JP2017146068A - Refrigerating machine and its control method - Google Patents

Refrigerating machine and its control method Download PDF

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Publication number
JP2017146068A
JP2017146068A JP2016030060A JP2016030060A JP2017146068A JP 2017146068 A JP2017146068 A JP 2017146068A JP 2016030060 A JP2016030060 A JP 2016030060A JP 2016030060 A JP2016030060 A JP 2016030060A JP 2017146068 A JP2017146068 A JP 2017146068A
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Japan
Prior art keywords
refrigerant
condenser
expansion valve
liquid refrigerant
intermediate cooler
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JP2016030060A
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Japanese (ja)
Inventor
紀行 松倉
Noriyuki Matsukura
紀行 松倉
長谷川　泰士
Hiroshi Hasegawa
泰士 長谷川
潤 宮本
Jun Miyamoto
潤 宮本
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Priority to JP2016030060A priority Critical patent/JP2017146068A/en
Priority to CN201780005701.6A priority patent/CN108474598A/en
Priority to PCT/JP2017/003828 priority patent/WO2017141720A1/en
Priority to US16/065,918 priority patent/US20190017730A1/en
Publication of JP2017146068A publication Critical patent/JP2017146068A/en
Pending 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
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
    • 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
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • 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
    • F25B49/022—Compressor control arrangements
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/02—Details of evaporators
    • F25B2339/024—Evaporators with refrigerant in a vessel in which is situated a heat exchanger
    • F25B2339/0242—Evaporators with refrigerant in a vessel in which is situated a heat exchanger having tubular elements
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
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    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
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    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
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    • 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
    • F25B2400/12—Inflammable refrigerants
    • F25B2400/121—Inflammable refrigerants using R1234
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    • 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
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    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
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    • 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
    • F25B2600/02—Compressor control
    • F25B2600/022—Compressor control for multi-stage operation
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/026—Compressor control by controlling unloaders
    • F25B2600/0261—Compressor control by controlling unloaders external to the compressor
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/027—Compressor control by controlling pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass valves
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    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2515—Flow valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
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    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
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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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • 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
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    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21161—Temperatures of a condenser of the fluid heated by the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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    • 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
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    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
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    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
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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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a refrigerating machine capable of appropriately operating against the increase in refrigerant circulation amount that can occur when using a plate type heat exchanger as an inter-cooler.SOLUTION: A refrigerating machine comprises: a turbo compressor 2 for compressing refrigerant; a condenser 3 for condensing the refrigerant compressed by the turbo compressor 2; an inter-cooler 4 to be a plate type heat exchanger for heat exchange between the liquid refrigerant introduced from the condenser 3 and two-phase refrigerant in which a part of the liquid refrigerant introduced from the condenser 3 is expanded in a duplicate expansion valve 13; a main expansion valve 5 for expanding the liquid refrigerant introduced from the inter-cooler 4; and an evaporator 7 for evaporating the refrigerant introduced from the main expansion valve 5, in which with the plate type heat exchanger, the width of a plate is 100 mm or more and 400 mm or less; the height of the plate is 300 mm or more and 1000 mm or less; and the number of the laminated plates is 80 or more.SELECTED DRAWING: Figure 1

Description

本発明は、プレート式熱交換器とされた中間冷却器を備えた冷凍機およびその制御方法に関するものである。   The present invention relates to a refrigerator including an intercooler that is a plate heat exchanger and a control method thereof.

二段圧縮サブクーラ一段膨張サイクルは、例えば特許文献１に記載されているように中間冷却器がプレート式熱交換器のため、二段圧縮サブクーラ二段膨張サイクルで使用する気液分離型中間冷却器よりも冷媒充填量の削減ができる。   The two-stage compression subcooler one-stage expansion cycle is a gas-liquid separation type intercooler used in the two-stage compression subcooler two-stage expansion cycle because the intermediate cooler is a plate heat exchanger as described in Patent Document 1, for example. As a result, the refrigerant charging amount can be reduced.

特開２０１２−７７９７１号公報（［００３４］，図１）JP 2012-77971 A ([0034], FIG. 1)

しかし、冷却水温度が低く冷媒循環量が多い場合、膨張弁前後差圧（＝凝縮圧力−蒸発圧力−中間冷却器圧損）が小さくなり、膨張弁開度が大きくなりすぎて制御ができないといった問題がある。
この対策として、膨張弁口径を大きくすることが考えられる。しかし、最小開度変化での流量調整量が大きくなり、膨張弁制御の精度の低下という問題が生じる。
その他の対策として、中間冷却器の積層数を増やして全体の流路断面積を大きくして圧損を小さくすることが考えられる。しかし、積層数を増やして圧損を小さくしても、副膨張弁を経由した二相冷媒を各流路に分配する際の抵抗が小さくなり、冷媒分配の偏りが生じる。これでは、中間冷却器の伝熱面積を有効に使えず、冷凍機性能が低下してしまう。また、二相冷媒が十分にガス化されずに圧縮機の中間吸込口へ流れ込むキャリーオーバーが発生してしまう。 However, when the cooling water temperature is low and the refrigerant circulation rate is large, the differential pressure before and after the expansion valve (= condensation pressure−evaporation pressure−intermediate cooler pressure loss) becomes small and the expansion valve opening becomes too large to be controlled. There is.
As a countermeasure, it is conceivable to increase the expansion valve diameter. However, there is a problem that the flow rate adjustment amount with the minimum change in opening becomes large, and the accuracy of expansion valve control is lowered.
As another countermeasure, it is conceivable to increase the number of intermediate coolers to increase the overall flow path cross-sectional area and reduce the pressure loss. However, even if the number of stacks is increased to reduce the pressure loss, the resistance when distributing the two-phase refrigerant that has passed through the sub-expansion valve to each flow path is reduced, resulting in uneven distribution of the refrigerant. In this case, the heat transfer area of the intercooler cannot be used effectively, and the refrigerator performance is deteriorated. In addition, a carry-over occurs in which the two-phase refrigerant is not sufficiently gasified and flows into the intermediate suction port of the compressor.

本発明は、このような事情に鑑みてなされたものであって、プレート式熱交換器を中間冷却器に使用した場合に生じ得る冷媒循環量の増大に対して適正に運転を行うことができる冷凍機およびその制御方法を提供することを目的とする。   This invention is made | formed in view of such a situation, Comprising: When a plate-type heat exchanger is used for an intercooler, it can operate | move appropriately with respect to the increase in the refrigerant | coolant circulation amount which may arise. An object is to provide a refrigerator and a control method thereof.

上記課題を解決するために、本発明の冷凍機およびその制御方法は以下の手段を採用する。
すなわち、本発明にかかる冷凍機は、冷媒を圧縮する圧縮機と、該圧縮機により圧縮された冷媒を凝縮する凝縮器と、該凝縮器から導かれる液冷媒と該凝縮器から導かれる一部の液冷媒を副膨張弁で膨張させた二相冷媒とを熱交換させるプレート式熱交換器とされた中間冷却器と、該中間冷却器から導かれた液冷媒を膨張させる主膨張弁と、該主膨張弁から導かれた冷媒を蒸発させる蒸発器とを備え、前記プレート式熱交換器は、プレートの幅が１００ｍｍ以上４００ｍｍ以下、該プレートの高さが３００ｍｍ以上１０００ｍｍ以下、該プレートの積層枚数が８０枚以上とされていることを特徴とする。 In order to solve the above problems, the refrigerator and the control method thereof of the present invention employ the following means.
That is, the refrigerator according to the present invention includes a compressor that compresses a refrigerant, a condenser that condenses the refrigerant compressed by the compressor, a liquid refrigerant that is led from the condenser, and a part that is led from the condenser. An intermediate cooler that is a plate-type heat exchanger that exchanges heat with the two-phase refrigerant obtained by expanding the liquid refrigerant by the sub-expansion valve, and a main expansion valve that expands the liquid refrigerant led from the intermediate cooler, An evaporator for evaporating the refrigerant guided from the main expansion valve, wherein the plate heat exchanger has a plate width of 100 mm to 400 mm, a plate height of 300 mm to 1000 mm, and a stack of the plates The number of sheets is 80 or more.

中間冷却器としてプレート式熱交換器を用い、積層プレートの幅が１００ｍｍ以上４００ｍｍ以下、該積層プレートの高さが３００ｍｍ以上１０００ｍｍ以下、該積層プレートの積層枚数が８０枚以上とすることにより、中間冷却器の圧損を１００ｋＰａ以上、好ましくは１５０ｋＰａ以上２００ｋＰａ以下とすることができる。これにより、冷媒循環量が増大しても所定の圧損を確保できるので、プレート式熱交換器とされた中間冷却器内で冷媒分配が適正に行われ、冷凍機性能を損なわずに運転を行うことができる。
冷媒としては、ＨＦＣ−１３４ａが好適に用いられ、ＨＦＯ−１２３４ｚｅ（Ｅ）やＨＦＯ−１２３３ｚｄ（Ｅ）、ＨＦＯ−１２３３ｚｄ（Ｚ）を用いても良い。 By using a plate heat exchanger as the intermediate cooler, the width of the laminated plate is 100 mm or more and 400 mm or less, the height of the laminated plate is 300 mm or more and 1000 mm or less, and the number of laminated plates is 80 or more. The pressure loss of the cooler can be 100 kPa or more, preferably 150 kPa or more and 200 kPa or less. As a result, a predetermined pressure loss can be secured even if the refrigerant circulation amount increases, so that the refrigerant is properly distributed in the intermediate cooler that is a plate heat exchanger, and the operation is performed without impairing the performance of the refrigerator. be able to.
As the refrigerant, HFC-134a is preferably used, and HFO-1234ze (E), HFO-1233zd (E), or HFO-1233zd (Z) may be used.

また、本発明の冷凍機は、冷媒を圧縮する圧縮機と、該圧縮機により圧縮された冷媒を凝縮する凝縮器と、該凝縮器から導かれる液冷媒と該凝縮器から導かれる一部の液冷媒を副膨張弁で膨張させた二相冷媒とを熱交換させるプレート式熱交換器とされた中間冷却器と、該中間冷却器から導かれた液冷媒を膨張させる主膨張弁と、該主膨張弁から導かれた冷媒を蒸発させる蒸発器と、前記中間冷却器をバイパスして前記凝縮器からの液冷媒を前記主膨張弁の上流側に導くバイパス経路と、該バイパス経路に設けられたバイパス弁と、該バイパス弁の開度を制御する制御部とを備えていることを特徴とする。   The refrigerator of the present invention includes a compressor that compresses the refrigerant, a condenser that condenses the refrigerant compressed by the compressor, a liquid refrigerant led from the condenser, and a part of the refrigerant led from the condenser. An intermediate cooler configured as a plate heat exchanger for exchanging heat with the two-phase refrigerant obtained by expanding the liquid refrigerant with the sub-expansion valve; a main expansion valve for expanding the liquid refrigerant guided from the intermediate cooler; An evaporator configured to evaporate the refrigerant guided from the main expansion valve; a bypass path that bypasses the intermediate cooler and guides the liquid refrigerant from the condenser to the upstream side of the main expansion valve; and is provided in the bypass path. And a control unit for controlling the opening degree of the bypass valve.

制御部の指令によってバイパス弁を開き、バイパス経路を流れる冷媒流量を増大させることで、中間冷却器へ流れ込む液冷媒の流量を減少させることができる。これにより、冷媒循環量が大きくなった場合でも、中間冷却器に液冷媒が過剰に流れることを抑制できるので、プレート式熱交換器とされた中間冷却器での冷媒分配不良の発生を抑制することができる。   The flow rate of the liquid refrigerant flowing into the intermediate cooler can be decreased by opening the bypass valve according to the command from the control unit and increasing the flow rate of the refrigerant flowing through the bypass path. As a result, even when the refrigerant circulation amount becomes large, it is possible to suppress the liquid refrigerant from flowing excessively to the intermediate cooler, and thus it is possible to suppress the occurrence of refrigerant distribution failure in the intermediate cooler configured as a plate heat exchanger. be able to.

また、本発明の冷凍機は、冷媒を圧縮する圧縮機と、該圧縮機により圧縮された冷媒を凝縮する凝縮器と、該凝縮器から導かれる液冷媒と該凝縮器から導かれる一部の液冷媒を副膨張弁で膨張させた二相冷媒とを熱交換させるプレート式熱交換器とされた中間冷却器と、該中間冷却器から導かれた液冷媒を膨張させる主膨張弁と、該主膨張弁から導かれた冷媒を蒸発させる蒸発器と、前記中間冷却器をバイパスして前記凝縮器からの液冷媒を前記蒸発器の被冷却媒体入口側に導くバイパス経路と、該バイパス経路に設けられたバイパス弁と、該バイパス弁の開度を制御する制御部とを備えていることを特徴とする。   The refrigerator of the present invention includes a compressor that compresses the refrigerant, a condenser that condenses the refrigerant compressed by the compressor, a liquid refrigerant led from the condenser, and a part of the refrigerant led from the condenser. An intermediate cooler configured as a plate heat exchanger for exchanging heat with the two-phase refrigerant obtained by expanding the liquid refrigerant with the sub-expansion valve; a main expansion valve for expanding the liquid refrigerant guided from the intermediate cooler; An evaporator for evaporating the refrigerant led from the main expansion valve, a bypass path for bypassing the intermediate cooler and leading the liquid refrigerant from the condenser to the cooled medium inlet side of the evaporator, and the bypass path It is provided with the provided bypass valve and the control part which controls the opening degree of this bypass valve.

制御部の指令によってバイパス弁を開き、バイパス経路を流れる冷媒流量を増大させることで、中間冷却器へ流れ込む液冷媒の流量を減少させることができる。これにより、冷媒循環量が大きくなった場合でも、中間冷却器に液冷媒が過剰に流れることを抑制できるので、プレート式熱交換器とされた中間冷却器での冷媒分配不良の発生を抑制することができる。
また、主膨張弁もバイパスさせることができるので、冷媒循環量の増大を見込んで口径が大きな膨張弁を採用する必要もなく、膨張弁の制御精度の低下を招くおそれがない。
さらに、バイパス経路を経て液冷媒を蒸発器の被冷却媒体（例えば冷水）入口側に導くこととした。これにより、熱交換量が大きく冷媒が蒸発してドライアウトが生じ易い領域である被冷却媒体入口側に冷媒を導くことができるので、この領域でのドライアウトを抑制して蒸発器での熱伝達率の向上を図ることができる。 The flow rate of the liquid refrigerant flowing into the intermediate cooler can be decreased by opening the bypass valve according to the command from the control unit and increasing the flow rate of the refrigerant flowing through the bypass path. As a result, even when the refrigerant circulation amount becomes large, it is possible to suppress the liquid refrigerant from flowing excessively to the intermediate cooler, and thus it is possible to suppress the occurrence of refrigerant distribution failure in the intermediate cooler configured as a plate heat exchanger. be able to.
In addition, since the main expansion valve can also be bypassed, it is not necessary to employ an expansion valve having a large diameter in anticipation of an increase in the amount of refrigerant circulation, and there is no possibility of reducing the control accuracy of the expansion valve.
Furthermore, the liquid refrigerant is guided to the cooling medium (for example, cold water) inlet side of the evaporator through the bypass path. As a result, the refrigerant can be guided to the inlet side of the medium to be cooled, which is a region where the heat exchange amount is large and the refrigerant evaporates easily, so that the dryout in this region is suppressed and the heat in the evaporator is reduced. The transmission rate can be improved.

さらに、本発明の冷凍機では、前記制御部は、前記凝縮器内の圧力と前記蒸発器内の圧力との差が所定値以下になった場合、又は、前記主膨張弁の開度が所定値以上になった場合に、前記バイパス弁の開度を増大させることを特徴とする。   Further, in the refrigerator of the present invention, the control unit is configured such that the difference between the pressure in the condenser and the pressure in the evaporator becomes a predetermined value or less, or the opening of the main expansion valve is predetermined. When it becomes more than a value, the opening degree of the bypass valve is increased.

凝縮器内の圧力と蒸発器内の圧力との差が所定値以下になると、または、主膨張弁の開度が所定値以上になると、冷媒循環量が過剰になったと判断し、バイパス弁の開度を増大させる。これにより、プレート式熱交換器とされた中間冷却器での冷媒分配不良の発生を抑制することができる。   When the difference between the pressure in the condenser and the pressure in the evaporator becomes a predetermined value or less, or when the opening of the main expansion valve becomes a predetermined value or more, it is determined that the refrigerant circulation amount has become excessive, and the bypass valve Increase the opening. Thereby, generation | occurrence | production of the refrigerant | coolant distribution defect in the intermediate cooler made into the plate type heat exchanger can be suppressed.

また、本発明の冷凍機の制御方法は、冷媒を圧縮する圧縮機と、該圧縮機により圧縮された冷媒を凝縮する凝縮器と、該凝縮器から導かれる液冷媒と該凝縮器から導かれる一部の液冷媒を副膨張弁で膨張させた二相冷媒とを熱交換させるプレート式熱交換器とされた中間冷却器と、該中間冷却器から導かれた液冷媒を膨張させる主膨張弁と、該主膨張弁から導かれた冷媒を蒸発させる蒸発器と、前記中間冷却器をバイパスして前記凝縮器からの液冷媒を前記主膨張弁の上流側に導くバイパス経路と、該バイパス経路に設けられたバイパス弁とを備えた冷凍機の制御方法であって、前記凝縮器内の圧力と前記蒸発器内の圧力との差が所定値以下になった場合、又は、前記主膨張弁の開度が所定値以上になった場合に、前記バイパス弁の開度を増大することを特徴とする。   The refrigerator control method of the present invention includes a compressor that compresses a refrigerant, a condenser that condenses the refrigerant compressed by the compressor, a liquid refrigerant that is led from the condenser, and a condenser that is led from the condenser. An intermediate cooler that is a plate heat exchanger that exchanges heat with a two-phase refrigerant in which a part of the liquid refrigerant is expanded by the sub-expansion valve, and a main expansion valve that expands the liquid refrigerant guided from the intermediate cooler An evaporator for evaporating the refrigerant guided from the main expansion valve, a bypass path for bypassing the intermediate cooler and guiding the liquid refrigerant from the condenser to the upstream side of the main expansion valve, and the bypass path A control method for a refrigerator having a bypass valve provided in a case where a difference between the pressure in the condenser and the pressure in the evaporator becomes a predetermined value or less, or the main expansion valve When the opening of the valve exceeds a predetermined value, increase the opening of the bypass valve. Characterized in that it.

バイパス弁を開き、バイパス経路を流れる冷媒流量を増大させることで、中間冷却器へ流れ込む液冷媒の流量を減少させることができる。これにより、冷媒循環量が大きくなった場合でも、中間冷却器に液冷媒が過剰に流れることを抑制できるので、プレート式熱交換器とされた中間冷却器での冷媒分配不良の発生を抑制することができる。   The flow rate of the liquid refrigerant flowing into the intermediate cooler can be reduced by opening the bypass valve and increasing the flow rate of the refrigerant flowing through the bypass path. As a result, even when the refrigerant circulation amount becomes large, it is possible to suppress the liquid refrigerant from flowing excessively to the intermediate cooler, and thus it is possible to suppress the occurrence of refrigerant distribution failure in the intermediate cooler configured as a plate heat exchanger. be able to.

また、本発明の冷凍機の制御方法は、冷媒を圧縮する圧縮機と、該圧縮機により圧縮された冷媒を凝縮する凝縮器と、該凝縮器から導かれる液冷媒と該凝縮器から導かれる一部の液冷媒を副膨張弁で膨張させた二相冷媒とを熱交換させるプレート式熱交換器とされた中間冷却器と、該中間冷却器から導かれた液冷媒を膨張させる主膨張弁と、該主膨張弁から導かれた冷媒を蒸発させる蒸発器と、前記中間冷却器をバイパスして前記凝縮器からの液冷媒を前記蒸発器の被冷却媒体入口側に導くバイパス経路と、該バイパス経路に設けられたバイパス弁とを備えた冷凍機の制御方法であって、前記凝縮器内の圧力と前記蒸発器内の圧力との差が所定値以下になった場合、又は、前記主膨張弁の開度が所定値以上になった場合に、前記バイパス弁の開度を増大することを特徴とする。   The refrigerator control method of the present invention includes a compressor that compresses a refrigerant, a condenser that condenses the refrigerant compressed by the compressor, a liquid refrigerant that is led from the condenser, and a condenser that is led from the condenser. An intermediate cooler that is a plate heat exchanger that exchanges heat with a two-phase refrigerant in which a part of the liquid refrigerant is expanded by the sub-expansion valve, and a main expansion valve that expands the liquid refrigerant guided from the intermediate cooler An evaporator that evaporates the refrigerant guided from the main expansion valve, a bypass path that bypasses the intermediate cooler and guides the liquid refrigerant from the condenser to the cooled medium inlet side of the evaporator, A control method for a refrigerator having a bypass valve provided in a bypass path, wherein a difference between a pressure in the condenser and a pressure in the evaporator becomes a predetermined value or less, or When the opening of the expansion valve exceeds a predetermined value, the bypass valve Characterized by increasing the degree.

バイパス弁を開き、バイパス経路を流れる冷媒流量を増大させることで、中間冷却器へ流れ込む液冷媒の流量を減少させることができる。これにより、冷媒循環量が大きくなった場合でも、中間冷却器に液冷媒が過剰に流れることを抑制できるので、プレート式熱交換器とされた中間冷却器での冷媒分配不良の発生を抑制することができる。
また、主膨張弁もバイパスさせることができるので、冷媒循環量の増大を見込んで口径が大きな膨張弁を採用する必要もなく、膨張弁の制御精度の低下を招くおそれがない。
さらに、バイパス経路を経て液冷媒を蒸発器の被冷却媒体（例えば冷水）入口側に導くこととした。これにより、熱交換量が大きく冷媒が蒸発してドライアウトが生じ易い領域である被冷却媒体入口側に冷媒を導くことができるので、この領域でのドライアウトを抑制して蒸発器での熱伝達率の向上を図ることができる。 The flow rate of the liquid refrigerant flowing into the intermediate cooler can be reduced by opening the bypass valve and increasing the flow rate of the refrigerant flowing through the bypass path. As a result, even when the refrigerant circulation amount becomes large, it is possible to suppress the liquid refrigerant from flowing excessively to the intermediate cooler, and thus it is possible to suppress the occurrence of refrigerant distribution failure in the intermediate cooler configured as a plate heat exchanger. be able to.
In addition, since the main expansion valve can also be bypassed, it is not necessary to employ an expansion valve having a large diameter in anticipation of an increase in the amount of refrigerant circulation, and there is no possibility of reducing the control accuracy of the expansion valve.
Furthermore, the liquid refrigerant is guided to the cooling medium (for example, cold water) inlet side of the evaporator through the bypass path. As a result, the refrigerant can be guided to the inlet side of the medium to be cooled, which is a region where the heat exchange amount is large and the refrigerant evaporates easily, so that the dryout in this region is suppressed and the heat in the evaporator is reduced. The transmission rate can be improved.

積層プレートの幅、高さ及び積層数を適正に選定することにより、冷媒循環量が増大しても所定の圧損を確保できるので、プレート式熱交換器とされた中間冷却器内で冷媒分配が適正に行われ、冷凍機性能を損なわずに運転を行うことができる。
冷媒循環量が増大しても中間冷却器をバイパスするバイパス経路を流れる冷媒流量を増大させることで、中間冷却器へ流れ込む液冷媒の流量を減少させることができるので、プレート式熱交換器とされた中間冷却器での冷媒分配不良の発生を抑制することができる。 By properly selecting the width, height, and number of layers of the laminated plates, a predetermined pressure loss can be secured even if the amount of refrigerant circulation increases, so that the refrigerant distribution is performed in the intermediate cooler that is a plate heat exchanger. It is carried out properly and can be operated without impairing the performance of the refrigerator.
Even if the amount of refrigerant circulation increases, the flow rate of the liquid refrigerant flowing into the intermediate cooler can be reduced by increasing the flow rate of the refrigerant flowing through the bypass path that bypasses the intermediate cooler. Further, it is possible to suppress the occurrence of poor refrigerant distribution in the intermediate cooler.

本発明の第１実施形態に係るターボ冷凍機を示した概略構成図である。1 is a schematic configuration diagram illustrating a turbo refrigerator according to a first embodiment of the present invention. 図１の中間冷却器の概略構成を示した縦断面図である。It is the longitudinal cross-sectional view which showed schematic structure of the intercooler of FIG. 第１実施形態に係る中間冷却器のサーモグラフィの結果を示した図である。It is the figure which showed the result of the thermography of the intercooler which concerns on 1st Embodiment. 参考例に係る中間冷却器のサーモグラフィの結果を示した図である。It is the figure which showed the result of the thermography of the intercooler which concerns on a reference example. 本発明の第２実施形態に係るターボ冷凍機を示した概略構成図である。It is the schematic block diagram which showed the turbo refrigerator based on 2nd Embodiment of this invention. 本発明の第３実施形態に係るターボ冷凍機を示した概略構成図である。It is the schematic block diagram which showed the turbo refrigerator which concerns on 3rd Embodiment of this invention. 図６の蒸発器を概略的に示した縦断面図である。It is the longitudinal cross-sectional view which showed the evaporator of FIG. 6 schematically.

以下に、本発明にかかる実施形態について、図面を参照して説明する。
［第１実施形態］
以下、本発明の第１実施形態について説明する。
図１に示すように、ターボ冷凍機（冷凍機）１は、ターボ圧縮機（圧縮機）２と、凝縮器３と、中間冷却器４と、主膨張弁５と、蒸発器７と、制御部（図示せず）とを備えている。 Embodiments according to the present invention will be described below with reference to the drawings.
[First Embodiment]
The first embodiment of the present invention will be described below.
As shown in FIG. 1, a turbo refrigerator (refrigerator) 1 includes a turbo compressor (compressor) 2, a condenser 3, an intermediate cooler 4, a main expansion valve 5, an evaporator 7, and a control. Part (not shown).

ターボ圧縮機２は、インバータモータ９により駆動される遠心圧縮機であり、吸入口２Ａおよび吐出口２Ｂの他に、図示省略の第１羽根車と第２羽根車との間に設けられる中間吸入口２Ｃを備え、吸入口２Ａから吸い込んだ低圧ガス冷媒を第１羽根車および第２羽根車の回転により２段圧縮し、圧縮した高圧ガス冷媒を吐出口２Ｂから吐き出すように構成されている。
冷媒としては、ＨＦＣ−１３４ａが用いられる。ただし、ＨＦＯ−１２３４ｚｅ（Ｅ）やＨＦＯ−１２３３ｚｄ（Ｅ）、ＨＦＯ−１２３３ｚｄ（Ｚ）を用いても良い。 The turbo compressor 2 is a centrifugal compressor that is driven by an inverter motor 9, and in addition to the suction port 2A and the discharge port 2B, an intermediate suction provided between a first impeller and a second impeller (not shown). The low-pressure gas refrigerant sucked from the suction port 2A is compressed in two stages by the rotation of the first impeller and the second impeller, and the compressed high-pressure gas refrigerant is discharged from the discharge port 2B.
As the refrigerant, HFC-134a is used. However, HFO-1234ze (E), HFO-1233zd (E), or HFO-1233zd (Z) may be used.

ターボ圧縮機２の吐出口２Ｂから吐き出された高圧ガス冷媒は、油ミスト分離タンク１０へと導かれて、冷媒中の油分が遠心分離される。油分が遠心分離された高圧冷却ガスは、油ミスト分離タンク１０から凝縮器３へと導かれる。   The high-pressure gas refrigerant discharged from the discharge port 2B of the turbo compressor 2 is guided to the oil mist separation tank 10, and the oil content in the refrigerant is centrifuged. The high-pressure cooling gas from which the oil has been centrifuged is guided from the oil mist separation tank 10 to the condenser 3.

凝縮器３は、シェルアンドチューブ式熱交換器であり、ターボ圧縮機２から油ミスト分離タンク１０を経て供給される高圧ガス冷媒と冷却水回路１１を介して循環される冷却水とを熱交換させることにより、高圧冷却ガスを凝縮液化するものである。冷却水回路１１には、図示しない冷却塔が接続されており、この冷却塔にて冷却水が所定温度まで冷却される。なお、冷却水ポンプ１２によって供給される冷却水の流れと高圧ガス冷媒の流れとは、対向流となるようにすることが望ましい。なお、凝縮器３としてプレート式熱交換器を用いても良い。   The condenser 3 is a shell-and-tube heat exchanger, and exchanges heat between the high-pressure gas refrigerant supplied from the turbo compressor 2 via the oil mist separation tank 10 and the cooling water circulated through the cooling water circuit 11. By doing so, the high-pressure cooling gas is condensed and liquefied. A cooling tower (not shown) is connected to the cooling water circuit 11, and the cooling water is cooled to a predetermined temperature in this cooling tower. In addition, it is desirable that the flow of the cooling water supplied by the cooling water pump 12 and the flow of the high-pressure gas refrigerant are opposed to each other. Note that a plate heat exchanger may be used as the condenser 3.

中間冷却器４は、冷凍サイクル８の主回路中を流れて凝縮器３から導かれた液冷媒と、主回路から分流されて副膨張弁１３により減圧された二相冷媒とを熱交換させ、冷媒の蒸発潜熱により主回路中を流れる液冷媒を過冷却するプレート式熱交換器である。また、中間冷却器４には、液冷媒を過冷却することにより蒸発されたガス冷媒（中間圧冷媒）をターボ圧縮機２の中間吸入口２Ｃから中間圧の圧縮冷媒中に注入するためのガス回路１４が接続されている。   The intercooler 4 exchanges heat between the liquid refrigerant that flows in the main circuit of the refrigeration cycle 8 and is guided from the condenser 3, and the two-phase refrigerant that is diverted from the main circuit and decompressed by the sub-expansion valve 13, This is a plate heat exchanger that supercools the liquid refrigerant flowing in the main circuit by the latent heat of vaporization of the refrigerant. The intermediate cooler 4 also includes a gas for injecting gas refrigerant (intermediate pressure refrigerant) evaporated by supercooling the liquid refrigerant into the intermediate pressure compressed refrigerant from the intermediate suction port 2C of the turbo compressor 2. A circuit 14 is connected.

中間冷却器４を経て過冷却された冷媒は、主膨張弁５を通過することにより膨張して蒸発器７に供給される。蒸発器７は、シェルアンドチューブ式熱交換器であり、主膨張弁５から導かれた冷媒と冷水回路１５を介して循環される冷水（被冷却媒体）とを熱交換させることにより、冷媒を蒸発させ、その蒸発潜熱により冷水を冷却するものである。なお、冷水ポンプ１６によって供給される冷水の流れと冷媒の流れとは、対向流となるようにすることが望ましい。なお、蒸発器７としてプレート式熱交換器を用いても良い。   The refrigerant supercooled through the intermediate cooler 4 is expanded by passing through the main expansion valve 5 and supplied to the evaporator 7. The evaporator 7 is a shell-and-tube heat exchanger, and exchanges heat between the refrigerant guided from the main expansion valve 5 and cold water (cooled medium) circulated through the cold water circuit 15, thereby It evaporates, and cool water is cooled by the latent heat of evaporation. Note that it is desirable that the flow of the cold water supplied by the cold water pump 16 and the flow of the refrigerant be opposed to each other. A plate heat exchanger may be used as the evaporator 7.

また、冷凍サイクル８は、油ミスト分離タンク１０によって油分が分離された高圧ガス冷媒の一部を凝縮器３とターボ圧縮機２との間からバイパスするホットガスバイパス回路１７を備えている。このホットガスバイパス回路１７上には、ホットガスバイパス回路１７からターボ圧縮機２へと導かれる高圧ガス冷媒の流量を調整するホットガスバイパス弁１８が設けられている。   The refrigeration cycle 8 also includes a hot gas bypass circuit 17 that bypasses a part of the high-pressure gas refrigerant from which oil has been separated by the oil mist separation tank 10 from between the condenser 3 and the turbo compressor 2. On the hot gas bypass circuit 17, a hot gas bypass valve 18 that adjusts the flow rate of the high-pressure gas refrigerant guided from the hot gas bypass circuit 17 to the turbo compressor 2 is provided.

冷媒、冷却水および冷水の温度や圧力を測定する測定手段として、ターボ圧縮機２の吸入口２Ａ、吐出口２Ｂ、中間吸入口２Ｃには、圧力計４１、４２、４３および温度計３１、３２、３３が設けられ、冷却水回路１１の入口および出口、冷水回路１５の入口および出口には、各々温度計３５、３６、３７、３８が設けられ、主膨張弁５の入口には、温度計３４が設けられている。   As measuring means for measuring the temperature and pressure of refrigerant, cooling water and cold water, pressure gauges 41, 42, 43 and thermometers 31, 32 are provided at the suction port 2 A, the discharge port 2 B, and the intermediate suction port 2 C of the turbo compressor 2. 33 are provided at the inlet and outlet of the cooling water circuit 11 and at the inlet and outlet of the cooling water circuit 15 respectively, and thermometers are provided at the inlet of the main expansion valve 5 respectively. 34 is provided.

ターボ冷凍機１の制御は、図示しない制御部によって行われる。
制御部は、例えば、ＣＰＵ（Central Processing Unit）、ＲＡＭ（Random Access Memory）、ＲＯＭ（Read Only Memory）、及びコンピュータ読み取り可能な記憶媒体等から構成されている。そして、各種機能を実現するための一連の処理は、一例として、プログラムの形式で記憶媒体等に記憶されており、このプログラムをＣＰＵがＲＡＭ等に読み出して、情報の加工・演算処理を実行することにより、各種機能が実現される。なお、プログラムは、ＲＯＭやその他の記憶媒体に予めインストールしておく形態や、コンピュータ読み取り可能な記憶媒体に記憶された状態で提供される形態、有線又は無線による通信手段を介して配信される形態等が適用されてもよい。コンピュータ読み取り可能な記憶媒体とは、磁気ディスク、光磁気ディスク、ＣＤ−ＲＯＭ、ＤＶＤ−ＲＯＭ、半導体メモリ等である。 The turbo refrigerator 1 is controlled by a control unit (not shown).
The control unit includes, for example, a CPU (Central Processing Unit), a RAM (Random Access Memory), a ROM (Read Only Memory), and a computer-readable storage medium. A series of processes for realizing various functions is stored in a storage medium or the like in the form of a program as an example, and the CPU reads the program into a RAM or the like to execute information processing / arithmetic processing. As a result, various functions are realized. The program is preinstalled in a ROM or other storage medium, provided in a state stored in a computer-readable storage medium, or distributed via wired or wireless communication means. Etc. may be applied. The computer-readable storage medium is a magnetic disk, a magneto-optical disk, a CD-ROM, a DVD-ROM, a semiconductor memory, or the like.

図２には、中間冷却器４の概略構造が示されている。中間冷却器４は、積層プレート４０を複数枚重ねることによって並列に隣り合う複数の流路を形成したプレート式熱交換器となっている。なお、同図では、流路４２ａ，４２ｂが６つのみ示されているが、これはあくまでも例示であり、実際には８０以上の流路となる。
凝縮器３（図中に「ＣＯＮ」と表示）から導かれる液冷媒の流路４２ａと、凝縮器３から分岐されて副膨張弁１３を経た後に導かれる二相冷媒の流路４２ｂとは、交互に設けられており、また対向流となっている。 FIG. 2 shows a schematic structure of the intercooler 4. The intermediate cooler 4 is a plate heat exchanger in which a plurality of laminated plates 40 are stacked to form a plurality of adjacent flow paths. In the figure, only six flow paths 42a and 42b are shown, but this is merely an example, and actually 80 or more flow paths are provided.
The flow path 42a of the liquid refrigerant led from the condenser 3 (indicated by “CON” in the drawing) and the flow path 42b of the two-phase refrigerant led after branching from the condenser 3 and passing through the sub-expansion valve 13 are: It is provided alternately and is a counter flow.

凝縮器３からの液冷媒は、図において上方から下方へと流路４２ａ内を流れて中間冷却器４を通過する。中間冷却器４を通過した液冷媒は、主膨張弁５にて絞られた後に蒸発器７（図中に「ＥＶＡ」と表示）へと導かれる。   The liquid refrigerant from the condenser 3 flows through the intermediate cooler 4 through the flow path 42a from the upper side to the lower side in the figure. The liquid refrigerant that has passed through the intermediate cooler 4 is throttled by the main expansion valve 5 and then guided to the evaporator 7 (indicated as “EVA” in the drawing).

凝縮器３から分岐された一部の液冷媒は、副膨張弁１３にて絞られて二相冷媒とされた後に中間冷却器４の流路４２ｂ内へと流れ込み、図において下方から上方へと流れる。流路４２ｂの上流側には、所定の圧損を与えるディストリビュータ４４が設けられている。ディストリビュータ４４によって、各流路４２ｂに対して均等に二相冷媒を分配するようになっている。中間冷却器４を通過する間に二相冷媒からガス冷媒へと変化したガス冷媒は、ターボ圧縮機２（図中に「ＣＯＭＰ」と表示）の中間吸込口２Ｃへと流れる。
このように、凝縮器３から導かれて図において流路４２ａを上方から下方へ流れる液冷媒は、隣接する二相冷媒の蒸発潜熱によって冷却されて過冷却冷媒となり、副膨張弁１３から導かれて流路４２ｂを図において下方から上方へと流れる二相冷媒は、隣接する液冷媒から蒸発潜熱を得ることによってガス冷媒へと変化する。 A part of the liquid refrigerant branched from the condenser 3 is throttled by the sub-expansion valve 13 to become a two-phase refrigerant, and then flows into the flow path 42b of the intermediate cooler 4 from the lower side to the upper side in the figure. Flowing. A distributor 44 that provides a predetermined pressure loss is provided on the upstream side of the flow path 42b. The distributor 44 distributes the two-phase refrigerant equally to each flow path 42b. The gas refrigerant changed from the two-phase refrigerant to the gas refrigerant while passing through the intermediate cooler 4 flows to the intermediate suction port 2C of the turbo compressor 2 (indicated as “COMP” in the drawing).
Thus, the liquid refrigerant that is guided from the condenser 3 and flows from the upper side to the lower side in the flow path 42a in the drawing is cooled by the latent heat of vaporization of the adjacent two-phase refrigerant to become a supercooled refrigerant, and is led from the sub expansion valve 13. Thus, the two-phase refrigerant flowing from the lower side to the upper side in the drawing in the flow path 42b changes to a gas refrigerant by obtaining latent heat of evaporation from the adjacent liquid refrigerant.

積層プレート４０の幅は１００ｍｍ以上４００ｍｍ以下、積層プレート４０の高さは３００ｍｍ以上１０００ｍｍ以下、積層プレート４０の積層枚数が８０枚以上４００枚以下とされている。これにより、中間冷却器４の圧損を１００ｋＰａ以上、好ましくは１５０ｋＰａ以上２００ｋＰａ以下とすることができ、二相冷媒の流路４２ｂの冷媒分配不良を抑制することができる。
プレート式熱交換器とされた中間冷却器４の圧損は、積層プレート４０の積層数を増減することによって調整される。具体的には、積層枚数を増やすことによって合計の流路断面積を増やし流速を落として圧損を小さくし、積層枚数を減らすことによって合計の流路断面積を減らし流速を上げて圧損を大きくする。 The width of the laminated plate 40 is 100 mm to 400 mm, the height of the laminated plate 40 is 300 mm to 1000 mm, and the number of laminated plates 40 is 80 to 400. Thereby, the pressure loss of the intercooler 4 can be made 100 kPa or more, preferably 150 kPa or more and 200 kPa or less, and poor refrigerant distribution in the flow path 42b of the two-phase refrigerant can be suppressed.
The pressure loss of the intercooler 4 that is a plate heat exchanger is adjusted by increasing or decreasing the number of stacked layers of the stacked plates 40. Specifically, increasing the number of stacked layers increases the total channel cross-sectional area and decreases the flow velocity to reduce the pressure loss, and decreasing the number of stacked layers decreases the total channel cross-sectional area and increases the flow rate to increase the pressure loss. .

図３及び図４には、中間冷却器４における冷媒分配の状態が示されている。
図３は、本実施形態に係る中間冷却器４であり、積層枚数は８６枚とされている。冷媒はＨＦＣ−１３４ａを用いている。同図は、中間冷却器４を図２のように正面から見込んだ際のサーモグラフィの結果を示している。すなわち、図において左右方向が積層方向であり、下から上に向かって二相冷媒が流れ、上から下に向かって液冷媒が流れる。図３から、左右方向における温度差が大きくないことが分かる。これは、冷媒分配が良好であることを意味する。図３の場合、圧損は１００ｋＰａ以上となっていた。
一方、図４は、参考例であり、図３と同様のサーモグラフィの結果であるが、積層数が２１２枚という点で相違する。同図から、左右方向（積層方向）における温度差が大きく、冷媒分配が良好でないことが分かる。図４の場合、圧損は１０〜２０ｋＰａとなっていた。このように、冷媒循環量の増大に応じて積層数を増やすと、中間冷却器での圧損が小さくなり冷媒分配不良が生じることが分かる。 3 and 4 show the state of refrigerant distribution in the intercooler 4.
FIG. 3 shows the intercooler 4 according to this embodiment, in which the number of stacked layers is 86. As the refrigerant, HFC-134a is used. The figure shows the result of thermography when the intercooler 4 is viewed from the front as shown in FIG. That is, in the figure, the horizontal direction is the stacking direction, the two-phase refrigerant flows from the bottom to the top, and the liquid refrigerant flows from the top to the bottom. FIG. 3 shows that the temperature difference in the left-right direction is not large. This means that the refrigerant distribution is good. In the case of FIG. 3, the pressure loss was 100 kPa or more.
On the other hand, FIG. 4 is a reference example and is the result of thermography similar to FIG. 3, but is different in that the number of stacked layers is 212. From the figure, it can be seen that the temperature difference in the left-right direction (stacking direction) is large and the refrigerant distribution is not good. In the case of FIG. 4, the pressure loss was 10 to 20 kPa. In this way, it is understood that when the number of stacked layers is increased in accordance with the increase in the refrigerant circulation amount, the pressure loss in the intermediate cooler is reduced and refrigerant distribution failure occurs.

以上により、本実施形態によれば、以下の作用効果を奏する。
中間冷却器４としてプレート式熱交換器を用い、積層プレート４０の幅が１００ｍｍ以上４００ｍｍ以下、積層プレート４０の高さが３００ｍｍ以上１０００ｍｍ以下、積層プレート４０の積層枚数が８０枚以上とすることにより、中間冷却器４の圧損を１００ｋＰａ以上、好ましくは１５０ｋＰａ以上２００ｋＰａ以下とすることができる。これにより、冷媒循環量が増大しても所定の圧損を確保できるので、プレート式熱交換器とされた中間冷却器４内で冷媒分配が適正に行われ、冷凍機性能を損なわずに運転を行うことができる。 As mentioned above, according to this embodiment, there exist the following effects.
By using a plate heat exchanger as the intermediate cooler 4, the width of the laminated plate 40 is 100 mm to 400 mm, the height of the laminated plate 40 is 300 mm to 1000 mm, and the number of laminated plates 40 is 80 or more. The pressure loss of the intercooler 4 can be 100 kPa or more, preferably 150 kPa or more and 200 kPa or less. As a result, a predetermined pressure loss can be ensured even if the refrigerant circulation amount increases, so that the refrigerant is properly distributed in the intermediate cooler 4 that is a plate heat exchanger, and the operation is performed without impairing the performance of the refrigerator. It can be carried out.

［第２実施形態］
次に、本発明の第２実施形態について、図５を用いて説明する。
本実施形態は、第１実施形態に対してバイパス経路を備えている点で相違し、その他については同様である。したがって、同一構成については同一符号を付し、その説明を省略する。 [Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIG.
This embodiment is different from the first embodiment in that a bypass path is provided, and the rest is the same. Accordingly, the same components are denoted by the same reference numerals and description thereof is omitted.

図５に示されているように、中間冷却器４をバイパスして凝縮器３からの液冷媒を主膨張弁５の上流側に導くバイパス経路５０が設けられている。バイパス経路５０の上流端は、副膨張弁１３へと分岐する分岐点Ａよりも下流側に設けられている。
また、バイパス経路５０には、バイパス弁５２が設けられている。バイパス弁５２としては、開度調整が可能な電動ボール弁が用いられる。ただし、単なる開閉を行う電磁弁としても良い。バイパス弁５２の開度指令は、図示しない制御部によって行われる。制御部は、凝縮器３内の圧力と蒸発器７内の圧力との差が所定値以下になった場合、又は、主膨張弁５の開度が所定値以上になった場合、冷媒循環量が過剰になったと判断し、バイパス弁５２の開度を増大させる。 As shown in FIG. 5, a bypass path 50 that bypasses the intercooler 4 and guides the liquid refrigerant from the condenser 3 to the upstream side of the main expansion valve 5 is provided. The upstream end of the bypass path 50 is provided downstream of the branch point A that branches to the sub expansion valve 13.
Further, a bypass valve 52 is provided in the bypass path 50. As the bypass valve 52, an electric ball valve capable of adjusting the opening is used. However, it may be a solenoid valve that simply opens and closes. A command for opening the bypass valve 52 is issued by a control unit (not shown). When the difference between the pressure in the condenser 3 and the pressure in the evaporator 7 becomes a predetermined value or less, or when the opening of the main expansion valve 5 becomes a predetermined value or more, the control unit Is increased and the opening degree of the bypass valve 52 is increased.

このように、本実施形態によれば、制御部の指令によってバイパス弁５２を開き、バイパス経路５０を流れる冷媒流量を増大させることで、中間冷却器４へ流れ込む液冷媒の流量を減少させることができる。これにより、冷媒循環量が大きくなった場合でも、中間冷却器４に液冷媒が過剰に流れることを抑制できるので、プレート式熱交換器とされた中間冷却器４での冷媒分配不良の発生を抑制することができる。
なお、中間冷却器４としては、第１実施形態で示した構成のプレート式熱交換器を用いずに、バイパス経路５０に液冷媒をバイパスさせた際に中間冷却器４に流れ込む冷媒流量に対して所望の冷媒分配が行われるように圧損が調整された中間冷却器でもよい。 As described above, according to the present embodiment, the flow rate of the liquid refrigerant flowing into the intercooler 4 can be decreased by opening the bypass valve 52 according to the command from the control unit and increasing the flow rate of the refrigerant flowing through the bypass path 50. it can. Thereby, even when the refrigerant circulation amount becomes large, it is possible to prevent the liquid refrigerant from flowing excessively to the intermediate cooler 4, so that the refrigerant distribution failure in the intermediate cooler 4 that is a plate heat exchanger is prevented. Can be suppressed.
The intermediate cooler 4 does not use the plate-type heat exchanger having the configuration shown in the first embodiment, but with respect to the refrigerant flow rate that flows into the intermediate cooler 4 when liquid refrigerant is bypassed in the bypass path 50. An intermediate cooler in which the pressure loss is adjusted so that desired refrigerant distribution is performed may be used.

［第３実施形態］
次に、本発明の第３実施形態について、図６及び図７を用いて説明する。
本実施形態は、第１実施形態に対してバイパス経路を備えている点で相違し、その他については同様である。したがって、同一構成については同一符号を付し、その説明を省略する。 [Third Embodiment]
Next, a third embodiment of the present invention will be described with reference to FIGS.
This embodiment is different from the first embodiment in that a bypass path is provided, and the rest is the same. Accordingly, the same components are denoted by the same reference numerals and description thereof is omitted.

図６に示されているように、中間冷却器４をバイパスして凝縮器３からの液冷媒を蒸発器７の冷水（被冷却媒体）入口側に導くバイパス経路６０が設けられている。バイパス経路６０の上流端は、副膨張弁１３へと分岐する分岐点Ａよりも下流側に設けられている。
また、バイパス経路６０には、バイパス弁６２が設けられている。バイパス弁６２としては、開度調整が可能な電動ボール弁が用いられる。ただし、単なる開閉を行う電磁弁としても良い。バイパス弁６２の開度指令は、図示しない制御部によって行われる。制御部は、凝縮器３内の圧力と蒸発器７内の圧力との差が所定値以下になった場合、又は、主膨張弁５の開度が所定値以上になった場合、冷媒循環量が過剰になったと判断し、バイパス弁６２の開度を増大させる。 As shown in FIG. 6, a bypass path 60 is provided that bypasses the intermediate cooler 4 and guides the liquid refrigerant from the condenser 3 to the cold water (cooled medium) inlet side of the evaporator 7. The upstream end of the bypass path 60 is provided downstream of the branch point A that branches to the sub expansion valve 13.
The bypass path 60 is provided with a bypass valve 62. As the bypass valve 62, an electric ball valve capable of adjusting the opening is used. However, it may be a solenoid valve that simply opens and closes. The opening degree command of the bypass valve 62 is performed by a control unit (not shown). When the difference between the pressure in the condenser 3 and the pressure in the evaporator 7 becomes a predetermined value or less, or when the opening of the main expansion valve 5 becomes a predetermined value or more, the control unit Is increased and the opening of the bypass valve 62 is increased.

図７には、蒸発器７の概略構成が示されている。蒸発器７は、シェルアンドチューブ式とされており、横断面が略円形とされた水平方向軸線を有する円筒形状の容器とされている。蒸発器７の両側部には冷水が導かれる水室が設けられており、各水室４５，４６の間に挟まれた空間が中間冷却器４から導かれた冷媒が存在する蒸発室４７となっている。各水室４５，４６と蒸発室４７との間は、管板４８にて仕切られている。   FIG. 7 shows a schematic configuration of the evaporator 7. The evaporator 7 is of a shell and tube type, and is a cylindrical container having a horizontal axis whose cross section is substantially circular. Water chambers through which cold water is guided are provided on both sides of the evaporator 7, and a space sandwiched between the water chambers 45 and 46 is an evaporation chamber 47 in which refrigerant guided from the intermediate cooler 4 exists. It has become. The water chambers 45 and 46 and the evaporation chamber 47 are partitioned by a tube plate 48.

各水室４５，４６間には多数の伝熱管４９が接続されている。これら伝熱管４９は、図示しないが複数の管群を構成している。伝熱管４９の下方には、蒸発器７内に流入した二相冷媒を分配するための例えば多孔板とされた液分配構造６８が設けられている。
一方の水室４５から入った冷水は、各伝熱管４９を通り他方の水室４６にて折り返した後に、再び水室４５へと戻り、外部負荷へと導かれる。したがって、この場合、一方の水室４５は、冷水入口と冷水出口の部屋が仕切られていることになる。 A large number of heat transfer tubes 49 are connected between the water chambers 45 and 46. Although not shown, these heat transfer tubes 49 constitute a plurality of tube groups. Below the heat transfer tube 49, a liquid distribution structure 68, for example, a perforated plate for distributing the two-phase refrigerant flowing into the evaporator 7 is provided.
The cold water that has entered from one water chamber 45 passes through each heat transfer tube 49, is turned back in the other water chamber 46, returns to the water chamber 45 again, and is led to an external load. Therefore, in this case, one water chamber 45 is partitioned into a cold water inlet and a cold water outlet.

蒸発器７の下方には、水平方向軸線の略中央位置に、中間冷却器４から主膨張弁５を経て導かれた冷媒を導入する冷媒配管５３が接続されている。蒸発器７の上部には、蒸発器７内で蒸発した冷媒ガスをターボ圧縮機２の吸込口２Ａへと導く吸込配管６４が接続されている。吸込配管６４が接続された位置の上流側近傍には、例えば多孔板とされた気液を分離するための気液分離構造６６が設けられている。蒸発器７の上方の端部には、ホットガスバイパス管６５が接続されている。
そして、バイパス経路６０は、蒸発器７の水平軸線方向の中央位置よりも冷水入口側（図において左側）に接続されている。これにより、バイパス弁６２を経た冷媒は、蒸発器７の冷水入口側の冷水を流す伝熱管４９の近傍に導かれることになる。 Below the evaporator 7, a refrigerant pipe 53 that introduces the refrigerant guided from the intermediate cooler 4 through the main expansion valve 5 is connected to a substantially central position of the horizontal axis. A suction pipe 64 that guides the refrigerant gas evaporated in the evaporator 7 to the suction port 2 </ b> A of the turbo compressor 2 is connected to the upper part of the evaporator 7. In the vicinity of the upstream side of the position where the suction pipe 64 is connected, for example, a gas-liquid separation structure 66 for separating gas-liquid formed as a perforated plate is provided. A hot gas bypass pipe 65 is connected to the upper end of the evaporator 7.
The bypass path 60 is connected to the cold water inlet side (left side in the drawing) from the central position of the evaporator 7 in the horizontal axis direction. As a result, the refrigerant having passed through the bypass valve 62 is guided to the vicinity of the heat transfer tube 49 through which the cold water on the cold water inlet side of the evaporator 7 flows.

このように、本実施形態によれば、制御部の指令によってバイパス弁６２を開き、バイパス経路６０を流れる冷媒流量を増大させることで、中間冷却器４へ流れ込む液冷媒の流量を減少させることができる。これにより、冷媒循環量が大きくなった場合でも、中間冷却器４に液冷媒が過剰に流れることを抑制できるので、プレート式熱交換器とされた中間冷却器４での冷媒分配不良の発生を抑制することができる。
また、主膨張弁５もバイパスさせることができるので、冷媒循環量の増大を見込んで口径が大きな膨張弁を採用する必要もなく、膨張弁の制御精度の低下を招くおそれがない。
さらに、バイパス経路６０を経て冷媒を蒸発器７の冷水入口側に導くこととしたので、熱交換量が大きく冷媒が蒸発してドライアウトが生じ易い領域である冷水入口側に冷媒を導くことができ、この領域でのドライアウトを抑制して蒸発器での熱伝達率の向上を図ることができる。 As described above, according to the present embodiment, the flow rate of the liquid refrigerant flowing into the intercooler 4 can be reduced by opening the bypass valve 62 according to a command from the control unit and increasing the flow rate of the refrigerant flowing through the bypass path 60. it can. Thereby, even when the refrigerant circulation amount becomes large, it is possible to prevent the liquid refrigerant from flowing excessively to the intermediate cooler 4, so that the refrigerant distribution failure in the intermediate cooler 4 that is a plate heat exchanger is prevented. Can be suppressed.
Further, since the main expansion valve 5 can also be bypassed, it is not necessary to employ an expansion valve having a large diameter in anticipation of an increase in the amount of refrigerant circulation, and there is no possibility of causing a decrease in the control accuracy of the expansion valve.
Furthermore, since the refrigerant is guided to the cold water inlet side of the evaporator 7 via the bypass path 60, the refrigerant can be guided to the cold water inlet side, which is a region where the heat exchange amount is large and the refrigerant is liable to evaporate. It is possible to suppress the dryout in this region and improve the heat transfer coefficient in the evaporator.

なお、中間冷却器４としては、第１実施形態で示した構成のプレート式熱交換器を用いずに、バイパス経路６０に液冷媒をバイパスさせた際に中間冷却器４に流れ込む冷媒流量に対して所望の冷媒分配が行われるように圧損が調整された中間冷却器でもよい。   Note that the intermediate cooler 4 does not use the plate heat exchanger having the configuration shown in the first embodiment, but with respect to the refrigerant flow rate that flows into the intermediate cooler 4 when the liquid refrigerant is bypassed in the bypass path 60. An intermediate cooler in which the pressure loss is adjusted so that desired refrigerant distribution is performed may be used.

１ ターボ冷凍機（冷凍機）
２ ターボ圧縮機（圧縮機）
２Ａ 吸入口
２Ｂ 吐出口
２Ｃ 中間吸込口
３ 凝縮器
４ 中間冷却器
５ 主膨張弁
７ 蒸発器
１３ 副膨張弁
４０ 積層プレート
５０，６０ バイパス経路
５２，６２ バイパス弁 1 Turbo refrigerator (refrigerator)
2 Turbo compressor (compressor)
2A Suction port 2B Discharge port 2C Intermediate suction port 3 Condenser 4 Intermediate cooler 5 Main expansion valve 7 Evaporator 13 Sub expansion valve 40 Laminated plate 50, 60 Bypass path 52, 62 Bypass valve

Claims (6)

冷媒を圧縮する圧縮機と、
該圧縮機により圧縮された冷媒を凝縮する凝縮器と、
該凝縮器から導かれる液冷媒と該凝縮器から導かれる一部の液冷媒を副膨張弁で膨張させた二相冷媒とを熱交換させるプレート式熱交換器とされた中間冷却器と、
該中間冷却器から導かれた液冷媒を膨張させる主膨張弁と、
該主膨張弁から導かれた冷媒を蒸発させる蒸発器と、
を備え、
前記プレート式熱交換器は、プレートの幅が１００ｍｍ以上４００ｍｍ以下、該プレートの高さが３００ｍｍ以上１０００ｍｍ以下、該プレートの積層枚数が８０枚以上とされていることを特徴とする冷凍機。 A compressor for compressing the refrigerant;
A condenser for condensing the refrigerant compressed by the compressor;
An intermediate cooler configured as a plate heat exchanger for exchanging heat between the liquid refrigerant led from the condenser and a two-phase refrigerant obtained by expanding a part of the liquid refrigerant led from the condenser with a sub-expansion valve;
A main expansion valve for expanding the liquid refrigerant led from the intermediate cooler;
An evaporator for evaporating the refrigerant guided from the main expansion valve;
With
The plate heat exchanger has a plate width of 100 mm or more and 400 mm or less, a height of the plate of 300 mm or more and 1000 mm or less, and a stack number of the plates of 80 or more. 冷媒を圧縮する圧縮機と、
該圧縮機により圧縮された冷媒を凝縮する凝縮器と、
該凝縮器から導かれる液冷媒と該凝縮器から導かれる一部の液冷媒を副膨張弁で膨張させた二相冷媒とを熱交換させるプレート式熱交換器とされた中間冷却器と、
該中間冷却器から導かれた液冷媒を膨張させる主膨張弁と、
該主膨張弁から導かれた冷媒を蒸発させる蒸発器と、
前記中間冷却器をバイパスして前記凝縮器からの液冷媒を前記主膨張弁の上流側に導くバイパス経路と、
該バイパス経路に設けられたバイパス弁と、
該バイパス弁の開度を制御する制御部と、
を備えていることを特徴とする冷凍機。 A compressor for compressing the refrigerant;
A condenser for condensing the refrigerant compressed by the compressor;
An intermediate cooler configured as a plate heat exchanger for exchanging heat between the liquid refrigerant led from the condenser and a two-phase refrigerant obtained by expanding a part of the liquid refrigerant led from the condenser with a sub-expansion valve;
A main expansion valve for expanding the liquid refrigerant led from the intermediate cooler;
An evaporator for evaporating the refrigerant guided from the main expansion valve;
A bypass path that bypasses the intermediate cooler and guides the liquid refrigerant from the condenser to the upstream side of the main expansion valve;
A bypass valve provided in the bypass path;
A control unit for controlling the opening of the bypass valve;
A freezer comprising the above. 冷媒を圧縮する圧縮機と、
該圧縮機により圧縮された冷媒を凝縮する凝縮器と、
該凝縮器から導かれる液冷媒と該凝縮器から導かれる一部の液冷媒を副膨張弁で膨張させた二相冷媒とを熱交換させるプレート式熱交換器とされた中間冷却器と、
該中間冷却器から導かれた液冷媒を膨張させる主膨張弁と、
該主膨張弁から導かれた冷媒を蒸発させる蒸発器と、
前記中間冷却器をバイパスして前記凝縮器からの液冷媒を前記蒸発器の被冷却媒体入口側に導くバイパス経路と、
該バイパス経路に設けられたバイパス弁と、
該バイパス弁の開度を制御する制御部と、
を備えていることを特徴とする冷凍機。 A compressor for compressing the refrigerant;
A condenser for condensing the refrigerant compressed by the compressor;
An intermediate cooler configured as a plate heat exchanger for exchanging heat between the liquid refrigerant led from the condenser and a two-phase refrigerant obtained by expanding a part of the liquid refrigerant led from the condenser with a sub-expansion valve;
A main expansion valve for expanding the liquid refrigerant led from the intermediate cooler;
An evaporator for evaporating the refrigerant guided from the main expansion valve;
A bypass path that bypasses the intermediate cooler and guides the liquid refrigerant from the condenser to the cooled medium inlet side of the evaporator;
A bypass valve provided in the bypass path;
A control unit for controlling the opening of the bypass valve;
A freezer comprising the above. 前記制御部は、前記凝縮器内の圧力と前記蒸発器内の圧力との差が所定値以下になった場合、又は、前記主膨張弁の開度が所定値以上になった場合に、前記バイパス弁の開度を増大させることを特徴とする請求項２又は３に記載の冷凍機。   The control unit, when the difference between the pressure in the condenser and the pressure in the evaporator becomes a predetermined value or less, or when the opening of the main expansion valve becomes a predetermined value or more, The refrigerator according to claim 2 or 3, wherein the opening degree of the bypass valve is increased. 冷媒を圧縮する圧縮機と、
該圧縮機により圧縮された冷媒を凝縮する凝縮器と、
該凝縮器から導かれる液冷媒と該凝縮器から導かれる一部の液冷媒を副膨張弁で膨張させた二相冷媒とを熱交換させるプレート式熱交換器とされた中間冷却器と、
該中間冷却器から導かれた液冷媒を膨張させる主膨張弁と、
該主膨張弁から導かれた冷媒を蒸発させる蒸発器と、
前記中間冷却器をバイパスして前記凝縮器からの液冷媒を前記主膨張弁の上流側に導くバイパス経路と、
該バイパス経路に設けられたバイパス弁と、
を備えた冷凍機の制御方法であって、
前記凝縮器内の圧力と前記蒸発器内の圧力との差が所定値以下になった場合、又は、前記主膨張弁の開度が所定値以上になった場合に、前記バイパス弁の開度を増大することを特徴とする冷凍機の制御方法。 A compressor for compressing the refrigerant;
A condenser for condensing the refrigerant compressed by the compressor;
An intermediate cooler configured as a plate heat exchanger for exchanging heat between the liquid refrigerant led from the condenser and a two-phase refrigerant obtained by expanding a part of the liquid refrigerant led from the condenser with a sub-expansion valve;
A main expansion valve for expanding the liquid refrigerant led from the intermediate cooler;
An evaporator for evaporating the refrigerant guided from the main expansion valve;
A bypass path that bypasses the intermediate cooler and guides the liquid refrigerant from the condenser to the upstream side of the main expansion valve;
A bypass valve provided in the bypass path;
A method of controlling a refrigerator comprising:
When the difference between the pressure in the condenser and the pressure in the evaporator becomes a predetermined value or less, or when the opening of the main expansion valve becomes a predetermined value or more, the opening of the bypass valve The control method of the refrigerator characterized by increasing. 冷媒を圧縮する圧縮機と、
該圧縮機により圧縮された冷媒を凝縮する凝縮器と、
該凝縮器から導かれる液冷媒と該凝縮器から導かれる一部の液冷媒を副膨張弁で膨張させた二相冷媒とを熱交換させるプレート式熱交換器とされた中間冷却器と、
該中間冷却器から導かれた液冷媒を膨張させる主膨張弁と、
該主膨張弁から導かれた冷媒を蒸発させる蒸発器と、
前記中間冷却器をバイパスして前記凝縮器からの液冷媒を前記蒸発器の被冷却媒体入口側に導くバイパス経路と、
該バイパス経路に設けられたバイパス弁と、
を備えた冷凍機の制御方法であって、
前記凝縮器内の圧力と前記蒸発器内の圧力との差が所定値以下になった場合、又は、前記主膨張弁の開度が所定値以上になった場合に、前記バイパス弁の開度を増大することを特徴とする冷凍機の制御方法。 A compressor for compressing the refrigerant;
A condenser for condensing the refrigerant compressed by the compressor;
An intermediate cooler configured as a plate heat exchanger for exchanging heat between the liquid refrigerant led from the condenser and a two-phase refrigerant obtained by expanding a part of the liquid refrigerant led from the condenser with a sub-expansion valve;
A main expansion valve for expanding the liquid refrigerant led from the intermediate cooler;
An evaporator for evaporating the refrigerant guided from the main expansion valve;
A bypass path that bypasses the intermediate cooler and guides the liquid refrigerant from the condenser to the cooled medium inlet side of the evaporator;
A bypass valve provided in the bypass path;
A method of controlling a refrigerator comprising:
When the difference between the pressure in the condenser and the pressure in the evaporator becomes a predetermined value or less, or when the opening of the main expansion valve becomes a predetermined value or more, the opening of the bypass valve The control method of the refrigerator characterized by increasing.
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