WO2016009516A1 - 冷凍空調装置 - Google Patents
冷凍空調装置 Download PDFInfo
- Publication number
- WO2016009516A1 WO2016009516A1 PCT/JP2014/068959 JP2014068959W WO2016009516A1 WO 2016009516 A1 WO2016009516 A1 WO 2016009516A1 JP 2014068959 W JP2014068959 W JP 2014068959W WO 2016009516 A1 WO2016009516 A1 WO 2016009516A1
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- WIPO (PCT)
- Prior art keywords
- refrigerant
- temperature
- outside air
- dew point
- pipe
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
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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
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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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
- 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
- F25B2400/0417—Refrigeration circuit bypassing means for the subcooler
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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
- 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
Definitions
- the present invention relates to a refrigeration air conditioner, and more particularly, to condensation in a liquid pipe.
- the cooling operation of the cooling device is controlled by the controller so that the temperature of the liquid piping does not become lower than the ambient temperature. Thereby, it controls so that the cooling capacity can be enhanced while preventing the occurrence of dew condensation in the liquid piping constituting the refrigerant circulation circuit (see, for example, Patent Document 1).
- the refrigeration and air-conditioning apparatus described in Patent Document 1 may reuse existing local piping when the apparatus is updated.
- the existing liquid piping may not be insulated. If only the refrigeration air conditioner is updated and the existing liquid pipe is used without heat insulation, condensation will occur in the liquid pipe when the surface temperature of the liquid pipe falls below the dew point temperature of the outside air. There have been problems such as water droplets generated by the condensation falling into the room, causing the room to become submerged, and causing mold.
- Non-Patent Document 1 when the liquid pipe is not thermally insulated, the temperature of the liquid refrigerant is set to the dew point of the outside air around the liquid pipe so that condensation does not occur in the liquid pipe. Can only be lowered to temperature. For this reason, there was a problem that the subcooling of the liquid refrigerant could not be increased and the cooling capacity could not be increased, so that energy saving could not be ensured.
- the refrigerant temperature at the outlet of the condenser may be lower than the dew point temperature of the outside air around the liquid piping.
- the liquid pipe is condensed, and there is a problem that the liquid pipe needs to be heat-insulated.
- the present invention has been made to solve the above-described problems, and a first object is to make the liquid refrigerant condensed by the heat source lower than the outside air dew point temperature lower than the dew point temperature of the surrounding outside air. Even in such a case, the object is to obtain a refrigeration air conditioner that does not cause condensation in the liquid piping.
- the second object of the present invention is that it requires a lot of construction costs and a lot of construction time if the local piping is insulated. For this reason, by adjusting the temperature of the liquid refrigerant, it is possible to select whether or not to heat-insulate the local liquid piping to prevent condensation on one model, and the cost of heat-insulating the customer, etc. Another object is to obtain a refrigeration air conditioner that can flexibly meet demands for delivery and delivery.
- the compressor, the means for cooling the refrigerant using the first heat source that is lower than the outside air dew point temperature, the first pressure reducing device, and the evaporator are connected in an annular shape through the refrigerant pipe.
- a bypass circuit connected between a refrigerant pipe on the inlet side and a refrigerant pipe on the outlet side of the main refrigerant circuit and a means for cooling the refrigerant using the first heat source lower than the outside air dew point temperature.
- Cools the refrigerant using the first heat source below the outside air dew point by bypassing the means for cooling the refrigerant using the first heat source below the outside air dew point temperature with a part of the refrigerant discharged from the compressor To the refrigerant piping on the outlet side of the means for performing.
- the bypass circuit bypasses the refrigerant cooling means using the first heat source that is lower than the outside air dew point temperature.
- the first heat source that is lower than the outside air dew point temperature is used.
- the temperature of the liquid refrigerant is adjusted to exceed the dew point temperature by adding superheated gas from the compressor to the refrigerant condensed by the means for cooling the refrigerant.
- FIG. 1 is a refrigerant circuit diagram of a refrigerating and air-conditioning apparatus according to Embodiment 1 of the present invention.
- the refrigerant circuit 100 of the refrigerating and air-conditioning apparatus includes a compressor 1, a means 2 for cooling refrigerant using a first heat source that is lower than an outside air dew point temperature, a use side expansion valve 3, and a use side heat exchange.
- the vessel 4 is configured to be connected annularly via a refrigerant pipe.
- a circuit having these configurations is referred to as a main refrigerant circuit.
- the compressor 1 and the means 2 for cooling the refrigerant using the first heat source lower than the outside air dew point temperature constitute a heat source side unit, and the use side expansion valve 3 and the use side heat exchanger 4 constitute a use side unit. is doing.
- the means 2 for cooling the refrigerant using the first heat source lower than the outside air dew point temperature and the use side expansion valve 3 are connected by a liquid pipe 5, and the liquid pipe 5 includes an on-site connection liquid pipe 20.
- the use side heat exchanger 4 and the compressor 1 are connected by a gas pipe 7, and the gas pipe 7 includes an on-site connection gas pipe 21.
- the local connection liquid pipe 20 and the local connection gas pipe 21 include cases where existing pipes are used.
- the refrigerant circuit 100 of the refrigeration air conditioner further includes a bypass circuit 11 (sub refrigerant circuit).
- the bypass circuit 11 is connected between the inlet side refrigerant pipe and the outlet side refrigerant pipe of the means 2 for cooling the refrigerant using the first heat source lower than the outside air dew point temperature.
- the bypass circuit 11 sends a part of the refrigerant discharged from the compressor 1 to the liquid pipe 5 by bypassing the means 2 for cooling the refrigerant using the first heat source lower than the outside air dew point temperature.
- the means 2 for cooling the refrigerant using the first heat source that is lower than the outside air dew point temperature is, for example, the outside air dew point temperature of tap water, ground water, geothermal heat, an evaporator of another refrigeration apparatus, or the like. Heat exchange with lower temperature heat source (first heat source). Thereby, the refrigerant
- the refrigerant in the refrigerant circuit 100 is compressed into a high-temperature and high-pressure superheated gas in the compressor 1 and then sent to the means 2 for cooling the refrigerant using the first heat source that is lower than the outside air dew point temperature.
- the refrigerant that passes through the means 2 for cooling the refrigerant using the first heat source that is lower than the outside air dew point temperature is condensed into a high-temperature and high-pressure liquid refrigerant by exchanging heat with the first heat source.
- the liquid refrigerant passes through the liquid pipe 5 and is passed through the use-side expansion valve 3 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant.
- the low-temperature low-pressure gas-liquid two-phase refrigerant is heat-exchanged with the surrounding air and water in the use-side heat exchanger 4 to become a low-temperature and low-pressure superheated gas state, passes through the gas pipe 7, and again enters the compressor 1. Inhaled.
- the bypass circuit 11 connected to both ends of the means 2 for cooling the refrigerant using the first heat source that is lower than the outside air dew point temperature converts a part of the refrigerant that has become high temperature and high pressure superheated gas in the compressor 1 to the outside air dew point temperature.
- the second means for cooling the refrigerant using the first heat source that is below the outside air dew point temperature is bypassed by branching upstream of the means 2 for cooling the refrigerant using the first heat source that is less than
- the cooled refrigerant flowing from the means 2 for cooling the refrigerant using one heat source and the refrigerant using the first heat source below the outside air dew point temperature are merged downstream of the means 2 for cooling and sent to the liquid pipe 5.
- the flow rate of the refrigerant branched to the bypass circuit 11 is, for example, the flow path resistance (tube diameter, length) of the means 2 for cooling the refrigerant using the first heat source that is lower than the outside air dew point temperature and the flow path of the bypass circuit 11. It is adjusted by the ratio with the resistance (tube diameter, length).
- the bypass circuit 11 (sub-refrigerant circuit) is provided in the main refrigerant circuit, and the high-temperature and high-pressure liquid refrigerant and the superheated gas are merged, thereby adjusting the temperature of the liquid refrigerant to the liquid pipe.
- the ambient temperature around 5 can be higher.
- the temperature of the liquid refrigerant is set higher than the temperature of the outside air to prevent condensation on the liquid pipe 5, but the present invention is not limited to this. For example, even if the temperature of the liquid refrigerant is higher than the dew point temperature of the outside air, it is possible to prevent the occurrence of condensation.
- the use side expansion valve 3 corresponds to the “first decompression device” of the present invention
- the use side heat exchanger 4 corresponds to the “evaporator” of the present invention
- the liquid pipe 5 corresponds to the “refrigerant pipe between the means for cooling the refrigerant using the first heat source below the outside air dew point temperature and the first pressure reducing device” of the present invention.
- Embodiment 2 a supercooled refrigerant circuit is added to the refrigerant circuit of the first embodiment.
- the basic configuration of the main refrigerant circuit is the same as the configuration of the main refrigerant circuit in the first embodiment. Therefore, the present embodiment will be mainly described below with respect to the differences from the first embodiment. 2 will be described.
- the refrigerant circuit 100 of the refrigeration air conditioner includes a supercooling refrigerant circuit 30.
- the subcooling refrigerant circuit 30 is configured such that the expansion device 12, the heat exchanger 13, and the refrigerant pipe 14 are connected in order.
- the inlet of the bypass circuit 11 is provided between the outlet side of the condenser 6 and the refrigerant pipe on the upstream side of the heat exchanger 13, and the outlet of the bypass circuit 11 branches from the refrigerant pipe on the downstream side of the heat exchanger 13. It is provided between the unit 16. Thereby, the bypass circuit 11 is configured to bypass the heat exchanger 13.
- the supercooling refrigerant circuit 30 is connected to the branch portion 16 downstream of the outlet of the bypass circuit 11, and then connected to the heat exchanger 13 via the expansion device 12.
- the heat exchanger 13 is provided between the inlet of the bypass circuit 11 and the outlet of the bypass circuit 11, and the refrigerant decompressed by the expansion device 12 (first refrigerant) and before branching on the outlet side of the condenser 6 Heat exchange with the other refrigerant (second refrigerant).
- the refrigerant heat-exchanged by the heat exchanger 13 is sent out to the injection pipe 1 a of the compressor 1 via the refrigerant pipe 14.
- the compressor 1 causes the medium-temperature / medium-pressure refrigerant flowing from the injection pipe 1 a to flow into an intermediate portion of the compression stroke of the compressor 1.
- the supercooling refrigerant circuit 30 branches a part of the high-temperature and high-pressure liquid refrigerant that has come out of the condenser 6 at the branching section 16 and causes the refrigerant to flow through the expansion device 12.
- the expansion device 12 is a variable flow rate adjusting valve that controls the flow rate, and causes the high-temperature and high-pressure liquid refrigerant to flow through the heat exchanger 13 as a medium-temperature and medium-pressure gas-liquid two-phase refrigerant (second heat source).
- the heat exchanger 13 exchanges heat between the high-temperature and high-pressure liquid refrigerant that has flowed out of the condenser 6 and the medium-temperature and medium-pressure gas-liquid refrigerant (second heat source) that flows in the supercooled refrigerant circuit 30. Subcooling is added to the liquid refrigerant on the outlet side 6. Thereafter, the refrigerant flowing through the supercooled refrigerant circuit 30 flows into the refrigerant pipe 14.
- the refrigerant (medium-temperature / medium-pressure refrigerant) that flows into the refrigerant pipe 14 flows into the middle part of the compression stroke of the compressor 1 through the injection pipe 1a. Thereby, the compressor 1 can be cooled and the discharge refrigerant temperature and the motor temperature of the compressor 1 can be lowered.
- the refrigerant in the refrigerant circuit 100 is compressed into a high-temperature and high-pressure superheated gas by the compressor 1, is then heat-exchanged with the first heat source in the condenser 6, and is condensed into a high-temperature and high-pressure liquid refrigerant.
- the liquid refrigerant exiting the condenser 6 is supercooled at a high pressure by the heat exchanger 13 of the supercooling refrigerant circuit 30 as described above.
- the bypass circuit 11 branches a part of the refrigerant that has become high-temperature and high-pressure superheated gas in the compressor 1 on the downstream side of the condenser 6 to bypass the heat exchanger 13, and is cooled by flowing from the heat exchanger 13.
- the refrigerant is combined with the downstream side of the heat exchanger 13 and sent to the liquid pipe 5.
- the refrigerant sent to the liquid pipe 5 passes through the use side expansion valve 3 and becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant.
- the heat is exchanged with the air and water to form a low-temperature and low-pressure superheated gas state, and is sucked into the compressor 1 again.
- the high-temperature and high-pressure liquid refrigerant that has passed through the condenser 6 is largely supercooled by the heat exchanger 13 of the supercooling refrigerant circuit 30. Even when the temperature of the liquid refrigerant is equal to or lower than the temperature of the outside air, the temperature of the liquid refrigerant is made higher than the temperature of the outside air around the liquid pipe 5 by joining the high-temperature and high-pressure liquid refrigerant by the bypass circuit 11. Can be high.
- the expansion device 12 corresponds to the “second decompression device” of the present invention.
- the refrigerant on the downstream side of the expansion device 12 of the subcooling refrigerant circuit 30 corresponds to the “first refrigerant” of the present invention, and the refrigerant on the outlet side of the condenser 6 (high temperature / high pressure liquid refrigerant).
- the liquid pipe 5 corresponds to the “refrigerant pipe between the condenser and the first pressure reducing device” of the present invention.
- Embodiment 3 FIG.
- a variable flow rate adjusting valve or a switching valve that can be opened and closed is added to the bypass circuit 11 of the second embodiment.
- the basic configuration of the refrigerant circuit 100 is the same as the configuration of the refrigerant circuit 100 in the second embodiment. Therefore, the present embodiment will be mainly described below with respect to the differences from the second embodiment. 3 will be described.
- the refrigerant circuit 100 of the refrigeration air conditioner further includes a valve 15 in the bypass circuit 11 that bypasses the heat exchanger 13.
- the valve 15 of the bypass circuit 11 is a variable flow rate adjusting valve that controls the flow rate of the refrigerant, or a switching valve that can open and close the flow path of the refrigerant.
- valve 15 of the bypass circuit 11 When the temperature of the liquid refrigerant in the liquid pipe 5 exceeds the ambient outside air temperature, the liquid pipe 5 does not condense, so the valve 15 of the bypass circuit 11 is closed. However, when the temperature of the liquid refrigerant in the liquid pipe 5 is equal to or lower than the ambient outside air temperature, the valve 15 of the bypass circuit 11 is opened to allow the high-temperature and high-pressure liquid refrigerant to flow to the bypass circuit 11. Thereby, the temperature of the liquid refrigerant is raised so as to exceed the ambient temperature of the surroundings, and condensation of the liquid pipe 5 is prevented.
- the flow rate of the refrigerant flowing through the bypass circuit 11 can be finely adjusted.
- the temperature is higher than the ambient temperature (or dew point temperature) and can be controlled in the vicinity of that temperature.
- the switching valve that can be opened and closed is fully closed or the variable flow rate adjustment valve that controls the flow rate of the refrigerant is controlled to be fully closed, the refrigerant does not pass through the bypass circuit 11.
- the refrigerant does not pass through the bypass circuit 11.
- the refrigerating and air-conditioning apparatus adjusts the flow rate of the refrigerant with the valve 15 of the bypass circuit 11 and condenses with the condenser 6 when the local liquid piping 5 cannot be insulated.
- the liquid refrigerant that has been supercooled by the heat exchanger 13 is merged with the liquid refrigerant that has been added. Thereby, the temperature of the liquid refrigerant can be made higher than the outside air temperature around the liquid pipe 5, and condensation can be prevented from occurring in the liquid pipe 5.
- the valve 15 of the bypass circuit 11 is used. Is fully closed, and all of the high-temperature and high-pressure liquid refrigerant discharged from the condenser 6 is supercooled by the heat exchanger 13, so that the liquid refrigerant can be largely subcooled. Thereby, the cooling capacity of the refrigeration air conditioner is increased, and energy saving can be ensured.
- Embodiment 4 the opening degree of the valve 15 of the bypass circuit 11 of the third embodiment is automatically controlled. Since the configuration of the refrigerant circuit 100 of the fourth embodiment is the same as the configuration of the third embodiment, the fourth embodiment will be described below with a focus on differences from the third embodiment.
- the refrigerant circuit 100 of the fourth embodiment further includes an outside air temperature sensor 31, a refrigerant temperature sensor 32, and a flow rate control device 33.
- the flow control device 33 is configured by, for example, a microcomputer.
- the outside air temperature sensor 31 detects the surrounding outside air temperature, and the flow rate control device 33 takes in the outside air temperature data from the outside air temperature sensor 31.
- the refrigerant temperature sensor 32 detects the temperature of the liquid refrigerant flowing through the liquid pipe 5, and the flow rate control device 33 takes in the temperature data of the liquid refrigerant from the refrigerant temperature sensor 32.
- the opening degree of the valve 15 of the bypass circuit 11 corresponding to the outside air temperature and the liquid refrigerant temperature is stored in advance in the table, and based on the data of the taken outside air temperature and liquid refrigerant temperature With reference to the table, the opening degree of the valve 15 of the bypass circuit 11 is obtained, and the valve 15 is controlled based on the opening degree.
- FIG. 5 is a flowchart showing the control operation of the flow control device 33.
- S1 Start the refrigeration air conditioner.
- S2 The flow rate control device 33 of the bypass circuit 11 takes in information on the outside air temperature around the liquid pipe 5 from the outside air temperature sensor 31 and takes in information on the temperature of the liquid refrigerant flowing through the liquid pipe 5 from the refrigerant temperature sensor 32.
- S3 Compare the outside air temperature and the liquid refrigerant temperature. When outside temperature is more than liquid refrigerant temperature, it shifts to Step S4. Otherwise, the process proceeds to step S5.
- valve 15 and the flow rate control device 33 are provided in the bypass circuit 11 to control the opening degree of the valve 15, and the liquid refrigerant condensed by the condenser 6 and the supercooled liquid added by the heat exchanger 13.
- the temperature of the liquid refrigerant can be made higher than the outside air temperature around the liquid pipe 5.
- the flow rate control device 33 of the bypass circuit 11 is provided and the amount of refrigerant flowing through the circuit bypassing the heat exchanger 13 is controlled, the liquid refrigerant temperature can be controlled near the outside air temperature, and the liquid pipe 5 It is possible to obtain a refrigeration air conditioner that can prevent condensation.
- the opening degree of the valve 15 of the bypass circuit 11 is controlled by comparing the outside air temperature and the liquid refrigerant temperature.
- the present invention is not limited to this, for example, the outside air temperature sensor 31 Instead, a dew point temperature of the outside air may be obtained using a dew point meter, and the opening degree of the valve 15 of the bypass circuit 11 may be controlled by comparing the dew point temperature of the outside air with the liquid refrigerant temperature.
- 1 Compressor 1a Injection piping
- 3 Usage side expansion valve 4 Usage side heat exchanger
- 5 Liquid piping 6 Condenser, 7 Gas Piping, 11 Bypass circuit, 12 Throttle device, 13 Heat exchanger, 14 Refrigerant piping, 15 Valve, 16 Branch, 20 Local connection liquid piping, 21 Local connection gas piping, 30 Supercooling refrigerant circuit, 31 Outside air temperature sensor, 32 Refrigerant temperature sensor, 33 flow control device, 100 refrigerant circuit.
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- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
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- Air Conditioning Control Device (AREA)
- Other Air-Conditioning Systems (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
図1は、本発明の実施の形態1に係る冷凍空調装置の冷媒回路図である。
図1に示されるように、冷凍空調装置の冷媒回路100は、圧縮機1、外気露点温度を下回る第一の熱源を用いた冷媒を冷却する手段2、利用側膨張弁3及び利用側熱交換器4が冷媒配管を介して環状に接続された構成となっている。これらの構成からなる回路を主冷媒回路と呼ぶ。
冷媒回路100内の冷媒は、圧縮機1において高温高圧の過熱ガスに圧縮された後、外気露点温度を下回る第一の熱源を用いた冷媒を冷却する手段2へ送られる。外気露点温度を下回る第一の熱源を用いた冷媒を冷却する手段2を通過する冷媒は、上記の第一の熱源と熱交換を行うことで高温高圧の液冷媒に凝縮される。そして、液冷媒は、液配管5を通過し、利用側膨張弁3に通されて低温低圧の気液2相冷媒となる。低温低圧の気液2相冷媒は、利用側熱交換器4内で周囲の空気や水と熱交換されて低温低圧の過熱ガスの状態となり、ガス配管7を通過し、再度、圧縮機1に吸入される。この一連の動作を行うことで、主冷媒回路の冷媒サイクルが構成されている。
このため、本実施の形態1によれば、従来の問題点、つまり、液配管5の表面温度が周囲の外気の露点温度を下回る場合に、液配管5の表面に結露が生じ、液配管5が配置されている天井裏などに結露水が垂れ、天井裏や室内が水浸しになったり、カビが発生する、という従来の問題点が解消されている。
本実施の形態2は、上記の実施の形態1の冷媒回路に過冷却冷媒回路を付加したものである。本実施の形態2において、主冷媒回路の基本的な構成は、実施の形態1における主冷媒回路の構成と同様であるため、以下、実施の形態1との相違点を中心に本実施の形態2を説明する。
バイパス回路11の入口は、凝縮器6の出側と熱交換器13の上流側の冷媒配管との間に設けられ、バイパス回路11の出口は、熱交換器13の下流側の冷媒配管と分岐部16との間に設けられている。これにより、バイパス回路11は、熱交換器13をバイパスする構成となっている。
過冷却冷媒回路30は、バイパス回路11の出口の下流にある分岐部16と接続され、その後、絞り装置12を経由して熱交換器13に接続される。熱交換器13は、バイパス回路11の入口とバイパス回路11の出口との間に設けられ、絞り装置12で減圧された冷媒(第一の冷媒)と、凝縮器6の出側の分岐する前の冷媒(第二の冷媒)とを熱交換する。熱交換器13で熱交換された冷媒は、冷媒配管14を経由して、圧縮機1が有するインジェクション配管1aに送り出される。圧縮機1は、インジェクション配管1aから流入した中温中圧の冷媒を、圧縮機1の圧縮行程の中間部分に流入させる。
まず、過冷却冷媒回路30の動作について説明する。
過冷却冷媒回路30は、凝縮器6から出た高温高圧の液冷媒の一部を分岐部16で分岐し、絞り装置12に冷媒を流す。絞り装置12は、流量を制御する可変式の流量調整弁であり、高温高圧の液冷媒を中温中圧の気液2相の冷媒(第二の熱源)として、熱交換器13に流す。熱交換器13は、凝縮器6から流出した高温高圧の液冷媒と、過冷却冷媒回路30を流れる中温中圧の気液2相の冷媒(第二の熱源)とを熱交換させ、凝縮器6の出側の液冷媒に過冷却を付加する。その後、過冷却冷媒回路30を流れる冷媒は、冷媒配管14に流入する。
冷媒回路100内の冷媒は、圧縮機1にて高温高圧の過熱ガスに圧縮された後、凝縮器6において第一の熱源と熱交換されて、高温高圧の液冷媒に凝縮される。凝縮器6を出た液冷媒は、上記のように、過冷却冷媒回路30の熱交換器13によって高圧で過冷却が付加される。
また、バイパス回路11は、圧縮機1で高温高圧の過熱ガスとなった冷媒の一部を凝縮器6の下流側で分岐して熱交換器13をバイパスし、熱交換器13から流れる冷却された冷媒と熱交換器13の下流側で合流させ、液配管5へ送る。
その後は、上記の実施の形態1と同様に、液配管5に送られた冷媒は、利用側膨張弁3を通り、低温低圧の気液2相冷媒となり、利用側熱交換器4内で周囲の空気や水と熱交換されて低温低圧の過熱ガスの状態となり、再度圧縮機1に吸入される。
また、過冷却冷媒回路30内の冷媒を圧縮機1に戻すようにしているので、過冷却冷媒回路30の絞り装置12で中温中圧にされ、熱交換器13にて主冷媒回路の冷媒と熱交換した冷媒を圧縮機1に入れ、圧縮機1を冷却することができる。
本実施の形態3は、上記の実施の形態2のバイパス回路11に可変式の流量調整弁又は開閉可能な切替弁を付加したものである。本実施の形態3において、冷媒回路100の基本的な構成は、実施の形態2における冷媒回路100の構成と同様であるため、以下、実施の形態2との相違点を中心に本実施の形態3を説明する。
液配管5の中の液冷媒の温度が、周囲の外気温度を上回る場合には、液配管5は結露しないため、バイパス回路11の弁15を閉める。
しかし、液配管5の中の液冷媒の温度が、周囲の外気温度以下となる場合には、バイパス回路11の弁15を開けて、高温高圧の液冷媒をバイパス回路11に流す。これにより、液冷媒の温度を上げ、周囲の外気温度を上回るようにし、液配管5の結露を防止する。
本実施の形態4は、上記の実施の形態3のバイパス回路11の弁15の開度を自動的に制御するようにしたものである。本実施の形態4の冷媒回路100の構成は、実施の形態3の構成と同様であるため、以下、実施の形態3との相違点を中心に本実施の形態4を説明する。
(S1)
冷凍空調装置を起動する。
(S2)
バイパス回路11の流量制御装置33が、外気温度センサ31から液配管5の周囲の外気温度の情報を取り込むと共に、冷媒温度センサ32から液配管5を流れる液冷媒温度の情報を取り込む。
(S3)
外気温度と液冷媒温度を比較する。外気温度が液冷媒温度以上の場合は、ステップS4へ移行する。それ以外は、ステップS5へ移行する。
(S4)
バイパス回路11の弁15を開き、バイパス回路11に流れる冷媒量を増やし、液冷媒温度を上げる。
(S5)
バイパス回路11の弁15を閉じ、バイパス回路11に流れる冷媒量を減らし、液冷媒温度を下げ、液冷媒温度を外気温度付近に調整する。
Claims (13)
- 圧縮機、外気露点温度を下回る第一の熱源を用いた冷媒を冷却する手段、第一の減圧装置及び蒸発器が、冷媒配管を介して環状に接続された主冷媒回路と、
前記外気露点温度を下回る第一の熱源を用いた冷媒を冷却する手段の入側の冷媒配管と出側の冷媒配管との間に接続されたバイパス回路と、
を備え、
前記バイパス回路は、前記圧縮機から吐出された冷媒の一部を、前記外気露点温度を下回る第一の熱源を用いた冷媒を冷却する手段をバイパスして前記外気露点温度を下回る第一の熱源を用いた冷媒を冷却する手段の出側の冷媒配管へ送る、
冷凍空調装置。 - 前記バイパス回路は、前記外気露点温度を下回る第一の熱源を用いた冷媒を冷却する手段と前記第一の減圧装置との間の冷媒配管内の冷媒の温度が、周囲の外気の露点温度より高くなるように、前記圧縮機から吐出された冷媒の一部を前記凝縮器の出側の冷媒配管へ送る、
請求項1に記載の冷凍空調装置。 - 前記バイパス回路は、前記外気露点温度を下回る第一の熱源を用いた冷媒を冷却する手段と前記第一の減圧装置との間の冷媒配管内の冷媒の温度が、周囲の外気の温度より高くなるように、前記圧縮機から吐出された冷媒の一部を前記凝縮器の出側の冷媒配管へ送る、
請求項1に記載の冷凍空調装置。 - 前記外気露点温度を下回る第一の熱源を用いた冷媒を冷却する手段は、水道水、地下水、地熱又は別の冷凍装置の蒸発器と熱交換する、
請求項1~3の何れか一項に記載の冷凍空調装置。 - 圧縮機、凝縮器、第一の減圧装置及び蒸発器が、冷媒配管を介して環状に接続された主冷媒回路と、
前記凝縮器の出側の冷媒を更に冷却する熱交換器を備えた過冷却冷媒回路と、
前記熱交換器の上流側の冷媒配管と前記熱交換器の下流側の冷媒配管との間に接続され、前記熱交換器をバイパスするバイパス回路と、
を備え、
前記バイパス回路は、前記凝縮器で凝縮された冷媒の一部を、前記熱交換器をバイパスして前記熱交換器の下流側の冷媒配管へ送る、
冷凍空調装置。 - 前記圧縮機は、インジェクション配管を有し、
前記過冷却冷媒回路は、
前記バイパス回路の出口と前記第一の減圧装置との間から分岐した第一の冷媒を減圧する第二の減圧装置と、
前記第二の減圧装置から送られた前記第一の冷媒と、前記凝縮器を出た第二の冷媒とで熱交換を行い、前記第二の冷媒を過冷却する前記熱交換器と、
を備え、
前記熱交換器で熱交換された前記第一の冷媒を前記圧縮機のインジェクション配管へ送る、
請求項5に記載の冷凍空調装置。 - 前記第二の減圧装置は、流量を制御する可変式の流量調整弁である、
請求項6に記載の冷凍空調装置。 - 前記バイパス回路は、前記凝縮器と前記第一の減圧装置との間の冷媒配管内の冷媒の温度が、周囲の外気の露点温度より高くなるように、前記凝縮器で凝縮された冷媒の一部を前記熱交換器の下流側の冷媒配管へ送る、
請求項5~7の何れか一項に記載の冷凍空調装置。 - 前記バイパス回路は、前記凝縮器と前記第一の減圧装置との間の冷媒配管内の冷媒の温度が、周囲の外気の温度より高くなるように、前記凝縮器で凝縮された冷媒の一部を前記熱交換器の下流側の冷媒配管へ送る、
請求項5~7の何れか一項に記載の冷凍空調装置。 - 前記バイパス回路は、冷媒の流量を調整する可変式の流量調整弁又は開閉可能な切替弁を備えた、
請求項5~9の何れか一項に記載の冷凍空調装置。 - 前記凝縮器と前記第一の減圧装置との間の冷媒配管内の冷媒の温度を検出する冷媒温度センサと、
外気の温度を検出する外気温度センサと、
前記冷媒温度センサによって検出された前記冷媒の温度と、前記外気温度センサによって検出された前記外気の温度とに基づいて前記流量調整弁又は前記切替弁を制御する流量制御装置と、
を更に備えた、
請求項10に記載の冷凍空調装置。 - 前記流量制御装置は、前記液配管内の冷媒が周囲の外気の露点温度より高くなるように、前記バイパス回路を流通する冷媒の流量を調整する、
請求項11に記載の冷凍空調装置。 - 前記流量制御装置は、前記液配管内の冷媒が周囲の外気の温度より高くなるように、前記バイパス回路を流通する冷媒の流量を調整する、
請求項11に記載の冷凍空調装置。
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