WO2016185568A1 - 冷凍装置 - Google Patents
冷凍装置 Download PDFInfo
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- WO2016185568A1 WO2016185568A1 PCT/JP2015/064363 JP2015064363W WO2016185568A1 WO 2016185568 A1 WO2016185568 A1 WO 2016185568A1 JP 2015064363 W JP2015064363 W JP 2015064363W WO 2016185568 A1 WO2016185568 A1 WO 2016185568A1
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- refrigerant
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- refrigerant circuit
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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
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
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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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
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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
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
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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
- F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
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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
- F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
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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
- F25B2400/0415—Refrigeration circuit bypassing means for the receiver
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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
- F25B2400/16—Receivers
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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
- F25B2600/25—Control of valves
- F25B2600/2523—Receiver valves
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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
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction pressures
Definitions
- the present invention relates to a refrigeration apparatus having a first refrigerant circuit and a second refrigerant circuit.
- Patent Document 1 a binary refrigeration apparatus that exchanges heat between an evaporator of a high temperature side refrigeration cycle and a condenser of a low temperature side refrigeration cycle is known (see Patent Document 1).
- the binary refrigeration apparatus described in Patent Document 1 the refrigerant in the low temperature side refrigeration cycle condensed by the condenser is cooled to the supercooled state by the subcooler.
- the subcooling coil and the cascade capacitor are connected in series in the first refrigerant circuit, and the second refrigerant circuit is connected to the subcooling coil of the first refrigerant circuit.
- the 1st refrigerant which cooled the 2nd refrigerant has condensed the 2nd refrigerant of the 2nd refrigerant circuit with a cascade capacitor. Therefore, in the refrigeration apparatus described in Patent Document 1, in the first refrigerant circuit, the saturation temperature of the first refrigerant that cools the second refrigerant in the second refrigerant circuit with the subcool coil is the second refrigerant circuit with the cascade capacitor. This is higher than the saturation temperature of the first refrigerant that condenses the second refrigerant.
- An object of the present invention is to obtain a refrigeration apparatus having an improved degree of freedom in adjusting the saturation temperature of the first refrigerant for cooling the second refrigerant in the two refrigerant circuit.
- a refrigeration apparatus includes a first refrigerant circuit that circulates a first refrigerant and a second refrigerant circuit that circulates a second refrigerant, and the first refrigerant circuit compresses the first refrigerant.
- a first condenser that condenses the first refrigerant compressed by the first compressor, a first main expansion device that expands the first refrigerant condensed by the first condenser, and expansion by the first main expansion device
- a first sub-expansion device connected in parallel with the evaporation section and expanding the first refrigerant condensed by the first condenser, and the first refrigerant expanded by the first sub-expansion device exchange heat with the second refrigerant.
- a second main refrigerant circuit connected to the two sub-condensing units.
- the saturation temperature of the first refrigerant that cools the second refrigerant in the second refrigerant circuit by the subcool coil, and the first refrigerant that cools the second refrigerant in the second refrigerant circuit by the cascade capacitor can be obtained.
- FIG. 1 is a diagram schematically illustrating an example of the configuration of the refrigeration apparatus according to Embodiment 1 of the present invention.
- the refrigeration apparatus 100 includes a first refrigerant circuit 50 through which a first refrigerant circulates and a second refrigerant circuit 60 through which a second refrigerant circulates.
- the cooling target is cooled using the second evaporator 16 of the second refrigerant circuit 60.
- the refrigeration apparatus 100 includes a pressure detection device 20 and a control device 21.
- the pressure detection device 20 detects a low pressure v that is the pressure on the suction side of the second compressor 7 of the second refrigerant circuit 60.
- the control device 21 is configured to include an analog circuit, a digital circuit, a CPU, or a combination of two or more thereof, and opens and closes the first opening / closing device 11 using at least the detection result of the pressure detection device 20. It is something to control.
- the control device 21 can also control other configurations as described below.
- FIG. 1 in order to facilitate understanding of this embodiment, the pipes connecting the respective configurations of the first refrigerant circuit 50 are indicated by solid lines, and the respective configurations of the second refrigerant circuit 60 are connected. The piping is shown with dotted lines.
- the first refrigerant circuit 50 includes a first main refrigerant circuit 52 and a first sub refrigerant channel 54.
- the 1st main refrigerant circuit 52 contains the 1st compressor 1, the 1st condenser 2, the 1st main expansion device 3, and the 1st main evaporation part 5 of the cascade condenser 18, and these are connected by piping.
- the first compressor 1 compresses the first refrigerant.
- the first compressor 1 is, for example, an inverter compressor that is controlled by an inverter, and can change the capacity (the amount of refrigerant sent out per unit time) by arbitrarily changing the operating frequency.
- the first compressor 1 may be a constant speed compressor that operates at a constant operating frequency.
- the first condenser 2 causes the first refrigerant flowing through the first condenser 2 to exchange heat with air to condense the first refrigerant.
- the first main expansion device 3 expands the first refrigerant.
- the first main expansion device 3 is an electronic expansion valve whose opening degree can be adjusted, but may be a capillary tube or the like.
- the cascade condenser 18 exchanges heat between the first refrigerant and the second refrigerant.
- the first main evaporator 5 through which the first refrigerant in the first refrigerant circuit 50 flows and the second refrigerant in the second refrigerant circuit 60 are exchanged. And a flowing second main condensing unit 8.
- the 1st main evaporation part 5 makes the 1st refrigerant
- the first sub refrigerant flow path 54 connects between the first condenser 2 and the first main expansion device 3 and between the first main evaporator 5 and the first compressor 1.
- the 1 main expansion device 3 and the first main evaporation unit 5 are connected in parallel.
- the first sub refrigerant channel 54 is provided with the first sub expansion device 4 and the first sub evaporation unit 6 of the sub cool coil 19.
- the first sub expansion device 4 expands the first refrigerant and is, for example, an electronic expansion valve capable of adjusting the opening degree, but may be a capillary tube or the like.
- the subcooling coil 19 exchanges heat between the first refrigerant and the second refrigerant, and the first sub-evaporating unit 6 through which the first refrigerant in the first refrigerant circuit 50 flows and the second refrigerant in the second refrigerant circuit 60 are exchanged. And a second sub-condensing unit 13 that flows.
- the first sub-evaporating unit 6 causes the first refrigerant flowing through the first sub-evaporating unit 6 to exchange heat with the second refrigerant flowing through the second sub-condensing unit 13 to evaporate the first refrigerant.
- the second refrigerant circuit 60 includes a second main refrigerant circuit 62, a bypass flow path 64, and an injection flow path 66.
- the second main refrigerant circuit 62 includes a second compressor 7, a second main condenser 8 of the cascade condenser 18, a first opening / closing device 11, a receiver 9, a check valve 12, and a second sub condenser of the subcool coil 19. 13, a second opening / closing device 14, a second expansion device 15, and a second evaporator 16, which are connected by piping.
- the second compressor 7 compresses the second refrigerant.
- the second compressor 7 is, for example, an inverter compressor that is controlled by an inverter, and can change the capacity (amount of refrigerant sent out per unit time) by arbitrarily changing the operating frequency.
- the second compressor 7 may be a constant speed compressor that operates at a constant operating frequency.
- the second main condensing unit 8 heat-exchanges the second refrigerant flowing through the second main condensing unit 8 with the first refrigerant flowing through the first main evaporating unit 5 to condense the second refrigerant.
- the first opening / closing device 11 is, for example, an electromagnetic valve that controls the passage of the second refrigerant by performing an opening / closing operation.
- the liquid receiver 9 is, for example, a container for storing a refrigerant.
- the check valve 12 allows the refrigerant flowing out of the liquid receiver 9 to pass therethrough and prevents the refrigerant from flowing into the liquid receiver 9 through the check valve 12.
- the second sub-condensing unit 13 cools the second refrigerant by exchanging heat between the second refrigerant flowing through the second sub-condensing unit 13 and the first refrigerant flowing through the first sub-evaporating unit 6.
- the second opening / closing device 14 is, for example, an electromagnetic valve that controls the passage of the second refrigerant by performing an opening / closing operation.
- the second expansion device 15 expands the second refrigerant.
- the second expansion device 15 is an electronic expansion valve whose opening degree can be adjusted, but may be a capillary tube or the like.
- the second evaporator 16 causes the second refrigerant flowing through the second evaporator 16 to exchange heat with air, thereby evaporating the second refrigerant.
- the bypass flow path 64 connects between the second main condensing unit 8 and the first opening / closing device 11 and between the check valve 12 and the second sub-condensing unit 13.
- the liquid receiver 9 and the check valve 12 are connected in parallel.
- the injection flow channel 66 connects between the second sub-condensing unit 13 and the second opening / closing device 14 and between the second evaporator 16 and the second compressor 7.
- the second expansion device 15 and the second evaporator 16 are connected in parallel.
- An injection expansion device 17 is disposed in the injection flow channel 66.
- the injection expansion device 17 expands the second refrigerant and is, for example, an electronic expansion valve capable of adjusting the opening degree, but may be a capillary tube or the like.
- FIG. 2 is a diagram illustrating a refrigerant used in the refrigeration apparatus illustrated in FIG. 1.
- a refrigerant having a low GWP global warming potential
- a refrigerant having a low GWP is selected as the refrigerant used in the second refrigerant circuit 60. Because the second refrigerant circuit 60 shown in FIG.
- the 1 includes, for example, an indoor unit (not shown) that includes the second opening / closing device 14, the second expansion device 15, and the second evaporator 16, and The outdoor unit unitized including the second compressor 7, the second main condensing unit 8, the first opening / closing device 11, the liquid receiver 9, the check valve 12, the second sub-condensing unit 13, and the injection expansion device 17. And a unit (not shown).
- the indoor unit and the outdoor unit that are not shown are connected and constructed by an operator at the site where the refrigeration apparatus 100 is installed. It is known that the refrigerant may leak from a portion where an indoor unit and an outdoor unit that are not shown are connected. Therefore, in the second refrigerant circuit 60 of the example of this embodiment, for example, CO2 (carbon dioxide) having a low GWP is employed.
- coolant used for the 2nd refrigerant circuit 60 is not limited to CO2, What is necessary is just to select a thing with low GWP.
- the first refrigerant used in the first refrigerant circuit 50 a refrigerant having higher efficiency (COP) than that in the case where the second refrigerant is circulated through the first refrigerant circuit 50 is selected. That is, in the operating condition of the first refrigerant circuit 50, the first refrigerant has higher efficiency than the second refrigerant. This is because the unit (not shown) including the first refrigerant circuit 50 is assembled by a manufacturer (manufacturer), and the first refrigerant circuit 50 is inspected for airtightness and shipped. Since the first refrigerant circuit 50 is less likely to leak the refrigerant than the second refrigerant circuit 60, it is possible to select a refrigerant with high efficiency. Preferably, the first refrigerant also has a low GWP.
- the refrigerant having a low GWP is used in the second refrigerant circuit 60 in which the refrigerant may leak, measures against global warming and the like are taken. Furthermore, in the example of this embodiment, since the refrigerant having high efficiency is used in the first refrigerant circuit 50 in which the risk of leakage of the refrigerant is reduced, the entire first refrigerant circuit 50 and the entire refrigeration apparatus 100 are used. Efficiency (COP) is improved.
- FIG. 3 is a diagram for explaining an example of the operation of the first refrigerant circuit and the second refrigerant circuit shown in FIG.
- coolant compressed with the 1st compressor 1 becomes the position of the point B of FIG.
- the first refrigerant compressed by the first compressor 1 in FIG. 1 is heat-exchanged and condensed by the first condenser 2 and becomes a position of a point C in FIG.
- the first refrigerant that has flowed into the first main expansion device 3 is expanded by the first main expansion device 3 to a position of a point D in FIG.
- the first refrigerant expanded in the first main expansion device 3 in FIG. 1 is heat-exchanged and evaporated in the first main evaporation unit 5 and merges with the first refrigerant that has passed through the first sub-evaporation unit 6.
- the position of the point A is 3.
- the first refrigerant expanded by the first sub-expansion device 4 in FIG. 1 is heat-exchanged by the first sub-evaporating unit 6 and evaporated, and merges with the first refrigerant that has passed through the first main evaporation unit 5.
- the position of the point A is 3.
- the first refrigerant at point A is compressed again by the first compressor 1 in FIG.
- the flow rate of the first refrigerant flowing in the first main expansion device 3 and the first main evaporation unit 5 by adjusting the opening degree of at least one of the first main expansion device 3 and the first sub expansion device 4. And the flow rate of the first refrigerant flowing through the first sub expansion device 4 and the first sub evaporation unit 6 can be adjusted.
- the second refrigerant compressed by the second compressor 7 is located at a point F in FIG.
- the second refrigerant compressed by the second compressor 7 in FIG. 1 is heat-exchanged and condensed by the second main condensing unit 8, and becomes a point H in FIG. 3.
- coolant condensed by the 2nd main condensation part 8 is 1st switchgear. 11, except that it flows through the liquid receiver 9 and the check valve 12 and flows into the second sub-condensing unit 13. Therefore, in the following, the description overlapping with the above will be omitted or simplified.
- the second refrigerant condensed in the second main condensing unit 8 is located at a point H in FIG.
- the second refrigerant is radiated by the liquid receiver 9 and becomes the position of point G in FIG.
- the second refrigerant that has flowed out of the liquid receiver 9 in FIG. 1 passes through the check valve 12 and is heat-exchanged in the second sub-condensing unit 13 to reach the position of point L in FIG.
- the ability exhibited by the second evaporator 16 when the first opening / closing device 11 of FIG. 1 is in the open state and the ability exhibited by the second evaporator 16 when the first opening / closing device 11 is in the closed state. And compare.
- the ability of the second evaporator 16 to be exhibited when the first opening / closing device 11 is in an open state depends on the product of the difference in enthalpy between point L and point E in FIG. 3 and the refrigerant circulation amount through which the second refrigerant circulates. I want.
- the ability of the second evaporator 16 to be exhibited when the first opening / closing device 11 is in a closed state is obtained by the product of the difference in enthalpy between the point K and the point E and the refrigerant circulation amount through which the second refrigerant circulates. . Therefore, if the refrigerant circulation amount of the second refrigerant is the same, the ability to be exhibited by the second evaporator 16 is greater when the first opening / closing device 11 is in the closed state and the second refrigerant is not passed through the liquid receiver 9. . This is because the heat dissipation of the second refrigerant in the liquid receiver 9 is avoided by flowing the second refrigerant through the bypass flow path 64.
- the bypass flow path 64 is set so that the ability of the second evaporator 16 is increased. Pour the second refrigerant.
- the second sub-condensing unit 13 performs heat exchange.
- a part of the two refrigerants (point K in FIG. 3) is expanded by the injection expansion device 17 and mixed with the second refrigerant evaporated by the second evaporator 16 to lower the temperature at the point E in FIG. .
- the temperature at the point E in FIG. 3 is lowered, the temperature of the discharge temperature of the second compressor 7 (the point F in FIG. 3) can be lowered.
- the second opening / closing device 14 when the cooling of the object to be cooled performed by the refrigeration apparatus 100 becomes unnecessary, that is, when the cooling using the second evaporator 16 becomes unnecessary, the second opening / closing device 14 is closed.
- the pressure on the low pressure side of the second compressor 7 from the second opening / closing device 14 to the second compressor 7 decreases.
- the pressure on the low pressure side of the second compressor 7 decreases to a preset set pressure, the second compressor 7 stops operating.
- the second refrigerant circuit 60 includes an indoor unit (not shown) including, for example, the second opening / closing device 14, the second expansion device 15, and the second evaporator 16.
- the outdoor unit (not shown) is configured, and the indoor unit and the outdoor unit are controlled independently. As shown below, the opening and closing of the first opening / closing device 11 is controlled using the pressure on the low pressure side of the second compressor 7, and the second refrigerant is stored in the liquid receiver 9, so that the illustration is omitted. It can suppress that the 2nd refrigerant circuit 60 will be in an abnormal state by the outdoor unit side.
- FIG. 4 is a diagram illustrating an opening / closing threshold value for determining opening / closing of the first opening / closing device illustrated in FIG.
- the opening / closing judgment of the first opening / closing device 11 is performed using the low pressure v on the low pressure side of the second compressor 7.
- the opening / closing threshold value V2 for determining opening / closing of the first opening / closing device 11 includes a target operating pressure value V1 that is a target low pressure v during the normal operation of the second compressor 7 and a low pressure at which the second compressor 7 is stopped. It is set between the stop pressure value V3 which is the pressure v.
- the second opening / closing device 14 is in an open state, and the second compressor 7 is configured so that the second evaporator 16 selects the object to be cooled.
- the low pressure v is controlled so as to be close to the target operating pressure value V1 so as to cool to the target temperature. Therefore, when it is estimated that the low pressure v of the second compressor 7 is controlled to approach the target operating pressure value V1, it is determined that the second opening / closing device 14 is in the open state, and the first opening / closing device 11 Close.
- the second refrigerant does not flow into the liquid receiver 9 but flows through the bypass flow path 64, so that the capacity of the second evaporator 16 increases.
- pressure pressure v will fall. Therefore, when the low pressure v drops below the opening / closing threshold value V2 estimated that the second opening / closing device 14 is closed, the first opening / closing device 11 is opened and the second refrigerant is received by the receiver 9. To store.
- FIG. 5 is a diagram for explaining an example of the operation of the refrigeration apparatus shown in FIG.
- step S1 of FIG. 5 it is determined whether or not the second compressor 7 is operating. If it is determined in step S1 that the second compressor 7 is operating, the process proceeds to step S2.
- step S2 the low pressure v of the second compressor 7 is acquired, and it is determined whether or not the low pressure v of the second compressor 7 is less than or equal to the open / close threshold value V2. If the low pressure v of the second compressor 7 is equal to or lower than the opening / closing threshold value V2 in step S2, the first opening / closing device 11 is opened in step S3.
- step S2 If the low pressure v of the second compressor 7 is larger than the opening / closing threshold value V2 in step S2, the first opening / closing device 11 is closed in step S4. When it is determined in step S1 that the second compressor 7 is not operating, the first opening / closing device 11 is opened in step S5.
- the refrigeration apparatus 100 includes the first refrigerant circuit 50 that circulates the first refrigerant and the second refrigerant circuit 60 that circulates the second refrigerant
- the first refrigerant circuit 50 includes: The first compressor 1 that compresses the first refrigerant, the first condenser 2 that condenses the first refrigerant compressed by the first compressor 1, and the first refrigerant that is condensed by the first condenser 2 are expanded.
- a first main expansion device 3 that causes the first refrigerant expanded in the first main expansion device 3 to exchange heat with the second refrigerant to evaporate the first refrigerant.
- the first main refrigerant circuit 52 connected, the first main expansion device 3 and the first main evaporation unit 5 are connected in parallel, and the first sub expansion device expands the first refrigerant condensed in the first condenser 2. 4 and the first refrigerant expanded by the first sub-expander 4 is used as the second refrigerant.
- the first main evaporator 5 of the cascade condenser 18 and the first sub evaporator 6 of the subcool coil 19 are connected in parallel.
- the degree of freedom in adjusting the saturation temperature of the first refrigerant flowing through the first main evaporator 5 and the saturation temperature of the first refrigerant flowing through the first sub-evaporator 6 is improved.
- the saturation temperature of the first refrigerant flowing through the first sub-evaporating unit 6 is adjusted to be equal to or lower than the saturation temperature of the first refrigerant flowing through the first main evaporation unit 5, so that the refrigeration apparatus 100 efficiency is improved.
- the second main refrigerant circuit 62 of the refrigeration apparatus 100 includes a first opening / closing device 11 that controls passage of the second refrigerant condensed by the second main condensing unit 8, and the first opening / closing device 11.
- a liquid receiver 9 that stores the second refrigerant that has passed through the second sub-condensing unit 13, and a second opening / closing device 14 that controls the passage of the second refrigerant cooled by the second sub-condensing unit 13.
- the refrigeration apparatus 100 includes a pressure detection device 20 that detects a low pressure v on the suction side of the second compressor 7 and a first open / close using the low pressure v detected by the pressure detection device 20. And a control device 21 for controlling the opening and closing of the device 11, and the control device 21 uses the low pressure v to determine the first opening and closing device 11 when it is determined that the second opening and closing device 14 is open. When it is determined that the second opening / closing device 14 is in the closed state, the first opening / closing device 11 is in the open state.
- the refrigeration apparatus 100 when the second opening / closing device 14 is in the open state, the first evaporator 11 is closed and the second refrigerant is allowed to flow through the bypass flow path 64, whereby the second evaporator The ability of 16 can be increased. Further, in the refrigeration apparatus 100 of this embodiment, when the second opening / closing device 14 is in the closed state, the second opening / closing device 11 is opened, and the second refrigerant is stored in the liquid receiver 9, so that the second It can suppress that the refrigerant circuit 60 will be in an abnormal state.
- the present invention is not limited to the above embodiment, and can be variously modified within the scope of the present invention. That is, the configuration of the above embodiment may be improved as appropriate, or at least a part of the configuration may be replaced with another configuration. Further, the configuration requirements that are not particularly limited with respect to the arrangement are not limited to the arrangement disclosed in the embodiment, and can be arranged at a position where the function can be achieved.
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Abstract
Description
[冷凍装置]
図1は、この発明の実施の形態1に係る冷凍装置の構成の一例を模式的に記載した図である。図1に示すように、この実施の形態に係る冷凍装置100は、第1冷媒が循環する第1冷媒回路50と第2冷媒が循環する第2冷媒回路60とを有しており、例えば、第2冷媒回路60の第2蒸発器16を利用して、冷却対象を冷却するものである。また、冷凍装置100は、圧力検出装置20および制御装置21を含んでいる。圧力検出装置20は、第2冷媒回路60の第2圧縮機7の吸入側の圧力である低圧圧力vを検出するものである。制御装置21は、アナログ回路、デジタル回路、CPU、またはこれらのうちの2つ以上の組み合わせを含んで構成されており、少なくとも圧力検出装置20の検出結果を用いて第1開閉装置11の開閉を制御するものである。なお、制御装置21は、以下に説明するような他の構成を制御することもできる。図1では、この実施の形態の理解を容易にするために、第1冷媒回路50の構成のそれぞれを接続している配管を実線で記載し、第2冷媒回路60の構成のそれぞれを接続している配管を点線で記載してある。
第1冷媒回路50は、第1メイン冷媒回路52と第1サブ冷媒流路54とを含んでいる。第1メイン冷媒回路52は、第1圧縮機1と第1凝縮器2と第1メイン膨張装置3とカスケードコンデンサ18の第1メイン蒸発部5とを含み、これらが配管で接続されている。第1圧縮機1は、第1冷媒を圧縮するものである。第1圧縮機1は、例えば、インバータで制御が行われるインバータ圧縮機であり、運転周波数を任意に変化させて、容量(単位時間あたりに冷媒を送り出す量)を変化させることができる。なお、第1圧縮機1は、一定の運転周波数で動作する一定速圧縮機であってもよい。第1凝縮器2は、例えば、第1凝縮器2を流れる第1冷媒を空気と熱交換させて、第1冷媒を凝縮させるものである。第1メイン膨張装置3は、第1冷媒を膨張させるものであり、例えば、開度を調整できる電子膨張弁であるが、毛細管等であってもよい。カスケードコンデンサ18は、第1冷媒と第2冷媒とを熱交換させるものであり、第1冷媒回路50の第1冷媒が流れる第1メイン蒸発部5と、第2冷媒回路60の第2冷媒が流れる第2メイン凝縮部8と、を含んでいる。第1メイン蒸発部5は、第1メイン蒸発部5を流れる第1冷媒を、第2メイン凝縮部8を流れる第2冷媒と熱交換させて、第1冷媒を蒸発させるものである。
第2冷媒回路60は、第2メイン冷媒回路62とバイパス流路64とインジェクション流路66とを含んでいる。第2メイン冷媒回路62は、第2圧縮機7とカスケードコンデンサ18の第2メイン凝縮部8と第1開閉装置11と受液器9と逆止弁12とサブクールコイル19の第2サブ凝縮部13と第2開閉装置14と第2膨張装置15と第2蒸発器16とを含み、これらが配管で接続されている。
図2は、図1に記載の冷凍装置で使用される冷媒を例示した図である。近年、地球温暖化等への対応を考慮して、GWP(地球温暖化係数)が低い冷媒を使用することが推奨されている。したがって、この実施の形態の例の冷凍装置100では、第2冷媒回路60に使用される冷媒は、GWPが低いものが選択されている。なぜなら、図1に記載の第2冷媒回路60は、例えば、第2開閉装置14と第2膨張装置15と第2蒸発器16とを含んでユニット化された室内ユニット(図示を省略)と、第2圧縮機7と第2メイン凝縮部8と第1開閉装置11と受液器9と逆止弁12と第2サブ凝縮部13とインジェクション用膨張装置17とを含んでユニット化された室外ユニット(図示を省略)と、を含んで構成されている。図示を省略してある室内ユニットと室外ユニットとは、冷凍装置100が設置される現地にて、作業者によって接続施工される。図示を省略してある室内ユニットと室外ユニットとを接続した部分から、冷媒が漏洩するおそれがあることが知られている。したがって、この実施の形態の例の第2冷媒回路60では、例えば、GWPが低いCO2(二酸化炭素)が採用されている。なお、第2冷媒回路60に使用される冷媒は、CO2に限定されるものではなく、GWPが低いものが選択されればよい。
次に、第1冷媒回路50および第2冷媒回路60の動作の一例について説明する。なお、冷凍装置100が冷却対象を冷却するとき、すなわち、第2蒸発器16が冷却対象を冷却するために利用されるときは、第2開閉装置14が開状態となり、第2冷媒が第2蒸発器16に流れるようになっている。
Claims (4)
- 第1冷媒を循環させる第1冷媒回路と第2冷媒を循環させる第2冷媒回路とを有し、
前記第1冷媒回路は、前記第1冷媒を圧縮する第1圧縮機と、前記第1圧縮機で圧縮された前記第1冷媒を凝縮させる第1凝縮器と、前記第1凝縮器で凝縮された前記第1冷媒を膨張させる第1メイン膨張装置と、前記第1メイン膨張装置で膨張された前記第1冷媒を前記第2冷媒と熱交換させて前記第1冷媒を蒸発させるカスケードコンデンサの第1メイン蒸発部と、が接続された第1メイン冷媒回路と、
前記第1メイン膨張装置および前記第1メイン蒸発部と並列に接続され、前記第1凝縮器で凝縮された前記第1冷媒を膨張させる第1サブ膨張装置と、前記第1サブ膨張装置で膨張された前記第1冷媒を前記第2冷媒と熱交換させて前記第1冷媒を蒸発させるサブクールコイルの第1サブ蒸発部と、が配設された第1サブ冷媒流路と、を含み、
前記第2冷媒回路は、前記第2冷媒を圧縮する第2圧縮機と、前記第2圧縮機で圧縮された前記第2冷媒を前記第1冷媒と熱交換させて前記第2冷媒を凝縮させる前記カスケードコンデンサの第2メイン凝縮部と、前記第2メイン凝縮部で凝縮された前記第2冷媒を前記第1冷媒と熱交換させて前記第2冷媒を冷却する前記サブクールコイルの第2サブ凝縮部と、が接続された第2メイン冷媒回路を含む、
冷凍装置。 - 前記第2メイン冷媒回路は、前記第2メイン凝縮部で凝縮された前記第2冷媒の通過を制御する第1開閉装置と、前記第1開閉装置を通過した前記第2冷媒を貯留する受液器と、前記第2サブ凝縮部で冷却された前記第2冷媒の通過を制御する第2開閉装置と、をさらに有し、
前記第2冷媒回路は、前記第1開閉装置および前記受液器と並列に接続されたバイパス流路をさらに含む、
請求項1に記載の冷凍装置。 - 前記第2圧縮機の吸入側の低圧圧力を検出する圧力検出装置と、
前記圧力検出装置が検出した前記低圧圧力を用いて前記第1開閉装置の開閉を制御する制御装置と、をさらに有し、
前記制御装置は、前記低圧圧力を用いて、前記第2開閉装置が開状態であると判断したときに前記第1開閉装置を閉状態とし、前記第2開閉装置が閉状態であると判断したときに前記第1開閉装置を開状態とする、
請求項2に記載の冷凍装置。 - 前記第1冷媒は、前記第1冷媒回路に前記第2冷媒を循環させた場合と比較して、効率(COP)が高くなるものが選択されている、
請求項1~請求項3の何れか1項に記載の冷凍装置。
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Cited By (13)
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US10443900B2 (en) * | 2015-01-09 | 2019-10-15 | Trane International Inc. | Heat pump |
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