve 7, the injection pipe 11 part upstream of the electromagnetic valve 10, and the first This is a bypass pipe 16 portion from the end portion 16 a to the electromagnetic valve 13.
  • FIG. 2 is a ph diagram showing a refrigeration cycle of the refrigeration air-conditioning apparatus according to Embodiment 1 of the present invention.
  • FIG. 3 is explanatory drawing for demonstrating the operation
  • FIG. 2A shows a state in which an impact liquid hammer phenomenon that can damage the expansion mechanism 9 may occur after the compressor 2 is restarted.
  • FIG. 2B shows a state after the state of FIG. 2A, in which the liquid hammer phenomenon of impact that causes the expansion mechanism 9 to break is not generated. That is, FIG. 2B shows a state where the electromagnetic valve 10 of the injection circuit 8 may be opened after the compressor 2 is restarted.
  • the control unit 53 of the control device 50 opens the electromagnetic valve 7 and starts the compressor 2. Moreover, the control part 53 controls the expansion mechanisms 6 and 9 to arbitrary opening.
  • the electromagnetic valve 10 of the injection circuit 8 is opened, an amount of refrigerant corresponding to the pressure difference before and after the electromagnetic valve 10 flows into the expansion mechanism 9 of the injection circuit 8. For this reason, if the pressure difference between the front and rear of the solenoid valve 10 is larger than a specified pressure value, a large amount of liquid refrigerant tries to flow into the expansion mechanism 9 and collides with the expansion mechanism 9, and the liquid hammer phenomenon occurs in the expansion mechanism 9. Will occur.
  • the refrigerating and air-conditioning apparatus 100 includes the supercooler 5
  • the degree of supercooling of the refrigerant flowing into the expansion mechanism 9 is large. That is, since the liquid density of the refrigerant flowing into the expansion mechanism 9 increases, more liquid refrigerant tends to flow into the expansion mechanism 9, and the impact force on the expansion mechanism 9 is further increased and the expansion mechanism 9. There is concern about damage.
  • the solenoid valve 10 is opened with ⁇ P2 being smaller than ⁇ P0. In this case, the expansion mechanism 9 can be prevented from being damaged. Therefore, in the first embodiment, when ⁇ P2 becomes equal to or less than a specified value ⁇ P ⁇ obtained by multiplying ⁇ P0 by a coefficient ⁇ (less than 1) set as a safety factor, the electromagnetic valve 10 is opened to prevent the expansion mechanism 9 from being damaged. ing.
  • the pressure of the refrigerant on the upstream side of the electromagnetic valve 10 of the injection circuit 8 is equal to that of the refrigeration cycle shown in FIG. 2 (A).
  • High pressure Pa that is, the pressure of the refrigerant on the upstream side of the electromagnetic valve 10 of the injection circuit 8 becomes a high pressure equivalent to the pressure from the discharge side of the compressor 2 to the outlet side of the subcooler 5 in the refrigeration cycle circuit 1.
  • the pressure of the refrigerant on the downstream side of the electromagnetic valve 10 of the injection circuit 8 becomes the low pressure Pb of the refrigeration cycle shown in FIG.
  • ⁇ P2 Pa ⁇ Pb is larger than ⁇ P0.
  • the inner diameter of the bypass pipe 16 is made smaller than the inner diameter of the portion of the injection pipe 11 closer to the electromagnetic valve 10 than the expansion mechanism 9. For this reason, the amount of the liquid refrigerant flowing from the bypass pipe 16 to the downstream side of the electromagnetic valve 10 is an amount that does not damage the expansion mechanism 9.
  • the pressure Pc shown in FIG. 2A is the pressure of the liquid refrigerant flowing from the bypass pipe 16 to the downstream side of the solenoid valve 10.
  • the inner diameter of the portion of the injection pipe 11 closer to the electromagnetic valve 10 than the expansion mechanism 9 is larger than the inner diameter of the bypass pipe 16. For this reason, when the solenoid valve 10 of the injection circuit 8 is opened, as shown in FIG. 2 (B), the downstream side of the solenoid valve 10 (the injection pipe 11 portion between the solenoid valve 10 and the expansion mechanism 9). A refrigerant having a pressure Pd slightly higher than the refrigerant pressure Pe flows from the solenoid valve 10 to the downstream side.
  • FIG. 4 is an example of a control flow for controlling the opening / closing of the solenoid valve of the injection circuit when the compressor is restarted in the refrigerating and air-conditioning apparatus according to Embodiment 1 of the present invention.
  • the control unit 53 closes the electromagnetic valve 10 of the injection circuit 8, opens the electromagnetic valve 13 of the bypass circuit 12, and starts the compressor 2 (step S2).
  • the pressure sensors 14 and 15 detect the refrigerant pressures P14 and P15 at the respective sensor positions.
  • the comparison unit 52 calculates P14-P15, which is a comparison value, that is, calculates ⁇ P2, and compares the comparison value with the specified value ⁇ P ⁇ .
  • the control unit 53 When the comparison value P14-P15 is larger than the specified value ⁇ P ⁇ , the control unit 53 returns to Step S2. That is, the control unit 53 continues the operation of the compressor 2 with the electromagnetic valve 10 of the injection circuit 8 closed and the electromagnetic valve 13 of the bypass circuit 12 opened. On the other hand, when the comparison value P14-P15 becomes equal to or less than the specified value ⁇ P ⁇ , the control unit 53 opens the electromagnetic valve 10 of the injection circuit 8 (step S4), and ends the opening / closing control of the electromagnetic valve 10 (step S5). ).
  • FIG. 5 is another example of a control flow for controlling the opening and closing of the solenoid valve of the injection circuit when the compressor is restarted in the refrigerating and air-conditioning apparatus according to Embodiment 1 of the present invention.
  • the control unit 53 closes the electromagnetic valve 10 of the injection circuit 8, opens the electromagnetic valve 13 of the bypass circuit 12, and starts the compressor 2 (step S12).
  • step S ⁇ b> 13 the timer unit 51 measures the operation time T after the compressor 2 is started.
  • step S13 the comparison unit 52 compares T, which is the detection time of the time measuring unit 51, with the specified time T1.
  • the control unit 53 When the time T, which is the detection time of the time measuring unit 51, is shorter than the specified time T1, the control unit 53 returns to step S12. That is, the control unit 53 continues the operation of the compressor 2 with the electromagnetic valve 10 of the injection circuit 8 closed and the electromagnetic valve 13 of the bypass circuit 12 opened.
  • T which is the detection time of the time measuring unit 51
  • the control unit 53 opens the electromagnetic valve 10 of the injection circuit 8 (step S14) and ends the opening / closing control of the electromagnetic valve 10 ( Step S15).
  • the refrigerating and air-conditioning apparatus 100 according to Embodiment 1 restarts the compressor 2 after the pump-down operation, by opening the electromagnetic valve 13 of the bypass circuit before opening the electromagnetic valve 10 of the injection circuit 8, The amount of liquid refrigerant flowing into the expansion mechanism 9 of the injection circuit 8 can be reduced. For this reason, the refrigerating and air-conditioning apparatus 100 according to Embodiment 1 can suppress the liquid hammer phenomenon in the expansion mechanism 9 of the injection circuit 8 and can prevent the expansion mechanism 9 from being damaged.
  • the refrigerating and air-conditioning apparatus 100 according to the first embodiment can suppress the liquid hammer phenomenon in the expansion mechanism 9 of the injection circuit 8 without reducing the inner diameter of the injection pipe 11 of the injection circuit 8. For this reason, the refrigerating and air-conditioning apparatus 100 according to Embodiment 1 does not have a shortage of refrigerant amount to be injected into the compression chamber of the compressor 2 when entering the stable state.
  • the bypass pipe 16 can also function as an injection pipe. For this reason, the amount of refrigerant injected into the compression chamber of the compressor 2 can be further increased.
  • Embodiment 2 the first end portion 16 a of the bypass pipe 16 is connected between the subcooler 5 and the electromagnetic valve 10. However, if the first end 16a of the bypass pipe 16 is connected between the condenser 3 and the electromagnetic valve 10, the present invention can be implemented. Therefore, you may comprise the refrigerating and air-conditioning apparatus 100 as follows, for example.
  • items that are not particularly described are the same as those in the first embodiment, and the same functions and configurations are described using the same reference numerals.
  • FIG. 6 is a refrigerant circuit diagram of the refrigerating and air-conditioning apparatus according to Embodiment 2 of the present invention.
  • the refrigerating and air-conditioning apparatus 100 according to the second embodiment is different from the refrigerating and air-conditioning apparatus 100 shown in the first embodiment in the connection location of the first end portion 16a of the bypass pipe 16.
  • the first end 16 a of the bypass pipe 16 is connected between the condenser 3 and the subcooler 5.
  • the refrigerant flowing out of the condenser 3 is a gas-liquid two-phase refrigerant in which a gaseous refrigerant and a liquid refrigerant are mixed, or a liquid refrigerant having a small degree of supercooling. For this reason, this gas-liquid two-phase state or a liquid refrigerant with a small degree of supercooling flows into the bypass pipe 16.
  • this gas-liquid two-phase state or a liquid refrigerant with a small degree of supercooling flows into the bypass pipe 16.
  • the liquid flowing into the expansion mechanism 9 when the electromagnetic valve 10 is opened when the electromagnetic valve 13 is opened when the electromagnetic valve 10 is closed, the liquid flowing into the expansion mechanism 9 when the electromagnetic valve 10 is opened.
  • a smaller amount of liquid refrigerant than the refrigerant needs to flow into the expansion mechanism 9.
  • the refrigerant flowing out of the bypass pipe 16, that is, the refrigerant flowing into the expansion mechanism 9 is made into a gas-liquid two-phase state, thereby reducing the amount of the liquid refrigerant that flows into the expansion mechanism 9. ing.
  • the controller 53 of the control device 50 injects liquid refrigerant having a large degree of supercooling into the compressor 2 during operation of the refrigeration air conditioner 100 in a stable state after the compressor 2 is activated.
  • the electromagnetic valve 13 of the bypass circuit 12 is closed.
  • the pump-down operation in the refrigeration air conditioning apparatus 100 according to the second embodiment is the same as that of the first embodiment. For this reason, below, operation
  • FIG. 7 is a ph diagram showing the refrigeration cycle of the refrigeration air-conditioning apparatus according to Embodiment 2 of the present invention.
  • FIG. 8 is explanatory drawing for demonstrating the operation
  • FIG. 7A shows a state in which an impact liquid hammer phenomenon that can damage the expansion mechanism 9 may occur after the compressor 2 is restarted.
  • FIG. 7B shows a state after the state of FIG. 7A, in which a shocking liquid hammer phenomenon that causes damage to the expansion mechanism 9 does not occur. That is, FIG. 7B shows a state where the electromagnetic valve 10 of the injection circuit 8 may be opened after the compressor 2 is restarted.
  • the control unit 53 of the control device 50 opens the electromagnetic valve 7 and starts the compressor 2. Moreover, the control part 53 controls the expansion mechanisms 6 and 9 to arbitrary opening. As described above, when the pressure difference ⁇ P2 before and after the electromagnetic valve 10 is larger than ⁇ P0, an impact liquid hammer phenomenon that causes the expansion mechanism 9 to break occurs. Therefore, if the solenoid valve 10 is opened in a state where ⁇ P2 is smaller than ⁇ P0, the expansion mechanism 9 can be prevented from being damaged.
  • the pressure of the refrigerant on the upstream side of the electromagnetic valve 10 of the injection circuit 8 is equal to that of the refrigeration cycle shown in FIG. High pressure Pa. That is, the pressure of the refrigerant on the upstream side of the electromagnetic valve 10 of the injection circuit 8 becomes a high pressure equivalent to the pressure from the discharge side of the compressor 2 to the outlet side of the subcooler 5 in the refrigeration cycle circuit 1.
  • the refrigerant pressure on the downstream side of the electromagnetic valve 10 of the injection circuit 8 is the low pressure Pb of the refrigeration cycle shown in FIG.
  • ⁇ P2 Pa ⁇ Pb is larger than ⁇ P0.
  • the control unit 53 of the control device 50 restarts the compressor 2 with the electromagnetic valve 10 closed. Further, the control unit 53 restarts the compressor 2 with the electromagnetic valve 13 of the bypass circuit 12 opened. Thereby, when the compressor 2 is started, the refrigerant flowing out of the condenser 3 passes through the bypass pipe 16 and becomes a refrigerant in a gas-liquid two-phase state downstream of the solenoid valve 10 (the solenoid valve 10 and the expansion mechanism 9). It flows into the injection pipe 11 part) between.
  • the amount of the liquid refrigerant flowing from the bypass pipe 16 to the downstream side of the electromagnetic valve 10 is an amount that does not damage the expansion mechanism 9.
  • the pressure of the liquid refrigerant flowing from the bypass pipe 16 to the downstream side of the solenoid valve 10 is represented as Pf.
  • the opening / closing of the electromagnetic valve 10 can be controlled by the control flow described in FIG. 4 of the first embodiment. Further, for example, the opening and closing of the electromagnetic valve 10 can be controlled by the flow shown in FIG.
  • FIG. 9 is an example of a control flow for controlling the opening and closing of the solenoid valve of the injection circuit when the compressor is restarted in the refrigerating and air-conditioning apparatus according to Embodiment 2 of the present invention.
  • the control unit 53 closes the electromagnetic valve 10 of the injection circuit 8, opens the electromagnetic valve 13 of the bypass circuit 12, and starts the compressor 2 (step S22).
  • step S ⁇ b> 23 the timer unit 51 measures the operation time T after the compressor 2 is started.
  • step S23 the comparison unit 52 compares T, which is the detection time of the time measuring unit 51, with the specified time T2.
  • the controller 53 If the time T, which is the detection time of the timer 51, is shorter than the specified time T2, the controller 53 returns to step S22. That is, the control unit 53 continues the operation of the compressor 2 with the electromagnetic valve 10 of the injection circuit 8 closed and the electromagnetic valve 13 of the bypass circuit 12 opened. On the other hand, when T, which is the detection time of the time measuring unit 51, is equal to or longer than the specified time T2, the control unit 53 opens the electromagnetic valve 10 of the injection circuit 8 (step S24) and ends the opening / closing control of the electromagnetic valve 10 ( Step S25).
  • the refrigerating and air-conditioning apparatus 100 has a bypass circuit before opening the solenoid valve 10 of the injection circuit 8 when the compressor 2 is restarted after the pump-down operation, as in the first embodiment.
  • the electromagnetic valve 13 By opening the electromagnetic valve 13, the amount of liquid refrigerant flowing into the expansion mechanism 9 of the injection circuit 8 can be reduced.
  • the refrigerating and air-conditioning apparatus 100 according to the second embodiment can suppress the liquid hammer phenomenon in the expansion mechanism 9 of the injection circuit 8 and damage the expansion mechanism 9 as in the first embodiment. Can be prevented.
  • the refrigerating and air-conditioning apparatus 100 according to the second embodiment has a liquid hammer phenomenon in the expansion mechanism 9 of the injection circuit 8 without reducing the inner diameter of the injection pipe 11 of the injection circuit 8 as in the first embodiment. Can be suppressed. For this reason, the refrigerating and air-conditioning apparatus 100 according to the second embodiment does not have a shortage of the amount of refrigerant injected into the compression chamber of the compressor 2 when entering the stable state, as in the first embodiment.
  • the refrigerating and air-conditioning apparatus 100 according to the second embodiment causes the refrigerant in the gas-liquid two-phase state to flow into the downstream side of the electromagnetic valve 10 of the injection circuit 8 from the bypass pipe 16, and the expansion mechanism 9 of the injection circuit 8 The liquid hammer phenomenon is suppressed.
  • the refrigerating and air-conditioning apparatus 100 according to the second embodiment does not need to reduce the inner diameter of the bypass pipe 16.
  • the refrigerating and air-conditioning apparatus 100 according to the second embodiment stabilizes the time T2 from when the compressor 2 is restarted until it becomes stable after the compressor 2 according to the first embodiment is restarted. It can be made shorter than the time T1 until the state is reached.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
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  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

Un appareil de réfrigération et de climatisation selon la présente invention comporte : un circuit de cycle de réfrigération dans lequel un compresseur, un condenseur, un premier mécanisme d'expansion et un évaporateur sont reliés par une tuyauterie; une première électrovanne disposée sur la tuyauterie entre le condenseur et le premier mécanisme d'expansion; un super-refroidisseur placé entre le condenseur et la première électrovanne; une tuyauterie d'injection dont une extrémité est connectée entre le super-refroidisseur et la première électrovanne, et dont l'autre extrémité est en communication avec une chambre de compression du compresseur; une seconde électrovanne disposée sur la tuyauterie d'injection; un second mécanisme d'expansion disposé dans une position entre le compresseur et la seconde électrovanne dans la tuyauterie d'injection; une tuyauterie de dérivation, dont une première partie d'extrémité est connectée entre le condensateur et la seconde électrovanne, et dont une seconde partie d'extrémité est connectée entre la seconde électrovanne et le second mécanisme d'expansion; et une troisième électrovanne disposée sur la tuyauterie de dérivation. L'appareil est configuré de telle sorte que, lorsque la troisième électrovanne est ouverte, la quantité de réfrigérant liquide s'écoulant dans le second mécanisme d'expansion lorsque la seconde électrovanne est fermée est plus petite que la quantité de réfrigérant liquide s'écoulant dans le second mécanisme d'expansion lorsque la seconde électrovanne est ouverte.
PCT/JP2016/070375 2016-07-11 2016-07-11 Appareil de réfrigération et climatisation WO2018011841A1 (fr)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110425112A (zh) * 2019-08-12 2019-11-08 郑州海尔空调器有限公司 防压缩机液击的空调及防压缩机液击的控制方法

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JPS60148566U (ja) * 1984-03-13 1985-10-02 株式会社小松製作所 ヒ−トポンプ
JPH02187567A (ja) * 1989-01-13 1990-07-23 Mitsubishi Electric Corp 冷凍装置
JPH05164413A (ja) * 1991-12-13 1993-06-29 Daikin Ind Ltd 冷凍装置
JPH08233379A (ja) * 1995-02-24 1996-09-13 Mitsubishi Heavy Ind Ltd 冷凍装置
US20020021972A1 (en) * 2000-03-16 2002-02-21 Igor Vaisman Capacity control of refrigeration systems
WO2013001688A1 (fr) * 2011-06-29 2013-01-03 三菱電機株式会社 Dispositif de cycle de réfrigération
WO2015136706A1 (fr) * 2014-03-14 2015-09-17 三菱電機株式会社 Dispositif de réfrigation
EP3023711A1 (fr) * 2014-11-20 2016-05-25 Vaillant GmbH Contrôle de l'énergie d'injection de vapeur

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60148566U (ja) * 1984-03-13 1985-10-02 株式会社小松製作所 ヒ−トポンプ
JPH02187567A (ja) * 1989-01-13 1990-07-23 Mitsubishi Electric Corp 冷凍装置
JPH05164413A (ja) * 1991-12-13 1993-06-29 Daikin Ind Ltd 冷凍装置
JPH08233379A (ja) * 1995-02-24 1996-09-13 Mitsubishi Heavy Ind Ltd 冷凍装置
US20020021972A1 (en) * 2000-03-16 2002-02-21 Igor Vaisman Capacity control of refrigeration systems
WO2013001688A1 (fr) * 2011-06-29 2013-01-03 三菱電機株式会社 Dispositif de cycle de réfrigération
WO2015136706A1 (fr) * 2014-03-14 2015-09-17 三菱電機株式会社 Dispositif de réfrigation
EP3023711A1 (fr) * 2014-11-20 2016-05-25 Vaillant GmbH Contrôle de l'énergie d'injection de vapeur

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110425112A (zh) * 2019-08-12 2019-11-08 郑州海尔空调器有限公司 防压缩机液击的空调及防压缩机液击的控制方法
CN110425112B (zh) * 2019-08-12 2022-09-06 郑州海尔空调器有限公司 防压缩机液击的空调及防压缩机液击的控制方法

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