WO2020195711A1 - 液分離器、冷却システム及び気液分離方法 - Google Patents
液分離器、冷却システム及び気液分離方法 Download PDFInfo
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- WO2020195711A1 WO2020195711A1 PCT/JP2020/009696 JP2020009696W WO2020195711A1 WO 2020195711 A1 WO2020195711 A1 WO 2020195711A1 JP 2020009696 W JP2020009696 W JP 2020009696W WO 2020195711 A1 WO2020195711 A1 WO 2020195711A1
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- Prior art keywords
- refrigerant
- liquid
- closed container
- liquid separator
- compressor
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Classifications
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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
- 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
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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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
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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
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
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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
- F25B2700/04—Refrigerant level
Definitions
- the present invention relates to a liquid separator, a cooling system, and a gas-liquid separation method, which are mainly used in a cooling system and separate the liquid flowing from the evaporator to the compressor.
- an accumulator serving as a liquid separator may be installed in front of the suction port of the compressor.
- the cooling system shown in Patent Document 1 includes an evaporator, a compressor, a condenser, and a pressure reducing expansion valve along the refrigerant flow path.
- the evaporator absorbs ambient heat by evaporating the liquid phase refrigerant.
- the compressor compresses the vapor-phase refrigerant delivered from the evaporator.
- the condenser releases the heat of the refrigerant whose high pressure is increased by the compressor to condense the vapor phase refrigerant.
- the decompression expansion valve decompresses and expands the liquid phase refrigerant cooled by the condenser.
- a liquid separator for gas-liquid separation of the refrigerant after passing through the evaporator is provided on the upstream side of the compressor.
- This liquid separator has a vertically elongated separation container as a whole.
- a refrigerant inflow pipe and a gas phase refrigerant outflow pipe are installed above the separation container.
- a liquid phase refrigerant outflow pipe is installed below the separation container.
- the refrigerant that has flowed into the inside through the refrigerant inflow pipe rotates in the circumferential direction along the inner wall of the liquid separator of the separation container, and the liquid-phase refrigerant and the gas-phase refrigerant are mixed. Is centrifuged.
- the gas phase refrigerant in the separation container is guided to the pressure reducing expansion valve via the upper gas phase refrigerant outflow pipe, and the liquid phase refrigerant in the separation container is guided to the evaporator via the lower liquid phase refrigerant outflow pipe. You will be guided.
- Patent Document 2 also shows a similar liquid separator. Similar to Patent Document 1, the liquid separator disclosed in Patent Document 2 has a closed container formed vertically as a whole. At the bottom of this closed container, there is a first pipe that allows gas-liquid two-phase fluid to flow into the closed container, a second pipe that discharges the gas in the closed container to the outside, and a second pipe that discharges the liquid in the closed container to the outside. 3 pipes are connected.
- the present invention provides a liquid separator, a cooling system and a gas-liquid separation method capable of stably arranging the compressor on the upper part of the closed container.
- the liquid separator according to the first aspect of the present invention comprises a tubular closed container in which a refrigerant is stored, a refrigerant inflow pipe for inflowing the refrigerant into the closed container, and a gas phase refrigerant in the space inside the closed container. It has a refrigerant outflow pipe that allows the outflow to the outside, and the refrigerant inflow pipe and the refrigerant outflow pipe are arranged from the upper part of the closed container toward the inside of the container, respectively, and the closed container is height relative to the diameter. Is configured to form a relatively small short tube.
- a second aspect of the present invention is an evaporator that absorbs ambient heat by evaporating the liquid-phase refrigerant along the refrigerant flow path, a compressor that compresses the vapor-phase refrigerant, and a high pressure by the compressor.
- a cooling system including a condenser that releases the heat of the refrigerant to condense the gas-phase refrigerant and a decompression expansion valve that depressurizes and expands the liquid-phase refrigerant cooled by the condenser, and is on the upstream side of the compressor.
- the liquid separator for gas-liquid separation of the refrigerant after passing through the evaporator, and the liquid separator has a cylindrical closed container in which the refrigerant is stored and a refrigerant in the space inside the closed container. It has a refrigerant inflow pipe for inflowing the refrigerant and a refrigerant outflow pipe for discharging the refrigerant in the space inside the closed container to the outside, and the closed container has a short tubular shape whose height is relatively small with respect to the diameter. It is configured as follows.
- the gas-liquid separation method includes a refrigerant inflow pipe that allows the refrigerant to flow into a tubular closed container in which the refrigerant is stored, and a refrigerant outflow pipe that allows the refrigerant in the space inside the closed container to flow out.
- the closed container is formed so as to form a short cylinder whose height is relatively small with respect to the diameter.
- the liquid separator can be held in a stable state.
- FIG. 5A It is a perspective view which shows the modification 1 of the splash prevention plate. It is a perspective view which shows the modification 2 of the splash prevention plate.
- the liquid separator 10 is located on the upstream side of the compressor 3 in the cooling system 1, and is provided for gas-liquid separation of the refrigerant after passing through the evaporator 2, for example.
- the cooling system 1 includes an evaporator 2, a compressor 3, a condenser 4, and a pressure reducing expansion valve 5 along the refrigerant flow path 1A.
- the evaporator 2 absorbs ambient heat by evaporating the liquid phase refrigerant.
- the compressor compresses the vapor phase refrigerant.
- the condenser 4 releases the heat of the refrigerant that has become high pressure by the compressor 3 to condense (or forcibly compress) the vapor phase refrigerant.
- the pressure reducing expansion valve 5 expands the liquid phase refrigerant supplied from the condenser 4.
- the liquid separator 10 located on the upstream side of the compressor 3 has a tubular closed container 11 in which the refrigerant C is stored. Inside the closed container 11, a refrigerant inflow pipe 12 for flowing in a gas phase medium or a gas-liquid two-phase refrigerant and a refrigerant outflow pipe 13 for discharging the gas phase refrigerant in the closed container 11 to the outside are provided.
- the refrigerant inflow pipe 12 and the refrigerant outflow pipe 13 are installed from the upper surface 11A of the closed container 11 toward the inside of the container 11B, respectively.
- the refrigerant inflow pipe 12 and the refrigerant outflow pipe 13 are arranged at the largest possible mutual spacing in the radial direction (R direction) of the closed container 11.
- the closed container 11 of the liquid separator 10 has a height h relatively small with respect to a diameter along the R direction, and is configured to have a short tubular shape as a whole.
- liquid separator 10 since the closed container 11 is formed in a short cylinder shape, even if a heavy compressor 3 is arranged on the upper surface 11A of the closed container 11, the upper part of the liquid separator 10 The liquid separator 10 can be held in a stable state without becoming heavy, so-called top heavy.
- the vapor-phase refrigerant that has absorbed heat H1 from the heat source by the evaporator 2 and evaporated is gas-liquid separated by the liquid separator 10 and then compressed by the compressor 3. , Sent to the condenser 4. After that, the liquid-phase refrigerant condensed by heat dissipation H2 to the cold heat source by the condenser 4 is depressurized to a predetermined pressure by the decompression expansion valve 5 and sent to the evaporator 2 again.
- the liquid-phase refrigerant may not be sufficiently evaporated in the evaporator 2 due to a decrease in the load of the heat source, a failure of the pressure reducing expansion valve 5, or the like, and may be supplied to the compressor 3 as a gas-liquid mixed flow.
- the phenomenon in which the liquid is supplied to the compressor 3 in this way is called a liquid bag.
- the performance of the compressor 3 may be deteriorated or a failure may be caused.
- the liquid separator 10 in the liquid separator 10 according to the embodiment of the present invention, the liquid is separated from the gas-liquid mixed flow after passing through the evaporator 2, and only the gas is supplied to the compressor 3. There is.
- the closed container 11 has a short tubular shape whose height (h) is relatively small with respect to the radial direction (R direction). It is formed. Therefore, the height of the entire cooling system can be lowered, and even if the heavy compressor 3 is arranged on the upper surface 11A of the closed container 11, the entire device can be installed in a stable state without becoming top heavy. it can. Further, in the liquid separator 10, the closed container 11 is formed in a short cylinder shape. Therefore, the refrigerant inflow pipe 12 and the refrigerant outflow pipe 13 can be arranged on the upper surface 11A of the closed container 11 at sufficient intervals in the radial direction (R direction).
- the influence of the turbulence of the liquid level of the refrigerant caused by the inflow of the refrigerant from the refrigerant inflow pipe 12 into the closed container 11 extends to the refrigerant flowing out to the refrigerant outflow pipe 13. Can be prevented. Therefore, it is possible to prevent the liquid phase refrigerant in the closed container 11 from being wound up and flowing out from the refrigerant outflow pipe 13.
- the liquid separator 200 is installed in the cooling system F.
- the cooling system F includes the evaporator 100 in the middle of the refrigerant flow path (specifically, the pipeline) composed of the refrigerant flow paths 610, 620, 630, 640, and 650.
- a liquid separator 200 a compressor 300, a condenser 400, and a pressure reducing expansion valve 500.
- the evaporator 100 absorbs the ambient heat H1 by evaporating the liquid phase refrigerant.
- the liquid separator 200 separates the refrigerant into gas and liquid.
- the compressor 300 compresses the gas phase refrigerant discharged from the liquid separator 200.
- the condenser 400 releases the heat of the refrigerant whose high pressure is increased by the compressor 300 to condense the vapor phase refrigerant.
- the pressure reducing expansion valve 500 decompresses and expands the liquid phase refrigerant cooled by the condenser 400.
- the refrigerant supplied from the pressure reducing expansion valve 500 via the refrigerant flow path 650 absorbs heat H1 from the heat source in the evaporator 100 and evaporates.
- the evaporated vapor-phase refrigerant passes through the refrigerant flow path 610, the liquid separator 200, and the refrigerant flow path 620 in this order, and is sent to the compressor 300.
- the vapor-phase refrigerant compressed to a high temperature and high pressure by the compressor 300 is sent to the condenser 400 via the refrigerant flow path 630, dissipates heat to a cold heat source, and is condensed.
- the liquid-phase refrigerant condensed in the condenser 400 moves to the pressure reducing expansion valve 500 through the refrigerant flow path 640 and is reduced to a predetermined pressure. After that, the liquid-phase refrigerant is sent to the evaporator 100 again through the refrigerant flow path 650.
- the liquid separator 200 is arranged on the upstream side of the compressor 300 and has a role of preventing the liquid phase refrigerant from being sucked into the compressor 300. Since the compressor 300 is designed to compress the gas phase refrigerant, it is known that if the liquid phase refrigerant is mixed in, it may lead to a failure (referred to as a liquid back phenomenon). Normally, the refrigerant completely evaporates in the evaporator 100 and becomes only the vapor phase refrigerant. However, in the evaporator 100, when a disturbance such as a decrease in heat load occurs, the refrigerant may not evaporate and a part of the liquid phase refrigerant may remain.
- this liquid-phase refrigerant is sent to the refrigerant flow path 610. Therefore, the liquid separator 200 separates the liquid phase refrigerant contained in the refrigerant and supplies only the vapor phase refrigerant to the downstream compressor 300.
- the refrigerant flow path 620 Unless there are restrictions on installation, it is preferable to construct the refrigerant flow path 620 avoiding a structure having a reverse gradient with respect to the direction of gravity or a U-shaped structure. This is because if such a reverse gradient structure or U-shaped structure exists in the refrigerant flow path 620, the liquid phase refrigerant condensed in the refrigerant flow path 620 stays in the portion when the cooling system F is stopped. .. In this way, the liquid-phase refrigerant retained in the refrigerant flow path 620 is sucked into the compressor 300 together with the vapor-phase refrigerant when the cooling system F is started next time, so that the liquid separator 200 is installed. , There is a risk of causing a liquid back phenomenon in the compressor 300.
- the liquid separator 200 located on the upstream side of the compressor 300 has a tubular housing 210 that serves as a closed container in which the refrigerant is stored.
- a refrigerant inflow pipe 220 for inflowing a gas-phase refrigerant or a gas-liquid two-phase refrigerant and a refrigerant outflow pipe 230 for flowing out the gas-phase refrigerant in the housing 210 to the outside are installed in the housing 210.
- the refrigerant inflow pipe 220 and the refrigerant outflow pipe 230 are installed from the upper surface 210A of the housing 210 toward the inside of the container 210B.
- the refrigerant inflow pipe 220 and the refrigerant outflow pipe 230 are arranged at intervals in the radial direction (R direction) of the housing 210.
- the refrigerant inflow pipe 220 is connected to the refrigerant flow path 610 in which the gas-phase refrigerant or the gas-liquid two-phase refrigerant from the evaporator 100 is guided.
- the refrigerant outflow pipe 230 is connected to a refrigerant flow path 620 that guides the vapor phase refrigerant to the compressor 300.
- the gas-phase refrigerant or the gas-liquid two-phase refrigerant after passing through the evaporator 100 flows into the housing 210 through the refrigerant inflow pipe 220, and the liquid-phase refrigerant in the gas-liquid mixed flow reaches the bottom of the housing 210 by gravity. It falls and stays.
- the gas-phase refrigerant in the gas-liquid mixed flow is sent to the compressor 300 through the refrigerant outflow pipe 230.
- the housing 210 of the liquid separator 200 has a height h relatively small with respect to a diameter along the R direction, and is configured to have a short tubular shape as a whole. As described above, in the liquid separator 200, the housing 210 is formed in the shape of a short cylinder whose height h is relatively small with respect to the diameter in the R direction, so that the housing 210 is formed on the upper surface 210A of the housing 210. Even if the heavy compressor 300 is arranged, the compressor 300 can be held in a stable state.
- the vapor phase refrigerant which has absorbed heat H1 from the heat source by the evaporator 2 and evaporated is compressed by the compressor 300 and becomes high temperature and high pressure.
- Sent to the condenser 400 Sent to the condenser 400.
- the liquid-phase refrigerant condensed by heat dissipation H2 to the cold heat source by the condenser 400 is depressurized to a predetermined pressure by the decompression expansion valve 500 and sent to the evaporator 100 again.
- a mesh-shaped splash prevention plate 240 is installed to prevent the phase refrigerant C1 from blowing up the liquid phase refrigerant C2 staying in the housing 210.
- a mesh-shaped splash prevention plate 240 is installed below the refrigerant inflow pipe 220. The mesh-shaped splash prevention plate 240 mitigates the impact of the gas phase refrigerant C1 on the liquid surface of the liquid phase refrigerant C2, thereby preventing the liquid phase refrigerant C2 from being blown up.
- the housing 210 is formed in a short tubular shape having a height h relatively small in the radial direction (R direction). Even if a heavy compressor 300 is arranged on the upper surface 210A of the housing 210, the compressor 300 can be held in a stable state without becoming top heavy. Further, in the liquid separator 200, since the housing 210 is formed in a short cylinder shape, the refrigerant inflow pipe 220 is provided on the upper surface 210A of the housing 210 at regular intervals in the radial direction (R direction). And the refrigerant outflow pipe 230 can be arranged.
- the influence of the undulation (turbulence) of the liquid level of the liquid phase refrigerant C2 caused by the inflow of the refrigerant from the refrigerant inflow pipe 220 into the housing 210 affects the refrigerant outflow pipe 230. To prevent. Therefore, it is possible to prevent the liquid-phase refrigerant C2 in the housing 210 from being blown up and flowing out from the refrigerant outflow pipe 230.
- the momentum of the vapor phase refrigerant C1 colliding with the liquid surface is alleviated. Prevents the liquid level of the liquid phase refrigerant C2 from waving. This also prevents the liquid-phase refrigerant C2 in the housing 210 from flowing out from the outlet 230A of the refrigerant outflow pipe 230.
- liquid separator 200 there is no complicated structure that causes a large pressure loss in the flow path of the gas phase refrigerant from the refrigerant inflow pipe 220 to the refrigerant outflow pipe 230.
- the pressure loss at the time of gas-liquid separation of the refrigerant is suppressed, and the so-called liquid back phenomenon to the compressor 300 (due to the droplets of the refrigerant flowing through the flow path with kinetic energy). , Damage to the cooling system pipelines and equipment) can be prevented.
- a mesh-shaped plate is used as the splash prevention plate 240, but the present invention is not limited to this. That is, as the splash prevention plate 240, a plate having a large number of through holes 240a as shown in FIG. 6, for example, a plate having a plurality of holes such as punching metal may be used.
- (Modification 2) Further, as the splash prevention plate 240, a net-like body formed by entwining a plurality of fibers 240b as shown in FIG. 7, for example, a metal scrubbing brush processed into a flat shape may be used.
- liquid separator 200'according to the second embodiment of the present invention will be described with reference to FIG.
- the difference in configuration of the liquid separator 200'according to the second embodiment from the liquid separator 200 according to the first embodiment is that a liquid intrusion prevention plate 250 is provided below the outlet of the refrigerant outflow pipe 230. ..
- the splash prevention plate 240 alone is sufficient. There is a risk that the prevention of splashing will be insufficient. Therefore, in the liquid separator 200', in addition to providing the splash prevention plate 240 below the inflow port (outlet toward the liquid separator 200') 220A of the refrigerant inflow pipe 220, the outlet of the refrigerant outflow pipe 230 (outlet).
- a liquid intrusion prevention plate 250 for preventing inhalation of the liquid phase refrigerant C2 is provided below 230A (the port through which the liquid flows from the liquid separator 200').
- the liquid intrusion prevention plate 240 includes, in addition to a normal plate, a mesh-shaped plate shown in FIG. 5B, a plate having a large number of through holes shown in FIG. 6, or a plurality of plates shown in FIG. A net-like body (or cotton-like body) formed by entwining fibers can also be used.
- the liquid level sensor 260, the maintenance valve 270, and the control unit 700 are different in the configuration from the liquid separators 200 and 200'shown in the first and second embodiments. It is at the point where.
- the gaseous refrigerant is completely sent from the outlet of the evaporator 100, and the liquid phase refrigerant is transferred from the evaporator 100 to the liquid separator 200 only when the operation becomes unstable due to the disturbance. Will be sent to.
- the liquid phase refrigerant C2 staying in the housing 210 due to the unstable operation gradually evaporates during the subsequent normal operation to become the gas phase refrigerant C1, and the retention is eliminated.
- the liquid level sensor 260 for monitoring the amount of the liquid phase refrigerant C2 staying in the housing 210 is mounted on the housing. It is attached to 210. If the liquid level of the liquid phase refrigerant C2 staying in the housing 210 is higher than the position of the splash prevention plate 240, the splash prevention plate 240 will not function and the liquid separation function may be significantly reduced. is expected. In this case, the liquid phase refrigerant C2 may flow out from the refrigerant outflow pipe 230 and cause liquid back, so it is necessary to stop the compressor 300.
- the value of the liquid level sensor 260 of the liquid separator 200 is monitored, and the liquid level of the liquid phase refrigerant C2 exceeds the limit value.
- a control unit 700 for stopping the entire cooling system F'including the compressor 300 is provided.
- the maintenance valve 270 at the lower part of the housing 210 is opened and the retained liquid phase refrigerant C2 is discharged to return to the normal state. can do.
- the maintenance valve 270 may be opened and closed manually by an operator, or may be opened and closed by a drive means operated by a separately provided control unit 700.
- the present invention is mainly used in cooling systems and can be applied to liquid separators, cooling systems and gas-liquid separation methods that separate the liquid flowing from the evaporator into the compressor, with a compressor having weight on top of the liquid separator. Even if it is arranged, the liquid separator can be held in a stable state. ..
- Cooling system 1A Refrigerant flow path 2 Evaporator 3 Compressor 4 Condenser 5 Decompression expansion valve 10 Liquid separator 11 Closed container 12 Refrigerant inflow pipe 13 Refrigerant outflow pipe 100 Evaporator 200 Liquid separator 200'Liquid separator 200 "Liquid Separator 210 Housing 240 Splash prevention plate 250 Liquid intrusion prevention plate 260 Liquid level sensor 270 Maintenance valve 300 Compressor 400 Condenser 500 Decompression expansion valve 610 Refrigerant flow path 620 Refrigerant flow path 630 Refrigerant flow path 640 Liquid tube 650 Liquid tube 700 Control unit C Refrigerant C1 Gas phase refrigerant C2 Liquid phase refrigerant F Cooling cycle F'Cooling cycle R Radial direction
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Abstract
Description
例えば、特許文献1に示される冷却システムは、冷媒流路に沿って、蒸発器と、圧縮機と、凝縮器と、減圧膨張弁とを備える。蒸発器は、液相冷媒を蒸発させることで周囲の熱を吸収する。圧縮機は、蒸発器から送り出された気相冷媒を圧縮する。凝縮器は、圧縮機によって高圧となった冷媒の熱を放出し気相冷媒を凝縮させる。減圧膨張弁は、凝縮器によって冷やされた液相冷媒を減圧膨張させる。
特許文献1に示されるこの冷却システムには、圧縮機の上流側において、蒸発器を経由した後の冷媒を気液分離する液分離器が設けられている。
この液分離器においては、冷媒流入管を経由して内部に流入した冷媒が、分離容器の液分離器の内壁に沿うようにして円周方向に回転しながら、液相冷媒と気相冷媒とに遠心分離される。
その後、分離容器内の気相冷媒は上部の気相冷媒流出管を経由して減圧膨張弁に案内され、分離容器内の液相冷媒は下部の液相冷媒流出管を経由して蒸発器に案内される。
この特許文献2に開示された液分離器は、特許文献1と同様、全体として縦長に形成された密閉容器を有する。この密閉容器の下部には、気液二相流体を密閉容器の内部へ流入させる第1配管、密閉容器内のガスを外部に排出する第2配管、密閉容器内の液を外部に排出する第3配管が接続される。
このため、アキュムレータが上下に長く、このアキュムレータの上部に圧縮機を配置した場合には、液分離器の上部が重く重心が高くなる。そのため、液分離器が不安定な状態になり、この点を改良するための新たな技術提供が期待されていた。
本発明の第1態様による液分離器は、冷媒が貯留される筒状の密閉容器と、前記密閉容器内に冷媒を流入させる冷媒流入管と、前記密閉容器内の空間中の気相冷媒を外部に流出させる冷媒流出管とを有し、前記冷媒流入管及び前記冷媒流出管は、前記密閉容器の上部から容器内部へ向けてそれぞれ配置されており、前記密閉容器は径に対して高さが相対的に小さい短筒状をなすように構成される。
この液分離器10は、冷却システム1内にある圧縮機3の上流側に位置し、例えば蒸発器2を経由した後の冷媒を気液分離するために設けられる。
この冷却システム1は、冷媒流路1Aに沿って、蒸発器2と、圧縮機3と、凝縮器4と、減圧膨張弁5とを備える。蒸発器2は、液相冷媒を蒸発させることで周囲の熱を吸収する。圧縮機は、気相冷媒を圧縮する。凝縮器4は、この圧縮機3によって高圧となった冷媒の熱を放出し気相冷媒を凝縮(あるいは強制的に圧縮)させる。減圧膨張弁5は、この凝縮器4から供給された液相冷媒を膨張させる。
また、液分離器10の密閉容器11はR方向に沿う径に対して高さhが相対的に小さく、全体として短筒状となるように構成されている。
このような液分離器10においては、密閉容器11が短筒状に形成されているので、密閉容器11の上部面11Aに重量の大きな圧縮機3を配置したとしても、液分離器10の上部が重くなる、いわゆるトップヘビーとなることを避けて、液分離器10を安定した状態で保持することができる。
ここで、液相冷媒が、熱源の負荷低下や減圧膨張弁5の故障等によって蒸発器2において十分に蒸発せず、気液混合流となって圧縮機3に供給されることがある。このように液体が圧縮機3に供給される現象は液バックと称される。液体が圧縮機3に供給されると、圧縮機3の性能低下や故障を引き起こす可能性がある。これを防止するために本発明の実施形態に係る液分離器10では、蒸発器2を経た後の気液混合流のうち、液体を分離し、気体のみを圧縮機3に供給するようにしている。
また、上記液分離器10においては、密閉容器11が短筒状に形成されている。したがって、密閉容器11の上部面11Aに、冷媒流入管12及び冷媒流出管13を径方向(R方向)に十分な間隔で配置することができる。
その結果、上記液分離器10においては、冷媒流入管12から密閉容器11へ冷媒が流入することによって生じた冷媒の液面の乱れの影響が、冷媒流出管13へ流出する冷媒に及ぶことを防止することができる。したがって、密閉容器11内の液相冷媒が、巻き上げられて冷媒流出管13から流出する事態を未然に防止することができる。
本発明の第1実施形態に係る液分離器200について図2~図7を参照して説明する。
この液分離器200は、冷却システムF内に設置される。
冷却システムFは、図2に示されるように、冷媒流路610,620,630,640,および650により構成される冷媒の流通経路(具体的には管路)の途中に、蒸発器100と、液分離器200と、圧縮機300と、凝縮器400と、減圧膨張弁500とを備える。蒸発器100は、液相冷媒を蒸発させることで周囲の熱H1を吸収する。液分離器200は、冷媒を気液分離する。圧縮機300は、液分離器200から排出された気相冷媒を圧縮する。凝縮器400は、圧縮機300によって高圧となった冷媒の熱を放出し気相冷媒を凝縮させる。減圧膨張弁500は、凝縮器400によって冷やされた液相冷媒を減圧膨張させる。
圧縮機300で高温高圧に圧縮された気相冷媒は、冷媒流路630を経由して凝縮器400に送られ、冷熱源に放熱H2して凝縮する。
その後、凝縮器400において凝縮した液相冷媒は、冷媒流路640を通して減圧膨張弁500に移動し、所定の圧力まで減圧される。その後、液相冷媒は冷媒流路650を通して再び蒸発器100に送られる。
圧縮機300は気相冷媒を圧縮するように設計されているので、液相冷媒が混入した場合には故障に繋がることが知られている(液バック現象という)。通常、冷媒は、蒸発器100において完全に蒸発して気相冷媒のみになる。しかし、蒸発器100において、熱負荷の低下等の外乱が生じると、冷媒が蒸発せずに液相冷媒が一部残ることがある。その場合には、この液相冷媒が冷媒流路610に送られる。このため、液分離器200は、冷媒に含有される液相冷媒を分離し、気相冷媒のみを下流の圧縮機300に供給する。
蒸発器100を経た後の気相冷媒又は気液二相冷媒は、冷媒流入管220を通して筐体210内に流入し、気液混合流の中の液相冷媒が重力によって筐体210の底部に落下して滞留する。一方で、気液混合流の中の気相冷媒は冷媒流出管230を通して圧縮機300に送られる。
このように、液分離器200においては、その筐体210が、R方向の径に対して高さhが相対的に小さい短筒状に形成されているので、筐体210の上部面210Aに重量を有する圧縮機300を配置したとしても、圧縮機300を安定した状態で保持することができる。
筐体210内では、冷媒流入管220を通じて供給される気相冷媒C1の流速が大きい場合に、この冷媒C1に液相冷媒が混入していなくとも、気相冷媒C1の勢いによって筐体210の底面に滞留した液相冷媒C2が吹き上げられる可能性がある。この場合、吹き上げられた液相冷媒C2は、冷媒流出管230の流出口(筐体210から液が流出するための開口)230Aから流れ出る恐れがある。
このため、図5A及び図5Bに示されるように、冷媒流入管220の下方にメッシュ状の飛沫防止板240が設置される。このメッシュ状の飛沫防止板240によって、気相冷媒C1が液相冷媒C2の液面に与える衝撃を緩和することで、液相冷媒C2が吹き上げられることを未然に防止する。
また、上記液分離器200においては、筐体210が短筒状に形成されているので、筐体210の上部面210Aに、径方向(R方向)に一定の間隔を置いて冷媒流入管220及び冷媒流出管230を配置することができる。
その結果、上記液分離器200においては、冷媒流入管220から筐体210内への冷媒流入で生じた液相冷媒C2の液面の波打ち(乱れ)の影響が、冷媒流出管230に及ぶことを防止する。したがって、筐体210内の液相冷媒C2が吹き上げられて冷媒流出管230から流出することを防止することができる。
上記実施形態では、飛沫防止板240としてメッシュ状の板体を使用したが、これに限定されない。すなわち、飛沫防止板240として、図6に示されるような多数の貫通孔240aを有する板体、例えば、パンチングメタルのように複数の穴の開いた板などを使用しても良い。
さらに、飛沫防止板240として、図7に示されるような複数の繊維240bが絡み合うことで形成された網状体、例えば、金属たわしを偏平状に加工した形状のものを使用しても良い。
本発明の第2実施形態に係る液分離器200’について図8を参照して説明する。
第2実施形態による液分離器200’が、第1実施形態による液分離器200と構成を異にする点は、冷媒流出管230の出口の下方に液侵入防止板250を設けた点にある。
なお、液侵入防止板240としては、通常の板体の他、図5Bに示されるメッシュ状の板体、図6に示される多数の貫通孔を有する板体、又は図7に示される複数の繊維が絡み合うことで形成された網状体(ないしは綿状体)、なども使用可能である。
本発明の第3実施形態に係る液分離器200”について図9及び図10を参照して説明する。
このため、第3実施形態に示す液分離器200”では、図9に示すように、筐体210内に滞留する液相冷媒C2の液量を監視するための液面センサ260をこの筐体210に取り付けている。
仮に、筐体210内に滞留する液相冷媒C2の液面が、飛沫防止板240の位置より高くなった場合には、飛沫防止板240が機能しなくなり、液分離機能が著しく低下することが予想される。
この場合には、冷媒流出管230から液相冷媒C2が流れ出て液バックを引き起こす恐れがあるので、圧縮機300を停止させる必要がある。
そして、第3実施形態の液分離器200”では、冷却システムF’の停止後に、筐体210の下部のメンテバルブ270を開として、滞留した液相冷媒C2を放出することによって正常状態に復帰することができる。
なお、このメンテバルブ270は作業員が手動で開閉しても良いし、別途設けた制御部700により動作される駆動手段により開閉しても良い。
1A 冷媒流路
2 蒸発器
3 圧縮機
4 凝縮器
5 減圧膨張弁
10 液分離器
11 密閉容器
12 冷媒流入管
13 冷媒流出管
100 蒸発器
200 液分離器
200’ 液分離器
200” 液分離器
210 筐体
240 飛沫防止板
250 液侵入防止板
260 液面センサ
270 メンテバルブ
300 圧縮機
400 凝縮器
500 減圧膨張弁
610 冷媒流路
620 冷媒流路
630 冷媒流路
640 液管
650 液管
700 制御部
C 冷媒
C1 気相冷媒
C2 液相冷媒
F 冷却サイクル
F’ 冷却サイクル
R 径方向
Claims (10)
- 冷媒が貯留される筒状の密閉容器と、前記密閉容器内に冷媒を流入させる冷媒流入管と、前記密閉容器内の空間に流入した冷媒を外部に流出させる冷媒流出管とを有し、
前記冷媒流入管及び前記冷媒流出管は、前記密閉容器の上部から容器内部へ向けてそれぞれ配置されており、
前記密閉容器は径に対して高さが相対的に小さい短筒状である液分離器。 - 前記密閉容器内に位置する前記冷媒流入管の出口付近には、前記冷媒の飛沫が散乱することを防止する飛沫防止板が設置されている請求項1に記載の液分離器。
- 前記飛沫防止板はメッシュ状の板体により構成される請求項2に記載の液分離器。
- 前記飛沫防止板は多数の貫通孔を有する板体で構成される請求項2に記載の液分離器。
- 前記飛沫防止板は複数の繊維が絡み合うことで形成された網状体により構成される請求項2に記載の液分離器。
- 前記冷媒流出管の入口付近には、前記密閉容器内の液相冷媒の侵入を防止する液侵入防止板がさらに設けられる請求項1~5のいずれか1項に記載の液分離器。
- 前記密閉容器には液相冷媒の液面高さを検出する液面センサと、前記液面センサの検出値が予め定めた限界値を越えた場合に装置全体を停止する制御部とが設けられる請求項1~6のいずれか1項に記載の液分離器。
- 前記密閉容器の下部には液相冷媒を排出する排出バルブが設けられる請求項1~7のいずれか1項に記載の液分離器。
- 冷媒流路に沿って、液相冷媒を蒸発させることで周囲の熱を吸収する蒸発器と、前記気相冷媒を圧縮する圧縮機と、前記圧縮機によって高圧となった冷媒の熱を放出し気相冷媒を凝縮させる凝縮器と、前記凝縮器によって冷やされた液相冷媒を減圧膨張させる減圧膨張弁とを備える冷却システムであって、
前記圧縮機の上流側には、前記蒸発器を経由した後の冷媒を気液分離する液分離器が設けられ、
前記液分離器は、冷媒が貯留される筒状の密閉容器と、前記密閉空間に冷媒を流入させる冷媒流入管と、前記密閉容器内の空間中の冷媒を外部に流出させる冷媒流出管とを有し、前記密閉容器は径に対して高さが相対的に小さい短筒状をなすように構成される冷却システム。 - 冷媒が貯留される筒状の密閉容器に、冷媒を流入させる冷媒流入管と、前記密閉容器内の空間中の冷媒を外部に流出させる冷媒流出管とを接続し、
前記密閉容器を、径に対して高さが相対的に小さい短筒状に形成する
気液分離方法。
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US17/439,473 US20220154988A1 (en) | 2019-03-22 | 2020-03-06 | Liquid separator, cooling system, and gas-liquid separation method |
EP20779559.2A EP3943839A4 (en) | 2019-03-22 | 2020-03-06 | LIQUID SEPARATOR, COOLING SYSTEM AND GAS-LIQUID SEPARATION PROCESS |
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