EP3264008B1 - Tiefkühlvorrichtung - Google Patents

Tiefkühlvorrichtung Download PDF

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Publication number
EP3264008B1
EP3264008B1 EP15885373.9A EP15885373A EP3264008B1 EP 3264008 B1 EP3264008 B1 EP 3264008B1 EP 15885373 A EP15885373 A EP 15885373A EP 3264008 B1 EP3264008 B1 EP 3264008B1
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EP
European Patent Office
Prior art keywords
heat radiating
refrigerant
radiating unit
temperature
inverter
Prior art date
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Application number
EP15885373.9A
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English (en)
French (fr)
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EP3264008A1 (de
EP3264008A4 (de
Inventor
Takeshi Ito
Kazuyuki Tsukamoto
Masaaki Kamikawa
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP3264008A4 publication Critical patent/EP3264008A4/de
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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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser 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
    • F25B2700/21—Temperatures
    • F25B2700/2103—Temperatures near a heat exchanger
    • 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
    • F25B2700/21154—Temperatures of a compressor or the drive means therefor of an inverter

Definitions

  • the present invention relates to a refrigeration apparatus including an inverter heat radiating unit that cools an inverter device used for driving a compressor.
  • Patent Literature 1 discloses a refrigeration apparatus including a cooling refrigerant flow passage that branches off from a refrigerant circulation passage and communicates with a compressor body through an inverter.
  • Patent Literature 2 discloses a method in which a bypass cooling circuit for cooling an inverter heat radiating unit is provided within a refrigerant circuit and in which the amount of refrigerant that passes through the inverter heat radiating unit is controlled based on the temperature of the inverter heat radiating unit.
  • Document JP 2003 021406 A discloses a refrigeration apparatus comprising a refrigerant circuit in which a compressor configured to compress refrigerant, a condenser configured to cause the refrigerant discharged from the compressor to reject heat and cool, an economizer configured to subcool the refrigerant having flowed out of the condenser, an expansion device configured to reduce pressure of and expand the refrigerant subcooled in the economizer, an evaporator configured to cause the refrigerant reduced in pressure and expanded in the expansion device to receive heat and evaporate, are connected by a refrigerant pipe.
  • said refrigeration apparatus comprises an inverter device configured to drive the compressor and an inverter heat radiating unit configured to reject heat generated in the inverter device.
  • a possible method is to cool the inverter heat radiating unit by using refrigerant gas having passed through an economizer (subcooler).
  • the amount of refrigerant that passes through the economizer is controlled based on the temperature of the inverter heat radiating unit.
  • the economizer is not able to be used effectively, thereby resulting in a reduction in capacity in some cases.
  • the present invention has been made to overcome such drawbacks and provides a refrigeration apparatus that prevents condensation from occurring in an inverter device and also controls a reduction in capacity due to the fact that an economizer is prevented from being used effectively.
  • the opening degree of the flow rate regulation device is controlled based on the degree of superheat when the heat radiating unit temperature is within the target temperature range, and the opening degree of the flow rate regulation device is controlled based on the heat radiating unit temperature when the heat radiating unit temperature is outside the target temperature range. This can control a reduction in capacity due to insufficiency in effective use of the economizer and also prevent condensation from occurring during cooling the inverter device.
  • Fig. 1 is a refrigerant circuit diagram of a refrigeration apparatus according to Embodiment 1 of the present invention.
  • a refrigeration apparatus 1 includes a compressor 2, an oil separator 3, a condenser 4, an economizer 5, an expansion device 6, and an evaporator 7, and these are connected by a refrigerant pipe to constitute a refrigerant circuit 1A through which refrigerant circulates.
  • the compressor 2 is composed of a screw compressor, for example, and compresses and discharges refrigerant.
  • the compressor 2 includes a mechanism unit 2a including a compressor element and an electric-powered element that are housed in an airtight container.
  • the type of the compressor 2 is not limited to the screw compressor and may be a vane compressor, a rotary compressor, or a single-stage or multi-stage compressor, for example.
  • the compressor 2 is driven by an inverter device 20.
  • the oil separator 3 separates refrigerating machine oil contained in refrigerant discharged from the compressor 2, and the separated refrigerating machine oil returns to the compressor 2 again.
  • the condenser 4 is a heat exchanger that causes the refrigerant that has been discharged from the compressor 2 and from which oil has been separated in the oil separator 3 to reject heat and cool.
  • the economizer 5 is an inter-refrigerant heat exchanger that subcools the refrigerant having flowed out of the condenser 4.
  • the expansion device 6 is composed of an electronic expansion valve, for example, and reduces the pressure of and expands the refrigerant subcooled in the economizer 5.
  • the evaporator 7 is a heat exchanger that causes the refrigerant reduced in pressure and expanded in the expansion device 6 to receive heat and evaporate.
  • the refrigeration apparatus 1 also includes the inverter device 20 that drives the compressor 2, and an inverter heat radiating unit 12 that transfers heat generated in the inverter device 20.
  • the inverter device 20 and the inverter heat radiating unit 12 are integrally formed, and the inverter heat radiating unit 12 is provided so as to be integral with the compressor 2.
  • the inverter heat radiating unit 12 is formed on the outer surface of the airtight container of the mechanism unit 2a, and, on the inverter heat radiating unit 12, a heat-generating component, such as the inverter device 20, is placed together with a rectifier circuit and a smoothing capacitor.
  • the inverter heat radiating unit 12 is composed of a heat sink in which a flow passage is formed, for example, and cools the inverter device 20 by causing refrigerant to flow therethrough.
  • the refrigeration apparatus 1 includes an inverter cooling circuit 10 that causes refrigerant to flow through the above-described inverter heat radiating unit 12, and a flow rate regulation device 11 that is provided in the inverter cooling circuit 10 and regulates a flow rate of refrigerant that is to flow into the inverter heat radiating unit 12.
  • the inverter cooling circuit 10 includes a subcooling circuit 10A and a bypass cooling circuit 10B. In the subcooling circuit 10A, a refrigerant flow passage that branches off from between the economizer 5 and the expansion device 6, extends through the economizer 5 and the inverter heat radiating unit 12, and then extends into the compressor 2 is formed.
  • part of refrigerant flowing from the economizer 5 to the expansion device 6 is diverted and reduced in pressure by a first expansion valve 11A, and then flows into the inverter heat radiating unit 12.
  • the inverter heat radiating unit 12 is cooled, and refrigerant gas is supplied to an intermediate-pressure space in the compressor 2.
  • bypass cooling circuit 10B a refrigerant flow passage that branches off from between the economizer 5 and the expansion device 6, extends through the inverter heat radiating unit 12, and then extends into the compressor 2 is formed.
  • the bypass cooling circuit 10B diverts part of refrigerant flowing from the economizer 5 to the expansion device 6, reduces the pressure of the refrigerant by using a second expansion valve 11B, and then causes the refrigerant to flow into the inverter heat radiating unit 12.
  • the inverter heat radiating unit 12 is cooled by exchanging heat with the refrigerant, a flow of the refrigerant merges with a flow of the refrigerant gas having passed through the first expansion valve 11A, and refrigerant gas is supplied to the intermediate-pressure space in the compressor 2.
  • the inverter cooling circuit 10 includes the subcooling circuit 10A and the bypass cooling circuit 10B that cause refrigerant to flow through the inverter heat radiating unit 12. Then, in cooling the inverter heat radiating unit 12, refrigerant (for example, refrigerant gas at 20 to 30 degrees C) that is to flow to the intermediate-pressure space is used to cool the inverter heat radiating unit 12, thereby making it possible to prevent condensation from occurring on the inverter heat radiating unit 12. Furthermore, when the inverter heat radiating unit 12 is insufficiently cooled by the subcooling circuit 10A, the inverter cooling circuit 10 causes liquid refrigerant to flow through a bypass cooling circuit 10B side and can thus solve the insufficient cooling.
  • refrigerant for example, refrigerant gas at 20 to 30 degrees C
  • the flow rate regulation device 11 is provided in the inverter cooling circuit 10 and regulates a flow rate of refrigerant that is to flow through the inverter heat radiating unit 12.
  • the flow rate regulation device 11 includes the first expansion valve 11A provided on a subcooling circuit 10A side, and the second expansion valve 11 B and an valve 11C that are provided on the bypass cooling circuit 10B side.
  • the first expansion valve 11A is composed of an electronic expansion valve, for example, and is provided between a branch point between the economizer 5 and the expansion device 6, and the economizer 5.
  • a flow rate of refrigerant that is to flow from the economizer 5 to the inverter heat radiating unit 12 is controlled on the subcooling circuit 10A side.
  • the second expansion valve 11B is composed of an electronic expansion valve, for example, and is provided between a branch point between the economizer 5 and the expansion device 6, and the inverter heat radiating unit 12.
  • the second expansion valve 11B is provided between the branch point between the economizer 5 and the expansion device 6, and the valve 11C.
  • the second expansion valve 11B and the valve 11C constitute a bypass flow rate regulation device that controls a flow rate of refrigerant in the bypass cooling circuit 10B.
  • an electronic expansion valve capable of being fully closed may be used as the second expansion valve 11B, and the valve 11C may be omitted.
  • a flow rate of refrigerant that is to flow to the inverter heat radiating unit 12 is controlled on the bypass cooling circuit 10B side. Furthermore, when opening and closing of the valve 11C are controlled, the flow of refrigerant to the bypass cooling circuit 10B is controlled.
  • Refrigerant compressed in the compressor 2 is discharged from the compressor 2 and separated into refrigerant gas and oil in the oil separator 3, and the refrigerant gas flows into the condenser 4.
  • the refrigerant gas having flowed into the condenser 4 is condensed into liquid refrigerant and subcooled through heat exchange in the economizer 5.
  • the subcooled refrigerant is reduced in pressure in the expansion device 6 and then transferred to the evaporator 7.
  • the refrigerant transferred to the evaporator 7 exchanges heat with air, for example, to turn into refrigerant gas and flows into the compressor 2.
  • part of refrigerant flowing from the economizer 5 to the expansion device 6 is diverted to the inverter cooling circuit 10.
  • Refrigerant diverted to the subcooling circuit 10A side of the inverter cooling circuit 10 is reduced in pressure in the first expansion valve 11A and turns into refrigerant gas through heat exchange between refrigerant and refrigerant in the economizer 5.
  • the refrigerant cools the inverter device 20 in the inverter heat radiating unit 12 and then flows into the intermediate-pressure space in the compressor 2.
  • refrigerant diverted to the bypass cooling circuit 10B side of the inverter cooling circuit 10 passes through the second expansion valve 11B and the valve 11C and cools the inverter heat radiating unit 12.
  • a flow of the refrigerant merges with a flow of the refrigerant gas flowing through the subcooling circuit 10A, and the refrigerant is injected into the intermediate-pressure space in the compressor 2.
  • the refrigeration apparatus 1 includes a heat radiating unit temperature detection device 31, a state detection device (refrigerant temperature detection device 32a, intermediate-pressure detection device 32b), a suction temperature detection device 33, and a suction pressure detection device 34, for example.
  • the heat radiating unit temperature detection device 31 detects a temperature of the inverter heat radiating unit 12.
  • the refrigerant temperature detection device 32a and the intermediate-pressure detection device 32b function as a state detection device that detects the state of refrigerant flowing through the inverter cooling circuit 10.
  • the refrigerant temperature detection device 32a detects a temperature of refrigerant flowing through the economizer 5, that is, a temperature of refrigerant before flowing into the inverter heat radiating unit 12.
  • the intermediate-pressure detection device 32b detects a pressure of an intermediate-pressure chamber space in the middle of a compression process in the compressor 2.
  • the suction temperature detection device 33 detects a temperature of refrigerant gas to be sucked into the compressor 2.
  • the suction pressure detection device 34 detects a pressure of refrigerant gas to be sucked into the compressor 2. Detection values detected in these detection devices are output to the controller 40.
  • Fig. 2 is a functional block diagram illustrating an example of the controller in the refrigeration apparatus of Fig. 1 .
  • the controller 40 of Fig. 2 is constituted by hardware, such as a circuit device that implements functions thereof, or an arithmetic unit, such as a microprocessor or CPU, and software run thereon.
  • the controller 40 controls a flow rate of refrigerant that is to flow to the inverter cooling circuit 10 based on detection values detected in the heat radiating unit temperature detection device 31, the refrigerant temperature detection device 32a, and the intermediate-pressure detection device 32b, and includes a temperature determination unit 41, a superheat degree calculation unit 42, and an opening degree control unit 43.
  • the temperature determination unit 41 determines whether a heat radiating unit temperature Tr detected in the heat radiating unit temperature detection device 31 is within a target temperature range.
  • a lower limit Trl is set at 25 degrees C
  • an upper limit Tru is set at 40 degrees C.
  • the temperature determination unit 41 determines whether the heat radiating unit temperature Tr is within the target temperature range, above the upper limit Tru of the target temperature range, or below the lower limit Trl of the target temperature range.
  • the superheat degree calculation unit 42 calculates a degree of superheat SH of refrigerant gas flowing through the economizer 5 from a temperature detected by the refrigerant temperature detection device 32a and a pressure detected in the intermediate-pressure detection device 32b.
  • the opening degree control unit 43 controls the action of the flow rate regulation device 11 based on a determination result obtained in the temperature determination unit 41.
  • the opening degree control unit 43 controls an opening degree of the flow rate regulation device 11 so that the degree of superheat SH reaches a target degree of superheat.
  • the opening degree control unit 43 permits the flow of refrigerant on the subcooling circuit 10A side of the inverter cooling circuit 10 and puts the valve 11C on the bypass cooling circuit 10B side into a closed state to stop the flow of refrigerant into the bypass cooling circuit 10B.
  • the opening degree control unit 43 controls the opening degree of the first expansion valve 11A on the subcooling circuit 10A side so that the degree of superheat SH reaches the target degree of superheat.
  • the temperature determination unit 41 determines that the heat radiating unit temperature Tr is less than the lower limit Trl (for example, 25 degrees C) of the target temperature range, this determination means that cooling of the inverter heat radiating unit 12 is excessive.
  • the opening degree control unit 43 switches a control target from the degree of superheat SH to the heat radiating unit temperature Tr and controls the opening degree of the first expansion valve 11A so that the heat radiating unit temperature Tr reaches or exceeds the lower limit Trl of the target temperature range.
  • the opening degree control unit 43 determines that insufficient cooling of the inverter heat radiating unit 12 has occurred.
  • the opening degree control unit 43 switches the control target from the degree of superheat SH to the heat radiating unit temperature Tr and controls an opening degree of the flow rate regulation device 11 so that the heat radiating unit temperature Tr falls within the target temperature range.
  • the opening degree control unit 43 opens the valve 11C and causes refrigerant to flow through both the subcooling circuit 10A and the bypass cooling circuit 10B of the inverter cooling circuit 10.
  • the temperature determination unit 41 changes the initially-set upper limit Tru of the target temperature range to a second upper limit Trus (for example, 35 degrees C) lower than the upper limit Tru.
  • the opening degree control unit 43 performs control so that the opening degree of the second expansion valve 11B is increased until the heat radiating unit temperature Tr reaches or falls below the second upper limit Trus. Subsequently, even when the heat radiating unit temperature Tr reaches or falls below the second upper limit Trus, the opening degree control unit 43 performs control so that the opening degree of the second expansion valve 11B is maintained until the heat radiating unit temperature Tr falls below the lower limit Trl of the target temperature range. Subsequently, when the heat radiating unit temperature Tr falls below the lower limit Trl of the target temperature range, the opening degree control unit 43 reduces the opening degree of the second expansion valve 11B. Then, when the opening degree of the second expansion valve 11B reaches a minimum opening degree, the opening degree control unit 43 closes the valve 11C to stop the flow of refrigerant through the bypass cooling circuit 10B.
  • Fig. 3 is a flowchart illustrating an example of the action of the refrigeration apparatus of Fig. 1 . Processes illustrated in the flowchart of Fig. 3 are implemented at certain set control time intervals. First, based on a temperature detected by the refrigerant temperature detection device 32a and an intermediate pressure detected in the intermediate-pressure detection device 32b, a degree of superheat SH of refrigerant gas at a gas temperature detection area in the economizer 5 is calculated. The opening degree of the first expansion valve 11A is controlled so that the degree of superheat SH reaches a target degree of superheat (step ST11).
  • the temperature determination unit 41 determines whether a heat radiating unit temperature Tr of the inverter heat radiating unit 12 is less than or equal to an upper limit Tru of a target temperature range (step ST12). When the heat radiating unit temperature Tr is less than or equal to the upper limit Tru of the target temperature range, it is determined that an operation state is a steady operation state in which the temperature of the inverter device 20 is appropriate. When the heat radiating unit temperature Tr is above the upper limit Tru of the target temperature range, it is determined that the inverter device 20 is in a superheat operation state.
  • step ST12 When it is determined that an operation state is the steady operation state in which the heat radiating unit temperature Tr is less than or equal to the upper limit Tru of the target temperature range (YES in step ST12), the valve 11C is closed and the flow of refrigerant in the bypass cooling circuit 10B is stopped (step ST13). When the operation state has already been the steady operation state, the operation state is maintained. Subsequently, the controller 40 determines whether the heat radiating unit temperature Tr is greater than or equal to a lower limit Trl of the target temperature range (step ST14).
  • step ST14 When the heat radiating unit temperature Tr is greater than or equal to the lower limit Trl of the target temperature range (YES in step ST14), it is determined that the heat radiating unit temperature Tr is within the target temperature range and is in an appropriate state, and the operation state is maintained. On the other hand, when the heat radiating unit temperature Tr is less than the lower limit Trl of the target temperature range (NO in step ST14), it is determined that the inverter device 20 has been excessively cooled and condensation can occur. In this case, a control target of the first expansion valve 11A is changed from the degree of superheat SH to the heat radiating unit temperature Tr (step ST15).
  • control is performed so that the opening degree of the first expansion valve 11A is reduced until the heat radiating unit temperature Tr reaches or exceeds the lower limit Trl of the target temperature range (steps ST14 to ST16).
  • the control target is switched from the degree of superheat SH to the heat radiating unit temperature Tr, thereby enabling the inverter heat radiating unit 12 to be appropriately cooled so that it is not excessively cooled.
  • the control target is changed from the degree of superheat SH to the heat radiating unit temperature Tr. Furthermore, the upper limit Tru of the target temperature range is set to a second upper limit Trus (for example, 35 degrees C) less than the initially-set value thereof (step ST21). Then, the valve 11C is opened (step ST22), thereby resulting in the flow of refrigerant through both the subcooling circuit 10A and the bypass cooling circuit 10B. Then, control is performed so that the opening degree of the second expansion valve 11B is increased (step ST23).
  • step ST24 It is determined whether the heat radiating unit temperature Tr is less than or equal to the second upper limit Trus (step ST24), and the opening degree of the second expansion valve 11B is increased until the heat radiating unit temperature Tr reaches or falls below the second upper limit Trus (steps ST23 and ST24).
  • step ST24 when the heat radiating unit temperature Tr reaches or falls below the second upper limit Trus (YES in step ST24), it is determined whether the heat radiating unit temperature Tr is greater than or equal to the lower limit Trl of the target temperature range (step ST25). When it is determined that the heat radiating unit temperature Tr is less than the lower limit Trl of the target temperature range (NO in step ST25), the inverter heat radiating unit 12 has been excessively cooled, and the opening degree of the second expansion valve 11B is thus reduced (steps ST25 and ST29).
  • the opening degree of the second expansion valve 11B is maintained (step ST26). At this time, it is determined whether the opening degree of the second expansion valve 11B is a minimum opening degree (step ST27). When the opening degree of the second expansion valve 11B is not the minimum opening degree, the opening degree of the second expansion valve 11B is regulated as described above (step ST25 to step ST27).
  • step ST27 When the opening degree of the second expansion valve 11B reaches the minimum opening degree (YES in step ST27), it is determined that a state has been entered in which the heat radiating unit temperature Tr does not exceed the upper limit Tru of the target temperature range even when the valve 11C is closed so that refrigerant does not flow to the bypass cooling circuit 10B side, and the valve 11C is closed (step ST28).
  • the above-described processes of step ST21 to step ST29 are implemented at control time intervals.
  • the opening degree of the second expansion valve 11B is regulated in the superheat operation state is illustrated, not only the opening degree of the second expansion valve 11B but also an opening degree of the first expansion valve 11A may be regulated.
  • an opening degree of the flow rate regulation device 11 is controlled based on the degree of superheat SH, and, when the heat radiating unit temperature Tr is outside the target temperature range, an opening degree of the flow rate regulation device 11 is controlled based on the heat radiating unit temperature Tr.
  • This can control a reduction in capacity due to insufficiency in effective use of the economizer 5 and also prevent condensation from occurring during cooling the inverter device 20.
  • the use of refrigerant that is to flow to the intermediate-pressure space for cooling the inverter heat radiating unit 12 can prevent refrigerant having cooled the inverter device 20 from adversely affecting suction gas and enhance performance.
  • the inverter heat radiating unit 12 In the steady operation state, when the inverter heat radiating unit 12 is cooled by using refrigerant gas having passed through the economizer 5 that is to flow into the intermediate-pressure space, the difference in temperature between outdoor air and the inverter heat radiating unit 12 is reduced, thereby making it possible to prevent the occurrence of condensation.
  • the temperature of the inverter heat radiating unit 12 In the superheat operation state, when the temperature of the inverter heat radiating unit 12 is controlled to be close to the upper limit Tru of the target temperature range, the inverter heat radiating unit 12 is cooled without being subcooled, and the difference in temperature between outdoor air and the inverter heat radiating unit 12 is reduced, thereby making it possible to prevent the occurrence of condensation.
  • the inverter heat radiating unit 12 is further cooled by using liquid refrigerant on the bypass cooling circuit 10B side, thereby enabling the heat radiating unit temperature Tr to be less than or equal to the upper limit Tru of the target temperature range and be close to the upper limit Tru of the target temperature range.
  • excessive cooling of the inverter heat radiating unit 12 is prevented, and the difference in temperature between the inverter heat radiating unit 12 and outdoor air is reduced, thereby making it possible to prevent the occurrence of condensation.
  • control based on the degree of superheat SH is switched to control based on the heat radiating unit temperature Tr, thereby making it possible to avoid a state in which condensation is likely to occur.
  • the heat radiating unit temperature Tr can be reduced to a temperature within the target temperature range earlier in the superheat operation state.
  • Fig. 4 is a refrigerant circuit diagram illustrating a refrigeration apparatus according to Embodiment 2 of the present invention.
  • a refrigeration apparatus 100 will be described with reference to Fig. 4 .
  • components that have the same configurations as those in the refrigeration apparatus 1 of Fig. 1 are denoted by the same reference numerals, and description thereof is omitted.
  • the refrigeration apparatus 100 of Fig. 4 differs from the refrigeration apparatus 1 of Fig. 1 in the position where a refrigerant temperature detection device 132a is installed.
  • the refrigerant temperature detection device 132a is installed in a position where a temperature of refrigerant having flowed out of the inverter heat radiating unit 12 is detected.
  • the refrigerant temperature detection device 132a is provided in a position in front of the junction with the bypass cooling circuit 10B.
  • the superheat degree calculation unit 42 calculates a degree of superheat SH of refrigerant gas by using a refrigerant temperature detected by the refrigerant temperature detection device 132a.
  • the opening degree control unit 43 controls the first expansion valve 11A so that the degree of superheat SH reaches the target degree of superheat during steady operation.
  • Embodiment 2 as in Embodiment 1, a reduction in capacity due to insufficiency in effective use of the economizer 5 can be controlled, and condensation can also be prevented from occurring during cooling the inverter device 20. Furthermore, the first expansion valve 11A is controlled based on a temperature of refrigerant having cooled the inverter heat radiating unit 12, and an operable range in control during steady operation can thus be expanded further. Additionally, the amount of refrigerant injected in liquid form during superheat operation is reduced, and a reduction in performance in the superheat operation state can thus be suppressed.
  • Fig. 5 is a refrigerant circuit diagram illustrating a refrigeration apparatus according to Embodiment 3 of the present invention.
  • a refrigeration apparatus 200 will be described with reference to Fig. 5 .
  • components that have the same configurations as those in the refrigeration apparatus 1 of Fig. 1 are denoted by the same reference numerals, and description thereof is omitted.
  • the refrigeration apparatus 200 of Fig. 5 differs from the refrigeration apparatus 1 of Fig. 1 in the configuration of the inverter cooling circuit.
  • An inverter cooling circuit 210 of Fig. 5 is constituted by the subcooling circuit 10A without the bypass cooling circuit 10B.
  • the opening degree control unit 43 of the controller 40 controls the opening degree of the first expansion valve 11A serving as the flow rate regulation device 11.
  • Fig. 6 is a flowchart illustrating an example of the control of the refrigeration apparatus according to Embodiment 3 of the present invention. Processes illustrated in the flowchart of Fig. 6 are implemented at certain set control time intervals. In the flowchart of Fig. 6 , steps that are the same as those in the flowchart of Fig. 3 are denoted by the same reference numerals, and description thereof is omitted. In the steady operation state, the same control is performed except that step ST13 is not included. As control in the superheat operation state, steps ST31 to ST37 will be described below.
  • the control target of the first expansion valve 11A is changed from the degree of superheat SH to the heat radiating unit temperature Tr (step ST31).
  • the heat radiating unit temperature Tr is higher than the upper limit Tru of the target temperature range, and control is thus performed so that the opening degree of the first expansion valve 11A is increased (step ST32). Subsequently, it is determined whether the heat radiating unit temperature Tr is less than or equal to the upper limit Tru of the target temperature range (step ST33).
  • the inverter heat radiating unit 12 When it is determined that the heat radiating unit temperature Tr is above the upper limit Tru of the target temperature range (NO in step ST33), the inverter heat radiating unit 12 is in an insufficient cooling state, and control is thus performed so that the opening degree of the first expansion valve 11A is increased until the heat radiating unit temperature Tr reaches or falls below the upper limit Tru of the target temperature range (steps ST32 and ST33).
  • step ST34 it is determined whether the heat radiating unit temperature Tr is greater than or equal to the lower limit Trl of the target temperature range.
  • the inverter heat radiating unit 12 has been excessively cooled, and control is thus performed so that the opening degree of the first expansion valve 11A becomes smaller than the current opening degree (step ST37). Then, control is performed so that the opening degree of the first expansion valve 11A is reduced until the heat radiating unit temperature Tr reaches or exceeds the lower limit Trl of the target temperature range (steps ST34 and ST37).
  • step ST34 when the heat radiating unit temperature Tr is greater than or equal to the lower limit Trl of the target temperature range (YES in step ST34), it is determined whether the degree of superheat SH is greater than the target degree of superheat in the steady operation state to determine whether to perform control in the steady operation state (step ST35).
  • the degree of superheat SH is greater than the target degree of superheat (YES in step ST35)
  • the control target of the first expansion valve 11A is thus changed from the heat radiating unit temperature Tr to the degree of superheat SH in the steady operation state (step ST36).
  • step ST33 to ST35 when the degree of superheat SH is less than the control target degree of superheat, control based on the heat radiating unit temperature Tr is continued (steps ST33 to ST35).
  • Embodiment 3 as in Embodiment 1, in the superheat operation state, that is, in the case where the temperature of the inverter heat radiating unit 12 is above the upper limit Tru of the target temperature range, the control target of the first expansion valve 11A is changed, thereby enabling the temperature of the inverter heat radiating unit 12 to be less than or equal to the upper limit Tru of the target temperature range but be close to the upper limit Tru of the target temperature range.
  • the control target of the first expansion valve 11A is changed, thereby enabling the temperature of the inverter heat radiating unit 12 to be less than or equal to the upper limit Tru of the target temperature range but be close to the upper limit Tru of the target temperature range.
  • excessive cooling of the inverter heat radiating unit 12 is prevented, and the difference in temperature between the inverter heat radiating unit 12 and outdoor air can be reduced.
  • there is no cooling circuit using liquid injection thus enabling simplification of the refrigerant circuit and control.

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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)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Inverter Devices (AREA)

Claims (9)

  1. Kühlvorrichtung, welche aufweist:
    einen Kältemittelkreis (1A), in welchem ein Kompressor (2), der konfiguriert ist, ein Kältemittel zu verdichten, ein Kondensator (4), der konfiguriert ist, zu bewirken, dass von dem Kompressor (2) ausgegebenes Kältemittel Wärme und Kälte zurückweist, einen Economiser (5), der konfiguriert ist zum Unterkühlen des Kältemittels, das aus dem Kondensator (4) geströmt ist, eine Expansionsvorrichtung (6), die konfiguriert ist, den Druck des in dem Economiser (5) unterkühlten Kältemittels zu verringern und dieses zu expandieren, und einen Verdampfer (7), der konfiguriert ist, zu bewirken, dass das in der Expansionsvorrichtung (6) im Druck herabgesetzte und expandierte Kältemittel Wärme aufnimmt und verdampft, durch eine Kältemittelleitung verbunden sind;
    eine Wechselrichtervorrichtung (20), die konfiguriert ist, den Kompressor (2) anzutreiben;
    eine Wechselrichterwärme-Abstrahlungseinheit (12), die konfiguriert ist, in der Wechselrichtervorrichtung (20) erzeugte Wärme zurückzuweisen;
    einen Wechselrichter-Kühlkreis (10) enthaltend einen Unterkühlungskreis, in welchem ein Kältemittel-Strömungsdurchgang gebildet ist, der zwischen dem Economiser (5) und der Expansionsvorrichtung (6) abzweigt, sich durch den Economiser (5) und die Wechselrichter-Wärmeabstrahlungseinheit (12) erstreckt und dann in den Kompressor (2) erstreckt;
    eine Strömungsraten-Regelungsvorrichtung (11), die in dem Wechselrichter-Kühlkreis (10) angeordnet und konfiguriert ist, eine Strömungsrate von Kältemittel, das zur Strömung in die Wechselrichterwärme-Abstrahlungseinheit (12) bestimmt ist, zu regeln;
    eine Wechselrichtertemperatur-Erfassungsvorrichtung (31), die konfiguriert ist zum Erfassen einer Temperatur der Wechselrichterwärme-Abstrahlungseinheit (12) als eine Wärmeabstrahlungseinheiten-Temperatur;
    eine Zustandserfassungseinheit, die konfiguriert ist zum Erfassen eines Zustands von durch den Economiser (5) strömendem Kältemittel; und
    eine Steuervorrichtung (40), die konfiguriert ist zum Steuern der Tätigkeit der Strömungsraten-Regulierungsvorrichtung (11) auf der Grundlage der in der Wechselrichtertemperatur-Erfassungsvorrichtung (31) erfassten Wärmeabstrahlungseinheiten-Temperatur und des von der Zustandserfassungseinheit erfassten Zustands des durch den Economiser (5) strömenden Kältemittels,
    wobei die Steuervorrichtung (40) enthält:
    eine Temperaturbestimmungseinheit (41), die konfiguriert ist zum Bestimmen, ob die Wärmeabstrahlungseinheiten-Temperatur innerhalb eines Zieltemperaturbereichs ist,
    eine Überhitzungsgrad-Berechnungseinheit (42), die konfiguriert ist zum Berechnen eines Grads der Überhitzung von durch den Economiser (5) strömendem Kältemittel anhand des in der Zustandserfassungseinheit erfassten Zustands des Kältemittels, und
    eine Öffnungsgrad-Steuereinheit (43), die konfiguriert ist zum, wenn die Temperaturbestimmungseinheit (41) bestimmt, dass die Wärmeabstrahlungseinheiten-Temperatur innerhalb des Zieltemperaturbereichs ist, Steuern eines Öffnungsgrads der Strömungsraten-Regulierungsvorrichtung (11) derart, dass der in der Überhitzungsgrad-Berechnungseinheit (42) berechnete Überhitzungsgrad einen Zielüberhitzungsgrad erreicht, und konfiguriert ist zum, wenn die Temperaturbestimmungseinheit (41) bestimmt, dass die Wärmeabstrahlungseinheiten-Temperatur außerhalb des Zieltemperaturbereichs ist, Steuern des Öffnungsgrads der Strömungsraten-Regulierungsvorrichtung (11) derart, dass die Wärmeabstrahlungseinheiten-Temperatur in den Zieltemperaturbereich fällt.
  2. Kühlvorrichtung nach Anspruch 1, bei der die Zustandserfassungseinheit enthält: eine Zwischendruck-Erfassungsvorrichtung (32b), die konfiguriert ist zum Erfassen eines Zwischendrucks in dem Kompressor (2), und eine Kältemitteltemperatur-Erfassungsvorrichtung (32a), die konfiguriert ist zum Erfassen einer Temperatur von Kältemittel, das zur Strömung in die Wechselrichterwärme-Abstrahlungseinheit (12) bestimmt ist.
  3. Kühlvorrichtung nach Anspruch 1, bei der die Zustandserfassungseinheit enthält: eine Zwischendruck-Erfassungsvorrichtung (32b), die konfiguriert ist zum Erfassen eines Zwischendrucks in dem Kompressor (2), und eine Kältemitteltemperatur-Erfassungsvorrichtung (132a), die konfiguriert ist zum Erfassen einer Temperatur von Kältemittel, das aus der Wechselrichterwärme-Abstrahlungseinheit (12) geströmt ist.
  4. Kühlvorrichtung nach einem der Ansprüche 1 bis 3, bei der die Steuervorrichtung (40) konfiguriert ist zum Herabsetzen, wenn bestimmt wird, dass die Wärmeabstrahlungseinheiten-Temperatur niedriger als eine untere Grenze des Zieltemperaturbereichs ist, eines Öffnungsgrads der Strömungsraten-Regulierungsvorrichtung (11).
  5. Kühlvorrichtung nach einem der Ansprüche 1 bis 4, bei der, wenn bestimmt wird, dass die Wärmeabstrahlungseinheiten-Temperatur höher als eine obere Grenze des Zieltemperaturbereichs ist, die Öffnungsgrad-Steuereinheit (43) einen Öffnungsgrad der Strömungsraten-Regulierungsvorrichtung (11) erhöht.
  6. Kühlvorrichtung nach Anspruch 5, bei der, nachdem die Öffnungsgrad-Steuereinheit (43) den Öffnungsgrad der Strömungsraten-Regulierungsvorrichtung (11) erhöht hat, wenn die Wärmeabstrahlungseinheiten-Temperatur niedriger als die obere Grenze des Zieltemperaturbereichs ist und der Überhitzungsgrad größer als der Zielüberhitzungsgrad ist, die Öffnungsgrad-Steuereinheit (43) ein Steuerziel von der Wärmestrahlungseinheiten-Temperatur zu dem Überhitzungsgrad ändert.
  7. Kühlvorrichtung nach einem der Ansprüche 1 bis 5, bei der:
    der Wechselrichter-Kühlkreis (10) einen Umgehungskühlkreis (10b) enthält, der zwischen dem Economiser (5) und der Expansionsvorrichtung (6) abzweigt und durch die Wechselrichterwärme-Abstrahlungseinheit (12) mit dem Kompressor (2) verbunden ist,
    die Strömungsraten-Regulierungsvorrichtung (11) eine Umgehungsströmungsraten-Regulierungsvorrichtung enthält, die für den Umgehungskühlungskreis (10B) vorgesehen und konfiguriert ist, eine Strömungsrate von Kältemittel, das durch den Umgehungskühlungskreis (10B) strömt, zu regulieren, und
    die Öffnungsgrad-Steuereinheit (43) konfiguriert ist zum Durchführen, wenn die Wärmeabstrahlungseinheiten-Temperatur niedriger als eine oder gleich einer oberen Grenze des Zieltemperaturbereichs ist, einer Steuerung zum Versetzen der Umgehungsströmungsraten-Regulierungsvorrichtung in einen vollständig geschlossenen Zustand, und, wenn die Wärmeabstrahlungseinheiten-Temperatur höher als die obere Grenze des Zieltemperaturbereichs ist, die Öffnungsgrad-Steuereinheit (43) die Umgehungsströmungsraten-Regulierungsvorrichtung in einen offenen Zustand versetzt, um eine Strömungsrate zu regulieren.
  8. Kühlvorrichtung nach Anspruch 7, bei der, nachdem die Öffnungsgrad-Steuereinheit (43) die Umgehungsströmungsraten-Regulierungsvorrichtung in den offenen Zustand versetzt hat, um die Strömungsrate zu regulieren, wenn die Wärmeabstrahlungseinheiten-Temperatur niedriger als die untere Grenze des Zieltemperaturbereichs ist, die Öffnungsgrad-Steuereinheit (43) die Umgehungsströmungsraten-Regulierungsvorrichtung in einen geschlossenen Zustand versetzt.
  9. Kühlvorrichtung nach einem der Ansprüche 1 bis 8, bei der die Wechselrichtervorrichtung (20) und die Wechselrichterwärme-Abstrahlungseinheit (12) in einem Gehäuse des Kompressors (2) angeordnet sind.
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WO2018100711A1 (ja) * 2016-12-01 2018-06-07 三菱電機株式会社 冷凍装置
CN107356032A (zh) * 2017-08-10 2017-11-17 四川长虹电器股份有限公司 一种可以调整过热度的装置和方法
DE102018114786A1 (de) * 2018-06-20 2019-12-24 Stiebel Eltron Gmbh & Co. Kg Verfahren zum Betrieb einer Wärmepumpe und eine Kältemaschine
CN108775721B (zh) * 2018-07-27 2019-10-29 珠海格力电器股份有限公司 冷却系统及其控制方法
DE102019001632A1 (de) * 2019-03-08 2020-09-10 Stiebel Eltron Gmbh & Co. Kg Wärmepumpeneinrichtung, Heizungs- und/oder Warmwasserbereitungssystem und Verfaheren
CN112930075B (zh) * 2019-12-05 2022-08-12 株洲中车时代电气股份有限公司 变频器冷却系统、应用有变频器的设备和冷却控制方法
CN115800770A (zh) * 2022-11-09 2023-03-14 株洲中车时代电气股份有限公司 一种牵引变流器的水冷系统、方法、控制器及牵引系统

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EP3264008A4 (de) 2018-10-10

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