WO2021240615A1 - 冷凍サイクル装置 - Google Patents

冷凍サイクル装置 Download PDF

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Publication number
WO2021240615A1
WO2021240615A1 PCT/JP2020/020605 JP2020020605W WO2021240615A1 WO 2021240615 A1 WO2021240615 A1 WO 2021240615A1 JP 2020020605 W JP2020020605 W JP 2020020605W WO 2021240615 A1 WO2021240615 A1 WO 2021240615A1
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WIPO (PCT)
Prior art keywords
compressor
pressure
unit
refrigerant
condenser
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2020/020605
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English (en)
French (fr)
Japanese (ja)
Inventor
康太 鈴木
悠介 有井
洋貴 佐藤
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Filing date
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Priority to PCT/JP2020/020605 priority Critical patent/WO2021240615A1/ja
Priority to JP2022527292A priority patent/JP7309063B2/ja
Publication of WO2021240615A1 publication Critical patent/WO2021240615A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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 disclosure relates to a refrigeration cycle device using at least one compressor.
  • a compressor is used as the power of the heat source side unit in the refrigeration cycle device.
  • the compressor may have a set replacement time with the total operating time and the number of starts and stops (starting and stopping) as parameters. It is recommended to overhaul or replace the compressor with a new one when it is time to replace it.
  • the control device of the heat source side unit equipped with a compressor is communicated and connected to the load side unit equipped with an evaporator.
  • the control device of the heat source side unit acquires and acquires information on the temperature in the room or warehouse where the load side unit is installed (hereinafter, also referred to as “load temperature”) from the load side unit.
  • the drive frequency of the compressor can be controlled according to the information of the applied load temperature.
  • a plurality of compressors may be provided in the heat source side unit of the refrigeration cycle device.
  • Patent Document 1 in a refrigeration cycle apparatus including a plurality of compressors, the integrated operation time of each compressor is equalized based on the integrated operation time of each compressor. , The technology to rotate the compressor to be activated is described.
  • the control device of the heat source side unit When the control device of the heat source side unit is not communicatively connected to the load side unit, the control device of the heat source side unit generally has a low pressure refrigerant pressure sucked into the compressor (hereinafter referred to as “compressor suction pressure” or “compressor suction pressure”. It simply detects the "suction pressure”) and controls the compressor based on the difference between the detected suction pressure and the preset target pressure. In this case, since the control device of the heat source side unit cannot control the drive frequency of the compressor according to the load temperature, the load side unit implements the refrigerant shutoff by the electric valve for the purpose of preventing excessive cooling. NS.
  • the compressor of the heat source side unit may stop. After the compressor is stopped, the compressor is restarted when the specified time has elapsed or the suction pressure is restored. If the compressor is stopped and started frequently, there is a concern that the life of the compressor will be shortened.
  • Patent Document 1 Japanese Patent No. 3082755
  • the compressors are activated so that the integrated operation time of each compressor is equalized.
  • a technique for rotating a compressor is known.
  • the integrated operation time of each compressor is made equal, but the suction pressure of the compressor is increased in the low load period such as winter and intermediate period (spring and autumn). If the operation near the threshold pressure for starting and stopping the compressor continues, some compressors may repeatedly start and stop. Therefore, there is a concern that the number of times of starting and stopping of some compressors will increase and the life of the compressors will be shortened only by the parameter of the integrated operation time.
  • the present disclosure has been made to solve the above-mentioned problems, and an object thereof is to appropriately set the number of times of starting and stopping of the compressor even if the control device for controlling the compressor does not use the information of the load temperature. It is to be able to reduce to.
  • the refrigeration cycle device is a refrigeration cycle device in which a refrigerant circulates in a circulation flow path connecting at least one compressor, a condenser, a decompression device, and an evaporator.
  • This refrigeration cycle device is based on the result of comparing a pressure sensor that detects the suction pressure, which is the pressure of the refrigerant sucked into at least one compressor, with the suction pressure and the threshold pressure detected by the pressure sensor. It is equipped with a control device that starts and stops one compressor.
  • the control device includes a storage unit that stores the operation history of the refrigeration cycle device, and a calculation unit that adjusts the threshold pressure based on the operation history of the refrigeration cycle device.
  • control device that controls the compressor can appropriately reduce the number of times the compressor is started and stopped without using the information on the load temperature.
  • FIG. 1 is a schematic view showing an example of the configuration of the refrigeration cycle apparatus 100 according to the first embodiment.
  • the refrigeration cycle device 100 includes a heat source side unit (first unit) 1 and a load side unit (second unit) 2.
  • the heat source side unit 1 and the load side unit 2 are connected by refrigerant pipes 10c and 10d.
  • a main circuit in which the refrigerant circulates through the compressor 11 in the heat source side unit 1, the condenser 12, the decompression device 21 in the load side unit 2, and the evaporator 22 is formed.
  • one load-side unit 2 is provided, but the present invention is not limited to this, and for example, a plurality of load-side units 2 may be connected in parallel to the heat source-side unit 1. .. Further, when a plurality of load-side units 2 are provided, the capacities of the plurality of load-side units 2 may be the same or different.
  • the heat source side unit 1 includes a compressor unit 1a, a condenser unit 1b, and a control device 3.
  • the compressor unit 1a and the condenser unit 1b are connected by refrigerant pipes 10a and 10b.
  • the compressor unit 1a includes a compressor 11, a receiver 13, a supercooling heat exchanger 14, and a flow rate adjusting device 15.
  • the condenser unit 1b has a condenser 12 and a fan 12a.
  • the compressor 11 sucks in a low-temperature low-pressure refrigerant and compresses the sucked refrigerant into a high-temperature and high-pressure state.
  • the compressor 11 is a scroll compressor, and an injection port 11a is provided in an intermediate pressure portion of a compression chamber.
  • the bypass pipe 16 of the injection circuit 4 is connected to the injection port 11a.
  • the injection circuit 4 branches from the outlet side portion of the supercooled heat exchanger 14 in the main circuit (the portion between the condenser 12 and the decompression device 21 in the main circuit) and is connected to the injection port 11a of the compressor 11. Will be done.
  • one compressor 11 is provided, but the present invention is not limited to this, and for example, two or more compressors 11 are connected in parallel according to the load of the load side unit 2. You may.
  • the compressor 11 for example, an inverter compressor capable of controlling the capacity, which is the amount of refrigerant delivered per unit time, is used by changing the drive frequency.
  • a compressor inverter board (not shown) for changing the drive frequency is mounted on the heat source side unit 1, and the start / stop and drive frequency of the compressor 11 are controlled by the control device 3.
  • the condenser 12 is connected to the discharge side of the compressor 11 via the refrigerant pipe 10a.
  • the condenser 12 is configured to exchange heat between the refrigerant flowing through the main circuit and the fluid (water and air, refrigerant, brine, etc.) to condense the refrigerant.
  • the fan 12a is configured to blow air to the condenser 12.
  • the rotation speed of the fan 12a is controlled by the control device 3.
  • the receiver 13 is connected to the outlet side of the condenser 12 via the refrigerant pipe 10b.
  • the receiver 13 temporarily stores the refrigerant flowing out of the condenser 12, and separates the liquid refrigerant and the gas refrigerant.
  • the supercooled heat exchanger 14 is connected to the outlet side of the condenser 12 via the refrigerant pipe 10b and the receiver 13.
  • the supercooling heat exchanger 14 flows out of the condenser 12 by exchanging heat between the refrigerant flowing out of the condenser 12 and flowing through the main circuit and the refrigerant branching from the main circuit and flowing through the injection circuit 4. Then, the refrigerant flowing through the main circuit is supercooled.
  • the supercooled heat exchanger 14 does not have to be in the configuration of the refrigerant circuit.
  • the flow rate adjusting device 15 adjusts the flow rate of the refrigerant branched from the outlet side of the supercooling heat exchanger 14 to the injection circuit 4 based on the control of the control device 3.
  • the flow rate adjusting device 15 for example, an electronic expansion valve is used.
  • the heat source side unit 1 further includes a suction pressure sensor 41.
  • the suction pressure sensor 41 is provided on the suction side of the compressor 11, detects the pressure (suction pressure) of the refrigerant sucked into the compressor 11, and transmits the detection result to the control device 3.
  • the load side unit 2 is connected to the compressor unit 1a of the heat source side unit 1 by the refrigerant pipes 10c and 10d.
  • the load-side unit 2 has a decompression device 21 and an evaporator 22.
  • the decompression device 21 decompresses and expands the refrigerant supercooled by the supercooling heat exchanger 14, and adjusts the flow rate of the refrigerant.
  • the pressure reducing device 21 for example, an electronic expansion valve or a temperature expansion valve is used.
  • the evaporator 22 absorbs and evaporates the decompressed and expanded refrigerant in the decompression device 21 by exchanging heat between the refrigerant flowing in the main circuit and the fluid (water and air, refrigerant, brine, etc.). ..
  • a fin-and-tube heat exchanger having a heat transfer tube and a large number of fins is used.
  • the control device 3 includes a storage unit 3a, a calculation unit 3b, an input / output buffer (not shown) for inputting / outputting various signals, and the like.
  • the storage unit 3a stores a program in which the processing procedure of the control device 3 is described, an operation history of the refrigeration cycle device 100, and the like.
  • the calculation unit 3b is based on the suction pressure detected by the suction pressure sensor 41 and the information stored in the storage unit 3a, and the calculation unit 3b is a device (compressor 11, fan 12a, flow rate adjusting device 15) in the heat source side unit 1. ) Is executed. Further, the calculation unit 3b records information indicating the operating state of the refrigeration cycle device 100 in the storage unit 3a. The record of the operating state of the refrigerating cycle device 100 is stored in the storage unit 3a as the operating history of the refrigerating cycle device 100. These controls are not limited to software processing, but can also be processed by dedicated hardware (electronic circuits). The calculation unit 3b may control the decompression device 21 in the load side unit 2 in addition to each device in the heat source side unit 1.
  • a single refrigerant such as R22 and R134a a pseudo-azeotropic mixed refrigerant such as R410A and R404A, or a non-azeotropic mixed refrigerant such as R407C is used. You may.
  • a natural substance such as carbon dioxide and propane.
  • a refrigerant may be used.
  • the compressor 11 When the refrigeration cycle device 100 starts operation, the compressor 11 is first driven. Then, the high-temperature and high-pressure gas refrigerant compressed by the compressor 11 is discharged from the compressor 11 and flows into the condenser 12.
  • the condenser 12 the inflowing gas refrigerant is condensed by exchanging heat with a fluid such as air or water, and becomes a low-temperature and high-pressure liquid refrigerant.
  • the refrigerant flowing out of the condenser 12 and flowing through the main circuit exchanges heat with the refrigerant flowing through the injection circuit 4 branched from the main circuit at the supercooling heat exchanger 14.
  • the refrigerant flowing through the injection circuit 4 flows into the injection port 11a of the compressor 11.
  • the amount of refrigerant flowing from the injection circuit 4 to the injection port 11a of the compressor 11 is controlled by the flow rate adjusting device 15.
  • the start / stop of the compressor 11 is controlled based on the result of comparing the suction pressure detected by the suction pressure sensor 41 with the threshold pressure (starting pressure Pon and stopping pressure Pcut described later).
  • the threshold pressure is set by the calculation unit 3b of the control device 3 and stored in the storage unit 3a of the control device 3.
  • FIG. 2 is a flowchart showing an example of a processing procedure for starting / stopping control of the compressor 11 performed by the calculation unit 3b of the control device 3. This flowchart is repeatedly executed every time a predetermined condition is satisfied (for example, at regular intervals).
  • the calculation unit 3b determines whether or not the compressor 11 is operating (step S10). When the compressor 11 is operating (YES in step S10), the calculation unit 3b determines whether or not the suction pressure detected by the suction pressure sensor 41 is less than the stop pressure Pcut (step S12). When the suction pressure is not less than the stop pressure Pcut (NO in step S12), the calculation unit 3b shifts the process to the return while keeping the compressor 11 in the operating state. On the other hand, when the suction pressure is less than the stop pressure Pcut (YES in step S12), the calculation unit 3b stops the operation of the compressor 11 (step S14). After that, the calculation unit 3b shifts the processing to the return.
  • the calculation unit 3b determines whether or not the suction pressure detected by the suction pressure sensor 41 exceeds the starting pressure Pon (step S16). When the suction pressure does not exceed the starting pressure Pon (NO in step S16), the calculation unit 3b shifts the process to the return while keeping the compressor 11 in the stopped state. On the other hand, when the suction pressure exceeds the starting pressure Pon (YES in step S16), the calculation unit 3b starts the compressor 11 (step S18). After that, the calculation unit 3b shifts the processing to the return.
  • the calculation unit 3b of the control device 3 compares the suction pressure detected by the suction pressure sensor 41 with the threshold pressure (starting pressure Pon and stopping pressure Pcut described later), and the compressor is based on the result of comparison. It controls the start and stop (start and stop) of 11.
  • the calculation unit 3b starts and stops the compressor 11 by adjusting the above-mentioned threshold pressure (starting pressure Pon and stopping pressure Pcut) based on the operation history of the refrigerating cycle device 100 stored in the storage unit 3a. Reduce the number of times.
  • FIG. 3 is a flowchart showing an example of a processing procedure performed when the calculation unit 3b of the control device 3 adjusts the threshold pressure (starting pressure Pon and stopping pressure Pcut). This flowchart is repeatedly executed every time a predetermined condition is satisfied (for example, at regular intervals).
  • the calculation unit 3b estimates the behavior of the load-side unit 2 from the operation history of the refrigeration cycle device 100 stored in the storage unit 3a (step S20). For example, the calculation unit 3b has an operation state before the latest fixed time (for example, 24 hours) and an operation state within the latest fixed time in the operation history of the refrigeration cycle device 100 stored in the storage unit 3a. By comparing with, the behavior of the load side unit 2 is estimated.
  • the calculation unit 3b adjusts the threshold pressure (starting pressure Pon and stopping pressure Pcut) from the behavior of the load side unit 2 estimated in step S20 (step S22).
  • both the start pressure Pon and the stop pressure Pcut may be adjusted, or either one may be adjusted.
  • a defrost operation is performed using a heater or the like (not shown) in order to eliminate frost on the evaporator 22 of the load side unit 2.
  • the defrost operation is generally carried out periodically by the load side unit 2.
  • the calculation unit 3b estimates in step S20 whether or not the load side unit 2 is in the defrost operation based on the operation history of the refrigeration cycle device 100. Then, in step S22, the calculation unit 3b temporarily lowers the stop pressure Pcut when it is estimated that the load side unit 2 is in the defrost operation. This makes it difficult to stop the compressor 11 while the compressor 11 is in operation.
  • the suction pressure of the compressor 11 rises due to a slow leak from the valve stop of the heat source side unit 1 and the load side unit 2 after the compressor 11 is stopped, the suction pressure when the compressor 11 is stopped is still high. Since the time required for the suction pressure to rise to the starting pressure Pon can be delayed by a lower amount, it is possible to make it difficult to start the compressor 11. As a result, the number of times the compressor 11 is started and stopped can be appropriately reduced.
  • the suction pressure sensor 41 for detecting the suction pressure which is the pressure of the refrigerant sucked into the compressor 11 and the suction pressure detected by the suction pressure sensor 41 are used.
  • a control device 3 for starting and stopping the compressor 11 based on the result of comparison with the threshold pressure (starting pressure Pon and stopping pressure Pcut) is provided.
  • the control device 3 includes a storage unit 3a that stores the operation history of the refrigeration cycle device 100, and a calculation unit 3b that adjusts the threshold pressure (starting pressure Pon and stop pressure Pcut) based on the operation history of the refrigeration cycle device. ..
  • the threshold pressure (starting pressure Pon and stopping pressure Pcut) used for starting / stopping control of the compressor 11 is based on the operation history (past operating state) of the refrigerating cycle apparatus 100. By adjusting, the number of times the compressor is started and stopped can be suppressed. Therefore, the number of times of starting and stopping of the compressor 11 can be appropriately reduced without using the temperature information of the load side unit 2.
  • the threshold pressure is adjusted without using the temperature information of the load side unit 2. Therefore, in particular, as in the present embodiment, the evaporator 22 is provided in another load side unit 2 (second unit) different from the heat source side unit 1 (first unit), and the heat source side unit 1 is provided. Even if the control device 3 does not acquire the load temperature information from the load side unit 2 by communication, the number of times of starting and stopping of the compressor 11 can be appropriately reduced.
  • the threshold pressure may be adjusted by contact input using a relay or the like. Further, the threshold pressure may be adjusted according to the behavior information (information different from the load temperature) of the load side unit 2 acquired by communication with the load side unit 2.
  • FIG. 4 is a schematic view showing an example of the configuration of the refrigeration cycle apparatus 100A according to the second embodiment.
  • the refrigeration cycle device 100A includes a heat source side unit 1A and a load side unit 2.
  • the heat source side unit 1A includes a compressor unit 1Aa, a condenser unit 1b, and a control device 3.
  • the compressor unit 1Aa is obtained by changing the compressor 11 of the compressor unit 1a according to the first embodiment to the first compressor 11A and the second compressor 11B.
  • the other structure of the refrigeration cycle device 100A is the same as that of the refrigeration cycle device 100 according to the first embodiment described above.
  • the first compressor 11A and the second compressor 11B are connected in parallel to each other as shown in FIG. In this way, two compressors may be provided.
  • the number of compressors is not limited to two, and for example, three or more compressors may be connected in parallel depending on the load of the load side unit 2.
  • the control device 3 In the refrigeration cycle device 100A including two first compressors 11A and second compressors 11B connected in parallel to each other, the control device 3 generates the compressors 11A and 11B so that the integrated operation time is equal. Rotating the compressor subject to stop control (control shown in FIG. 2 above) is effective in extending the life of the compressor. However, if only the integrated operation time is rotated as a parameter, the integrated operation time of the compressors 11A and 11B can be made equal, but depending on the operation time and the operating environment, one of the compressors frequently starts and stops. It can fall into a repetitive state, with one compressor reaching its end of life earlier than the other.
  • the calculation unit 3b of the control device 3 implements rotation control incorporating the integrated operation time and the number of starts and stops of the compressors 11A and 11B.
  • FIG. 5 is a flowchart showing an example of a rotation control processing procedure carried out by the calculation unit 3b of the control device 3 according to the second embodiment. This flowchart is repeatedly executed every time a predetermined condition is satisfied (for example, at regular intervals).
  • the integrated operation time TA of the first compressor 11A and the integrated operation time TB of the second compressor 11B are measured by, for example, the calculation unit 3b and stored in the storage unit 3a. Further, the margin time X can be set in advance.
  • the start / stop count NA of the first compressor 11A and the start / stop count NB of the second compressor 11B are measured by, for example, the calculation unit 3b and stored in the storage unit 3a. Further, the number of margins Y can be set in advance.
  • step S54 when the number of start / stop times ⁇ NB within a certain period of time of the second compressor 11B does not exceed the reference number of times Z (NO in step S42), the calculation unit 3b secondly compresses the compressor subject to start / stop control. Machine 11B (step S54).
  • the calculation unit 3b sets the compressor to be controlled by the start / stop to the second compressor 11B (step S54).
  • the calculation unit 3b sets the compressor to be the start / stop control to the first compressor. It is set to 11A (step S44).
  • the life of the first compressor 11A and the second compressor 11B can be made uniform.
  • the target of start / stop control is set to the first compressor 11A.
  • the target of the start / stop control is set to the second compressor 11B on condition that the start / stop count ⁇ NB within a certain time of the second compressor 11B does not exceed the reference number Z. ..
  • the target of start / stop control is set to the second compressor 11B.
  • the target of the start / stop control is set to the first compressor 11A on the condition that the start / stop count ⁇ NA within a certain time of the first compressor 11A does not exceed the reference number Z.
  • the rotation control is performed based on the integrated operation time and the number of starts and stops of each of the first compressor 11A and the second compressor 11B. Therefore, the life of the first compressor 11A and the second compressor 11B can be appropriately made uniform as compared with the case where the rotation control is performed using only the integrated operation time as a parameter.
  • the processing procedure shown in FIG. 5 is merely an example, and is not limited to the procedure shown in FIG.
  • the number of starts and stops is determined after the integrated operation time of the compressor is determined, but the integrated operation time may be determined after the number of starts and stops is determined.
  • the priority of the integrated operation time and the number of starts and stops can be appropriately set according to the structure of the compressor.
  • the life of the compressor also affects the number of liquid backs and the operating frequency.
  • the number of liquid backs leads to damage to the compression mechanism due to liquid compression. If the operating frequency is high, the refrigerating machine oil that lubricates the sliding part of the compressor is taken out of the compressor, leading to damage due to poor lubrication. Therefore, the number of liquid backs and the operating frequency can also be used as parameters for whether or not rotation control is performed.
  • 1,1A heat source side unit 1a, 1Aa compressor unit, 1b condenser unit, 2 load side unit, 3 control device, 3a storage unit, 3b calculation unit, 4 injection circuit, 10a, 10b, 10c, 10d refrigerant piping, 11 compressor, 11A 1st compressor, 11B 2nd compressor, 11a injection port, 12 condenser, 12a fan, 13 receiver, 14 overcooling heat exchanger, 15 flow control device, 16 bypass piping, 21 decompression device, 22 Evaporator, 41 Suction pressure sensor, 100, 100A refrigeration cycle device.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
PCT/JP2020/020605 2020-05-25 2020-05-25 冷凍サイクル装置 Ceased WO2021240615A1 (ja)

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PCT/JP2020/020605 WO2021240615A1 (ja) 2020-05-25 2020-05-25 冷凍サイクル装置
JP2022527292A JP7309063B2 (ja) 2020-05-25 2020-05-25 冷凍サイクル装置

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CN116069077B (zh) * 2023-03-14 2025-09-02 杭州医学院 一种医用气体设备的运行压力调节方法及系统

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001066032A (ja) * 1999-08-30 2001-03-16 Fuji Electric Co Ltd 冷蔵ショーケースの冷却装置
JP2004301361A (ja) * 2003-03-28 2004-10-28 Nakano Refrigerators Co Ltd 冷凍・冷蔵設備の集中管理システム
JP2007107730A (ja) * 2005-10-11 2007-04-26 Sanden Corp 冷却システム
JP2009287800A (ja) * 2008-05-27 2009-12-10 Daikin Ind Ltd 冷凍装置
WO2016046991A1 (ja) * 2014-09-26 2016-03-31 三菱電機株式会社 空調冷凍複合設備

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001066032A (ja) * 1999-08-30 2001-03-16 Fuji Electric Co Ltd 冷蔵ショーケースの冷却装置
JP2004301361A (ja) * 2003-03-28 2004-10-28 Nakano Refrigerators Co Ltd 冷凍・冷蔵設備の集中管理システム
JP2007107730A (ja) * 2005-10-11 2007-04-26 Sanden Corp 冷却システム
JP2009287800A (ja) * 2008-05-27 2009-12-10 Daikin Ind Ltd 冷凍装置
WO2016046991A1 (ja) * 2014-09-26 2016-03-31 三菱電機株式会社 空調冷凍複合設備

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