WO2017130319A1 - 冷凍サイクル装置 - Google Patents
冷凍サイクル装置 Download PDFInfo
- Publication number
- WO2017130319A1 WO2017130319A1 PCT/JP2016/052313 JP2016052313W WO2017130319A1 WO 2017130319 A1 WO2017130319 A1 WO 2017130319A1 JP 2016052313 W JP2016052313 W JP 2016052313W WO 2017130319 A1 WO2017130319 A1 WO 2017130319A1
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- WIPO (PCT)
- Prior art keywords
- refrigerant
- control device
- temperature
- heat exchanger
- load
- Prior art date
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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
-
- 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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
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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
-
- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
- F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
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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
- F25B2600/2513—Expansion 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
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21153—Temperatures of a compressor or the drive means therefor of electronic components
Definitions
- the present invention relates to a refrigeration cycle apparatus provided with a cooling mechanism of a control device.
- the heat dissipated refrigerant flows through the refrigerant cooler to exchange heat with the control device.
- a technique for cooling the control device is known (for example, see Patent Document 1).
- the refrigerant partially bypassed from the main flow on the high-pressure side cools the control device with the refrigerant cooler, and then flows to the low-pressure side through the expansion device that controls the refrigerant flow rate of the refrigerant cooler.
- the refrigerant flow rate of the refrigerant cooler is controlled by a throttle device downstream of the refrigerant cooler.
- the refrigerant in the refrigerant cooler has a high pressure and the evaporation temperature becomes high, so that a temperature difference between the temperature of the control device and the temperature of the refrigerant cannot be obtained. For this reason, when a large cooling capacity is required, the required cooling capacity cannot be achieved. In order to achieve the required cooling capacity, it is necessary to bypass a large amount of refrigerant, and the capacity of the refrigeration cycle apparatus itself is reduced.
- the present invention has been made to solve the above-described problems, and an object thereof is to obtain a refrigeration cycle apparatus capable of improving the cooling performance of a control apparatus.
- a refrigeration cycle apparatus includes a compressor, a heat source side heat exchanger, a first expansion device, and a load side heat exchanger, a refrigerant circuit in which refrigerant circulates, a control device that controls the refrigerant circuit, and a compression A bypass pipe branched from the high-pressure pipe leading from the compressor to the first throttle device and connected to the low-pressure pipe on the suction side of the compressor, and a precooling heat exchanger provided in the bypass pipe for cooling the refrigerant bypassed to the bypass pipe And a second expansion device that depressurizes the refrigerant cooled in the precooling heat exchanger and provided in the bypass piping, and a refrigerant that is provided in the bypass piping and cools the control device using the refrigerant depressurized by the second expansion device And a cooler.
- the second expansion device is provided between the precooling heat exchanger and the refrigerant cooler, the refrigerant cooled by the precooling heat exchanger is decompressed by the second expansion device, and the refrigerant temperature is further lowered.
- it can be passed through the refrigerant cooler, and the cooling performance of the control device can be improved.
- FIG. 6 is a diagram summarizing operations of the diaphragm device 602 based on the flowchart of FIG. 5. It is a schematic block diagram which shows an example of the refrigerant circuit structure of the air conditioning apparatus 500A which concerns on Embodiment 2 of this invention.
- FIG. 1 and the following drawings, the same reference numerals denote the same or corresponding parts, and are common to the whole text of the embodiments described below.
- the form of the component represented by the whole specification is an illustration to the last, Comprising: It does not limit to the form described in the specification.
- the level of temperature, pressure, etc. is not particularly determined in relation to absolute values, but is relatively determined in terms of the state, operation, etc. of the system, apparatus, etc.
- FIG. 1 is a schematic configuration diagram illustrating an example of a refrigerant circuit configuration of an air-conditioning apparatus 500 according to Embodiment 1 of the present invention.
- the air conditioner 500 is installed in, for example, a building or a condominium, and can perform a cooling operation or a heating operation using a refrigeration cycle (heat pump cycle) that circulates a refrigerant.
- a refrigeration cycle heat pump cycle
- the air conditioner 500 has a heat source side unit 100 and a plurality (two in FIG. 1) of load side units 300 (load side units 300a and 300b).
- the heat source side unit 100 and the load side unit 300 are connected by a gas extension pipe 401 and a liquid extension pipe 402 to form a refrigeration cycle.
- the gas extension pipe 401 includes a gas main pipe 401A, a gas branch pipe 401a, and a gas branch pipe 401b.
- the liquid extension pipe 402 includes a liquid main pipe 402A, a liquid branch pipe 402a, and a liquid branch pipe 402b.
- the heat source side unit 100 has a function of supplying cold or warm heat to the load side unit 300.
- the heat source unit 100 includes a compressor 101, a four-way switching valve 102 that is a flow path switching device, a heat source side heat exchanger 103, and an accumulator 104. These devices are connected in series to constitute a part of the main refrigerant circuit. In addition, a heat source side fan 106 is mounted on the heat source side unit 100.
- the compressor 101 sucks in a low-temperature and low-pressure gas refrigerant, compresses the refrigerant to discharge it as a high-temperature and high-pressure gas refrigerant, and circulates the refrigerant in the refrigerant circuit to perform an operation related to air conditioning.
- the compressor 101 may be composed of, for example, an inverter type compressor whose capacity can be controlled.
- the compressor 101 is not limited to an inverter type compressor capable of capacity control.
- it may be constituted by a constant speed type compressor, a compressor combined with an inverter type and a constant speed type, or the like.
- the compressor 101 is not particularly limited as long as it can compress the sucked refrigerant into a high-pressure state.
- the compressor 101 can be configured using various types such as reciprocating, rotary, scroll, or screw.
- the four-way switching valve 102 is provided on the discharge side of the compressor 101 and switches the refrigerant flow path between the cooling operation and the heating operation. And the flow of a refrigerant
- coolant is controlled so that the heat source side heat exchanger 103 functions as an evaporator or a condenser according to an operation mode.
- the heat source side heat exchanger 103 performs heat exchange between the heat medium (for example, ambient air, water, etc.) and the refrigerant. During the heating operation, the heat source side heat exchanger 103 functions as an evaporator, and evaporates and gasifies the refrigerant. Further, during the cooling operation, the heat source side heat exchanger 103 functions as a condenser (heat radiator) and condenses and liquefies the refrigerant.
- the heat medium for example, ambient air, water, etc.
- the heat source side unit 100 includes a blower such as the heat source side fan 106.
- the control device 118 described later controls the rotation speed of the heat source side fan 106.
- the condensing capacity or evaporation capacity of the heat source side heat exchanger 103 is controlled by controlling the rotation speed of a water circulation pump (not shown).
- the accumulator 104 is provided on the suction side of the compressor 101 and has a function of separating liquid refrigerant and gas refrigerant and a function of storing surplus refrigerant.
- the heat source side unit 100 includes a high pressure sensor 141 that detects the pressure (high pressure) of the refrigerant discharged from the compressor 101. Further, the heat source side unit 100 includes a low pressure sensor 142 that detects the pressure (low pressure) of the refrigerant sucked into the compressor 101.
- the heat source side unit 100 further includes an outside air temperature sensor 604 that detects the outside air temperature, a controller temperature sensor 605 that detects the temperature of the controller 118, and a temperature sensor 606 that detects the pipe temperature downstream of the refrigerant cooler 603. I have. Each of these sensors sends a signal related to the detected pressure and a signal related to the detected temperature to the control device 118 that controls the operation of the air conditioning apparatus 500.
- the control device 118 performs the drive frequency of the compressor 101, the rotation speed of the heat source side fan 106, the switching control of the four-way switching valve 102, and the like based on the high pressure and the low pressure. Further, the control device 118 controls a diaphragm device 602 described later based on the detected pressure and detected temperature from each sensor.
- the temperature sensor 606 and the low-pressure sensor 142 constitute the superheat detection device of the present invention.
- the superheat degree detection device only needs to be able to detect the superheat degree at the outlet of the refrigerant cooler 603 and may use a temperature sensor that detects the refrigerant temperature at the inlet of the refrigerant cooler 603 instead of the low pressure sensor 142.
- the control device 118 controls the air conditioner 500 with a focus on equipment included in the heat source side unit 100.
- the control device 118 is composed of, for example, a microcomputer.
- control arithmetic processing means such as a CPU (Central Processing Unit).
- CPU Central Processing Unit
- storage means not shown
- a control arithmetic processing means performs the process based on the data of a program, and implement
- the control device 118 is installed in the heat source side unit 100, but the installation location is not limited as long as the device and the like can be controlled.
- the heat source side unit 100 further includes a bypass pipe 608 that branches from the high-pressure pipe 611 through which the high-pressure gas refrigerant discharged from the compressor 101 passes and is connected to the low-pressure pipe 610 on the suction side of the compressor 101. .
- Bypass piping 608 bypasses the mainstream high pressure gas refrigerant.
- the bypass pipe 608 is provided with a precooling heat exchanger 601 that cools the high-pressure gas refrigerant that has flowed into the bypass pipe 608, and the throttle device 602 that adjusts the bypass flow rate and the control device 118 are cooled downstream of the precooling heat exchanger 601.
- a refrigerant cooler 603 is provided.
- the diaphragm device 602 corresponds to the second diaphragm device of the present invention.
- the throttle device 602 has a function as a pressure reducing valve or an expansion valve, and expands the refrigerant by decompressing it.
- the expansion device 602 has a role of depressurizing the high-pressure refrigerant cooled by the pre-cooling heat exchanger 601 and further reducing the refrigerant temperature to flow into the refrigerant cooler 603.
- the expansion device 602 is configured by a device whose opening degree can be variably controlled, for example, an electronic expansion valve.
- the pre-cooling heat exchanger 601 is configured as an integrated heat exchanger together with the heat source side heat exchanger 103, and a part of the integrated heat exchanger is configured as the pre-cooling heat exchanger 601.
- the precooling heat exchanger 601 may be configured separately from the heat source side heat exchanger 103.
- the refrigerant cooler 603 has a refrigerant pipe through which the refrigerant passes, and is configured by bringing the refrigerant pipe into contact with the control device 118.
- the refrigerant flowing into the bypass pipe 608 is cooled by the pre-cooling heat exchanger 601 to become liquid refrigerant, and the flow rate is adjusted by the expansion device 602 and flows into the refrigerant cooler 603.
- the liquid refrigerant that has flowed into the refrigerant cooler 603 absorbs the heat generated by the control device 118 and becomes a gas refrigerant.
- the refrigerant that has become the gas refrigerant passes through the downstream refrigerant cooler downstream pipe 609, passes through the low-pressure pipe 610, and flows to the accumulator 104.
- the load side unit 300 supplies the cooling heat or the heat from the heat source side unit 100 to the cooling load or the heating load.
- a is added after the code of each device provided in the “load side unit 300a”
- b is added after the code of each device provided in the “load side unit 300b”. This is shown in the figure.
- “a” and “b” after the reference may be omitted, but each device is provided in both the load side unit 300a and the load side unit 300b.
- the load-side unit 300 includes a load-side heat exchanger 312 (load-side heat exchangers 312a and 312b) and an expansion device 311 (expansion devices 311a and 311b) connected in series and mounted on the heat source side.
- a refrigerant circuit is configured together with the unit 100.
- the aperture device 311 corresponds to the first aperture device of the present invention.
- a blower (not shown) for supplying air to the load side heat exchanger 312 may be provided.
- the load-side heat exchanger 312 may perform heat exchange between the refrigerant and a heat medium different from the refrigerant such as water.
- the load-side heat exchanger 312 exchanges heat between a heat medium (for example, ambient air or water) and a refrigerant, condenses and liquefies the refrigerant as a condenser (heat radiator) during heating operation, and performs cooling operation. Sometimes an evaporator is used to evaporate and gasify the refrigerant.
- the load-side heat exchanger 312 is generally configured by combining a blower that is omitted in the drawing, and the condensing capacity or evaporation capacity is controlled by the rotational speed of the blower.
- the throttle device 311 has a function as a pressure reducing valve or an expansion valve, and expands the refrigerant by decompressing it.
- the throttling device 311 may be constituted by a device whose opening degree can be variably controlled, for example, a precise flow rate control device using an electronic expansion valve, an inexpensive refrigerant flow rate control means such as a capillary tube, or the like.
- the load side unit 300 includes a temperature sensor 314 (temperature sensors 314a and 314b) that detects the temperature of the refrigerant pipe between the expansion device 311 and the load side heat exchanger 312, the load side heat exchanger 312 and the four-way switching valve 102.
- the temperature sensor 313 (temperature sensors 313a and 313b) for detecting the temperature of the refrigerant pipe between them is provided at least.
- Information (temperature information) detected by these various detection means is sent to the control device 118 that controls the operation of the air conditioner 500, and is used to control various actuators. That is, the information from the temperature sensor 313 and the temperature sensor 314 is used for controlling the opening degree of the expansion device 311 provided in the load side unit 300, the rotational speed of the blower not shown, and the like.
- the type of the refrigerant used in the air conditioner 500 is not particularly limited, for example, a natural refrigerant such as carbon dioxide, hydrocarbon, or helium, an alternative refrigerant not containing chlorine such as HFC410A, HFC407C, and HFC404A, or Any of chlorofluorocarbon refrigerants such as R22 and R134a used in existing products may be used.
- a natural refrigerant such as carbon dioxide, hydrocarbon, or helium
- an alternative refrigerant not containing chlorine such as HFC410A, HFC407C, and HFC404A
- chlorofluorocarbon refrigerants such as R22 and R134a used in existing products may be used.
- control device 118 that controls the operation of the air conditioner 500 is mounted on the heat source side unit 100, it may be provided in the load side unit 300. Further, the control device 118 may be provided outside the heat source side unit 100 and the load side unit 300. Further, the control device 118 may be divided into a plurality according to the function and provided in each of the heat source side unit 100 and the load side unit 300. In this case, each control device is preferably connected wirelessly or by wire so that communication is possible.
- the air conditioning apparatus 500 performs any one of the two operation modes according to the request.
- the two operation modes include a cooling operation mode and a heating operation mode.
- FIG. 2 is a diagram illustrating a refrigerant flow when the air-conditioning apparatus 500 according to Embodiment 1 of the present invention is in the cooling operation mode. Based on FIG. 2, the operation
- Compressor 101 compresses a low-temperature and low-pressure refrigerant and discharges a high-temperature and high-pressure gas refrigerant.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 101 passes through the four-way switching valve 102 and flows to the heat source side heat exchanger 103. Since the heat source side heat exchanger 103 functions as a condenser, the refrigerant exchanges heat with the surrounding air to condense and liquefy.
- the liquid refrigerant that has flowed out of the heat source side heat exchanger 103 flows out of the heat source side unit 100 through the liquid main pipe 402A.
- the high-pressure liquid refrigerant that has flowed out of the heat source side unit 100 flows into the load side units 300a and 300b through the liquid branch pipes 402a and 402b.
- the liquid refrigerant that has flowed into the load-side units 300a and 300b is throttled by the throttle devices 311a and 311b to become a low-temperature gas-liquid two-phase refrigerant.
- This low-temperature gas-liquid two-phase refrigerant flows into the load side heat exchangers 312a and 312b. Since the load-side heat exchangers 312a and 312b work as evaporators, the refrigerant evaporates and gasifies by exchanging heat with the surrounding air.
- the refrigerant cools the room by absorbing heat from the surroundings. Thereafter, the refrigerant that has flowed out of the load-side heat exchangers 312a and 312b flows out of the load-side units 300a and 300b through the gas branch pipes 401a and 401b.
- the refrigerant that has flowed out of the load side units 300a and 300b returns to the heat source side unit 100 through the gas main pipe 401A.
- the gas refrigerant that has returned to the heat source side unit 100 is again sucked into the compressor 101 via the four-way switching valve 102 and the accumulator 104. With the above flow, the air conditioner 500 executes the cooling operation mode.
- FIG. 3 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus 500 according to Embodiment 1 of the present invention is in the heating operation mode. Based on FIG. 3, the operation
- the low-temperature and low-pressure refrigerant is compressed by the compressor 101 and discharged as a high-temperature and high-pressure gas refrigerant.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 101 passes through the four-way switching valve 102 and flows to the high-pressure pipe 404. Thereafter, the refrigerant flows out from the heat source unit 100.
- the high-temperature and high-pressure gas refrigerant flowing out from the heat source side unit 100 flows into the load side units 300a and 300b through the gas branch pipes 401a and 401b.
- the refrigerant that has flowed out of the load side units 300a and 300b returns to the heat source side unit 100 through the liquid main pipe 402A.
- the gas refrigerant returned to the heat source side unit 100 flows into the heat source side heat exchanger 103. Since the heat source side heat exchanger 103 functions as an evaporator, the refrigerant exchanges heat with the surrounding air, and the refrigerant evaporates and gasifies. Thereafter, the refrigerant that has flowed out of the heat source side heat exchanger 103 flows into the accumulator 104 via the four-way switching valve 102.
- the compressor 101 sucks the refrigerant in the accumulator 104 and circulates it in the refrigerant circuit, so that a refrigeration cycle is established. With the above flow, the air conditioning apparatus 500 executes the heating operation mode.
- refrigerant cooling control which is a characteristic part of the first embodiment, will be described.
- the refrigerant cooling control which is a control for cooling the control device 118 with the refrigerant, is the same control in both the cooling operation mode and the heating operation mode. For this reason, below, refrigerant
- FIG. 4 is a refrigerant circuit diagram illustrating a refrigerant flow in the refrigerant cooling control during the cooling operation mode of the air-conditioning apparatus 500 according to Embodiment 1 of the present invention.
- the refrigerant cooling control a part of the high-pressure gas refrigerant passing through the high-pressure pipe 611 is bypassed to the bypass pipe 608 and flows into the precooling heat exchanger 601.
- the liquid refrigerant flowing into the precooling heat exchanger 601 is cooled by exchanging heat with the air from the heat source side fan 106.
- the liquid refrigerant cooled to the low pressure by the pre-cooling heat exchanger 601 is reduced in pressure by the expansion device 602 and further reduced in pressure, and then flows into the refrigerant cooler 603.
- the refrigerant cooler 603 the refrigerant exchanges heat with the control device 118 and evaporates. At this time, the refrigerant absorbs heat from the control device 118 to cool the control device 118.
- the refrigerant that has cooled the control device 118 becomes a gas refrigerant or a two-phase refrigerant, flows through the low-pressure pipe 610, and flows into the accumulator 104.
- the refrigerant flow rate flowing through the refrigerant cooler 603 is adjusted by the expansion device 602.
- Control of the expansion device 602 is performed by the control device 118 based on information obtained from the low pressure sensor 142, the control device temperature sensor 605, the temperature sensor 606, and the outside air temperature sensor 604.
- specific control of the diaphragm device 602 will be described.
- FIG. 5 is a flowchart showing the control of the expansion device 602 during the refrigerant cooling control of the air-conditioning apparatus 500 according to Embodiment 1 of the present invention.
- FIG. 6 is a diagram summarizing the operation of the diaphragm device 602 based on the flowchart of FIG. In the following description, it is assumed that (A) to (E) indicating the temperature have a relationship of (B) ⁇ (D) ⁇ (C) ⁇ (E) ⁇ (A).
- the aperture device 602 is in a closed state. Then, after starting the operation of the air conditioner 500, the control device 118 determines whether the detected temperature of the control device temperature sensor 605 is equal to or higher than a preset start temperature (A) (for example, 75 ° C.) (S1). When the detected temperature is lower than the start temperature (A), it is not necessary to cool the control device 118, so that the opening degree of the expansion device 602 is maintained, that is, closed (S2), and the refrigerant cooler 603 receives the refrigerant. Do not flush.
- A preset start temperature
- the control device 118 opens the expansion device 602 to a preset fixed opening (S3). As a result, the refrigerant flows into the refrigerant cooler 603 and cooling of the control device 118 is started, and the temperature of the control device 118 is lowered.
- the control device 118 checks the detection temperature of the control device temperature sensor 605 and determines whether the detection temperature of the control device temperature sensor 605 is equal to or lower than a preset end temperature (B) (for example, 45 ° C.) ( S4).
- a preset end temperature B
- the control device 118 closes the expansion device 602 to end the cooling of the control device 118 (S5), and returns to step S1.
- the detected temperature of the control device temperature sensor 605 is higher than the end temperature (B)
- it is necessary to continue cooling so that whether the detected temperature of the control device temperature sensor 605 is equal to or lower than the outside air temperature (D). Is determined (S6). This determination is made to prevent the controller 118 from condensing.
- step S5 When the temperature detected by the control device temperature sensor 605 falls below the outside air temperature (D), dew condensation occurs in the control device 118, so the control device 118 closes the expansion device 602 and finishes cooling the control device 118 (S5). Return to step S1. On the other hand, if the detected temperature of the control device temperature sensor 605 is higher than the outside air temperature (D), then whether the detected temperature of the control device temperature sensor 605 is equal to or lower than a preset target temperature (C) (for example, 60 ° C.). Is determined (S7).
- C preset target temperature
- the control device 118 restricts the opening of the expansion device 602 so that the temperature of the control device 118 becomes the target temperature (C) (S8). Return to the determination in step S4. When the detected temperature of the control device temperature sensor 605 matches the target temperature (C), the current opening degree may be maintained. On the other hand, when the temperature detected by the control device temperature sensor 605 is higher than the target temperature (C), the control device 118 determines whether or not both of the following conditions (1) and (2) are satisfied (S9).
- the superheat degree at the outlet of the refrigerant cooler 603 calculated from the detected values of the temperature sensor 606 and the low pressure sensor 142 is equal to or less than a preset set value (for example, 2 ° C.).
- Controller temperature sensor 605 Detection temperature is below a certain value (E) (for example, 70 ° C.)
- the determination in step S9 is for the following purpose. That is, while the opening degree control of the expansion device 602 is performed for the purpose of lowering the detected temperature of the control device temperature sensor 605 to the target temperature (C) or less, for example, the bypass pipe 608 is controlled with respect to the temperature of the control device 118.
- the degree of superheat at the outlet of the refrigerant cooler 603 may be reduced, leading to liquid back. That is, if the amount of refrigerant passing through the bypass pipe 608 is large while the temperature of the control device 118 is not so high, there is a possibility that the cooling capacity will be excessive and liquid back may occur.
- the determination in step S9 (1) is intended to prevent this liquid back.
- condition (1) when the condition (1) is satisfied and the possibility of liquid back is high, control is performed so that the opening degree of the expansion device 602 is reduced.
- the temperature of the control device 118 when the temperature of the control device 118 is high, the temperature of the control device 118 may be excessively increased due to insufficient cooling if the opening degree is decreased.
- the condition of (2) is further provided, and when the detected temperature of the control device temperature sensor 605 is not high, control is performed so that the degree of superheat becomes a target. Note that the condition (2) can be omitted.
- the control device 118 restricts the expansion device 602 so that the superheat degree at the outlet of the refrigerant cooler 603 becomes the target superheat degree (S10).
- control device 118 detects the temperature detected by the control device temperature sensor 605 in order to continue cooling because it is not a cooling state in which liquid back occurs.
- the opening degree of the expansion device 602 is opened so that becomes the target temperature (C) (S11). And it returns to step S4 and repeats the same process.
- the flow is a flow for performing the liquid back prevention determination in step S9 when the temperature detected by the control device temperature sensor 605 is higher than the target temperature (C) and lower than the start temperature (A). This is because the degree of superheat does not become lower than the set value in other temperature states, or the throttle device 602 is controlled to be throttled as apparent from FIG. This is because it is sufficient.
- the control device 118 is cooled by the above refrigerant cooling control.
- the specific numerical value of each temperature in said description is only an example, and what is necessary is just to set them suitably according to actual use conditions.
- the expansion device 602 is provided upstream of the refrigerant cooler 603.
- the refrigerant cooler 603 I try to make it flow.
- the refrigerant passing through the refrigerant cooler 603 becomes a low pressure corresponding to the decompression by the expansion device 602, and the evaporation temperature becomes low. Therefore, the evaporation temperature in the refrigerant cooler can be lowered as compared with the conventional configuration in which the expansion device is provided downstream of the refrigerant cooler.
- the temperature difference between the temperature of the control device 118 and the temperature of the refrigerant passing through the refrigerant cooler 603 can be increased as compared with the conventional configuration, and the heat exchange efficiency is increased. As a result, it is possible to achieve the required cooling capacity with a small amount of refrigerant.
- the heat exchange efficiency of the refrigerant cooler 603 is increased and the bypass flow rate is reduced. be able to. Therefore, since the flow rate of the refrigerant flowing through the refrigerant circuit can be ensured, the cooling and heating performance of the air conditioner itself can be maintained.
- the expansion device 602 is provided upstream of the refrigerant cooler 603 and the expansion device 602 is not provided downstream, the refrigerant circuit configuration can be simplified.
- the air conditioner 500 having one heat source side unit 100A and two load side units 300 is shown, but the number of units is not particularly limited.
- the present invention is applied to the air conditioner 500A that can be operated by switching the load side unit 300 to either cooling or heating has been described as an example.
- the present invention is applied.
- the apparatus to be used is not limited to this apparatus.
- the present invention is also applied to other apparatuses that configure a refrigerant circuit using a refrigeration cycle, such as a refrigeration cycle apparatus and a refrigeration system that heats a load by supplying capacity. be able to.
- an air conditioner capable of operating in an air-conditioning mixed mode will be described as an example of another device to which the present invention can be applied.
- FIG. FIG. 7 is a schematic configuration diagram illustrating an example of a refrigerant circuit configuration of an air-conditioning apparatus 500A according to Embodiment 2 of the present invention.
- the air-conditioning apparatus 500A according to the second embodiment will be described with a focus on differences from the air-conditioning apparatus 500 according to the first embodiment shown in FIG.
- the relay unit 200 is further connected between the heat source side unit 100 and the plurality of load side units 300 of the air conditioning apparatus 500 of the first embodiment shown in FIG. Have a configuration.
- the configuration of the load side unit 300 is the same as that of the first embodiment.
- the heat source side unit 100A and the relay unit 200 of the second embodiment are connected by two pipes (low pressure pipe 403 and high pressure pipe 404), and the relay unit 200 and the load side units 300a and 300b are gas branch pipes. 401a, the liquid branch pipe 402a, the gas branch pipe 401b, and the liquid branch pipe 402b are connected.
- the heat source side unit 100A of the second embodiment further includes a check valve 112, a check valve 113, a check valve 114, a check valve 115, and a first connection pipe. 120 and the second connection pipe 121 are mounted.
- the check valve 112, the check valve 113, the check valve 114, the check valve 115, the first connection pipe 120, and the second connection pipe 121 constitute the rectifier of the present invention.
- the first connection pipe 120 is a pipe that connects the high pressure pipe 404 on the downstream side of the check valve 113 and the low pressure pipe 403 on the downstream side of the check valve 112.
- the second connection pipe 121 is a pipe that connects the high-pressure pipe 404 on the upstream side of the check valve 113 and the low-pressure pipe 403 on the upstream side of the check valve 112.
- a joining part of the second connection pipe 121 and the high-pressure pipe 404 is a joining part a.
- a joining part between the first connection pipe 120 and the high-pressure pipe 404 is a joining part b (downstream side from the joining part a).
- a junction between the second connection pipe 121 and the low-pressure pipe 403 is defined as a junction c.
- pressure piping 403 be the confluence
- the check valve 112 is provided between the junction c and the junction d, and allows the refrigerant to flow only in the direction from the relay unit 200 to the heat source unit 100A.
- the check valve 113 is provided between the merging portion a and the merging portion b, and allows the refrigerant to flow only in the direction from the heat source unit 100A to the relay unit 200.
- the check valve 115 is provided in the first connection pipe 120 and allows the refrigerant to flow only in the direction from the joining part d to the joining part b.
- the check valve 114 is provided in the second connection pipe 121 and allows the refrigerant to flow only in the direction from the junction c to the junction a.
- the flow of the refrigerant between the heat source unit 100A and the relay unit 200 can be unidirectional regardless of whether the load side unit 300 requires heating or cooling. That is, the high-pressure pipe 404 has a flow from the heat source side unit 100A toward the relay unit 200, and the low-pressure pipe 403 has a flow from the relay unit 200 toward the heat source side unit 100A.
- the heat source side unit 100A includes a bypass pipe 608A instead of the bypass pipe 608 of the first embodiment.
- the bypass pipe 608A differs from the bypass pipe 608 of the first embodiment in the connection position of one end on the high pressure side, and the bypass pipe 608 of the first embodiment is connected to the high pressure pipe 611 through which the high-pressure refrigerant discharged from the compressor 101 passes.
- the high-pressure pipe 404 extending from the heat source side heat exchanger 103 to the expansion device 311 is connected downstream of the junction b.
- the other passages of the bypass pipe 608A and the devices provided in the bypass pipe 608A are the same as the bypass pipe 608 of the first embodiment.
- the relay unit 200 distributes the low-temperature refrigerant to the load-side unit 300 that performs the cooling operation, and distributes the high-temperature refrigerant to the load-side unit 300 that performs the heating operation according to the operation state of the load-side unit 300. Thus, the refrigerant flow is switched.
- “a” or “b” is added after the codes of some devices included in the relay unit 200. This indicates whether it is connected to “load side unit 300a” or “load side unit 300b”.
- the suffix “a” or “b” added after the reference numeral may be omitted. When omitted, the description includes the case of any device connected to the “load unit 300a” or “load unit 300b”.
- the relay unit 200 includes a gas-liquid separator 211, a first on-off valve 212 (first on-off valves 212a and 212b), a second on-off valve 213 (second on-off valves 213a and 213b), and a first throttle device 214.
- the second expansion device 215, the first refrigerant heat exchanger 216, and the second refrigerant heat exchanger 217 are mounted.
- the relay unit 200 branches from a pipe on the downstream side of the primary side of the second refrigerant heat exchanger 217 (the side through which the refrigerant flows via the first expansion device 214), and is connected to the low-pressure pipe 403. 220 is provided.
- the gas-liquid separator 211 is provided in the high-pressure pipe 404 and has a function of separating the two-phase refrigerant flowing through the high-pressure pipe 404 into a gas refrigerant and a liquid refrigerant.
- the gas refrigerant separated by the gas-liquid separator 211 is supplied to the first on-off valve 212 via the connection pipe 221 and the liquid refrigerant is supplied to the first refrigerant heat exchanger 216, respectively.
- the first on-off valve 212 is for controlling the supply of the refrigerant to the load side unit 300 for each operation mode, and is provided between the connection pipe 221 and the gas branch pipes 401a and 401b. That is, one of the first on-off valves 212 is connected to the gas-liquid separator 211 and the other is connected to the load-side heat exchanger 312 of the load-side unit 300, and controls whether or not the refrigerant is allowed to pass by opening and closing. To do.
- the second on-off valve 213 is also for controlling the supply of the refrigerant to the load side unit 300 for each operation mode, and is provided between the gas branch pipes 401 a and 401 b and the low pressure pipe 403. That is, one of the second on-off valves 213 is connected to the low-pressure pipe 403, and the other is connected to the load-side heat exchanger 312 of the load-side unit 300. It ’s something that you do n’t.
- the first expansion device 214 is provided between the gas-liquid separator 211 and the liquid branch pipes 402a and 402b, that is, between the first refrigerant heat exchanger 216 and the second refrigerant heat exchanger 217. It functions as a pressure reducing valve or an expansion valve, and expands the refrigerant by decompressing it.
- the first throttle device 214 may be configured by a device whose opening degree can be variably controlled, for example, a precise flow rate control device using an electronic expansion valve, an inexpensive refrigerant flow rate control means such as a capillary tube, or the like.
- the second expansion device 215 is provided between the second refrigerant heat exchanger 217 and the second on-off valve 213 in the connection pipe 220, and functions as a pressure reducing valve and an expansion valve. Inflate. Similar to the first throttle device 214, the second throttle device 215 can be variably controlled, for example, a precise flow control device using an electronic expansion valve, an inexpensive refrigerant flow rate control means such as a capillary tube, etc. It is good to comprise.
- the first refrigerant heat exchanger 216 includes a refrigerant flowing on the primary side (the side on which the liquid refrigerant separated by the gas-liquid separator 211 flows) and the secondary side (on the connection pipe 220 after passing through the second expansion device 215). Heat exchange is performed between the refrigerant flowing through the refrigerant refrigerant flowing out of the two refrigerant heat exchangers 217 and the refrigerant flowing through the refrigerant refrigerant.
- the second refrigerant heat exchanger 217 performs heat exchange between the refrigerant flowing on the primary side (downstream side of the first expansion device 214) and the refrigerant flowing on the secondary side (downstream side of the second expansion device 215). Is.
- the first refrigerant heat exchanger 216 and the second refrigerant heat exchange are performed. Heat is exchanged between the refrigerant flowing through the main circuit (primary side) and the refrigerant flowing through the connection pipe 220 (secondary side) by the vessel 217 so that the refrigerant flowing through the main circuit can be supercooled.
- the bypass amount is controlled so that proper supercooling can be achieved at the primary outlet of the second refrigerant heat exchanger 217 according to the opening of the second expansion device 215.
- FIG. 7 shows an example in which the control device 118 that controls the operation of the air conditioner 500A is mounted on the heat source side unit 100A.
- the control device 118 is provided on either the relay unit 200 or the load side unit 300. May be.
- the control device 118 may be provided outside the heat source side unit 100A, the relay unit 200, and the load side unit 300.
- the control device 118 may be divided into a plurality according to the function and provided in each of the heat source side unit 100A, the relay unit 200, and the load side unit 300. In this case, each control device is preferably connected wirelessly or by wire so that communication is possible.
- the air conditioner 500A performs any one of the four operation modes in response to a request.
- the four operation modes are as follows. (1) Cooling operation mode in which all load side units 300 are cooling operation requests (2) Cooling operation requests and heating operation requests are mixed, and it is determined that the load to be processed by the cooling operation is large. Main operation mode (3) A cooling operation request and a heating operation request are mixed and a heating main operation mode in which it is determined that there is a large heating load. (4) All load-side units 300 are all heating operation requests. Heating operation mode
- FIG. 8 is a diagram illustrating a refrigerant flow when the air-conditioning apparatus 500A according to Embodiment 2 of the present invention is in the cooling only operation mode. Based on FIG. 8, the operation of the air conditioner 500A in the cooling only operation mode will be described. In the first on-off valve 212 and the second on-off valve 213 in FIG. 8, black is closed and white is open. This is the same in each of the drawings described later.
- Compressor 101 compresses a low-temperature and low-pressure refrigerant and discharges a high-temperature and high-pressure gas refrigerant.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 101 passes through the four-way switching valve 102 and flows to the heat source side heat exchanger 103. Since the heat source side heat exchanger 103 functions as a condenser, the refrigerant exchanges heat with the surrounding air to condense and liquefy.
- the liquid refrigerant that has flowed out of the heat source side heat exchanger 103 flows out of the heat source side unit 100A through the high-pressure pipe 404, the check valve 113, and the like.
- the high-pressure liquid refrigerant that has flowed out of the heat source side unit 100A flows into the primary side (refrigerant inflow side) of the first refrigerant heat exchanger 216 via the gas-liquid separator 211 of the relay unit 200.
- the liquid refrigerant flowing into the primary side of the first refrigerant heat exchanger 216 is supercooled by the refrigerant on the secondary side (refrigerant outflow side) of the first refrigerant heat exchanger 216.
- the liquid refrigerant whose degree of supercooling has been increased is throttled to an intermediate pressure by the first throttle device 214. Thereafter, the liquid refrigerant flows into the second refrigerant heat exchanger 217, and further increases the degree of supercooling. Then, the liquid refrigerant is divided, partly passes through the check valves 218 a and 218 b, flows out from the relay unit 200, and the rest goes to the second expansion device 215.
- the liquid refrigerant flowing out from the relay unit 200 flows into the load side units 300a and 300b.
- the liquid refrigerant that has flowed into the load-side units 300a and 300b is throttled by the throttle devices 311a and 311b to become a low-temperature gas-liquid two-phase refrigerant.
- This low-temperature gas-liquid two-phase refrigerant flows into the load side heat exchangers 312a and 312b. Since the load-side heat exchangers 312a and 312b work as evaporators, the refrigerant evaporates and gasifies by exchanging heat with the surrounding air. At this time, the refrigerant cools the room by absorbing heat from the surroundings. Thereafter, the refrigerant flowing out from the load side heat exchangers 312a and 312b flows through the gas branch pipes 401a and 401b and out of the load side unit 300a, and then flows into the relay unit 200.
- the refrigerant flowing into the relay unit 200 is connected to the connection pipe 220 via the first expansion device 214 and the second expansion device 215 to be supercooled by the second refrigerant heat exchanger 217 via the second on-off valves 213a and 213b.
- the refrigerant that has flowed through the refrigerant reaches the low-pressure pipe 403.
- the refrigerant flowing through the low pressure pipe 403 flows out of the relay unit 200 and then returns to the heat source side unit 100A.
- the gas refrigerant that has returned to the heat source side unit 100 ⁇ / b> A is again sucked into the compressor 101 via the check valve 112, the four-way switching valve 102, and the accumulator 104.
- the air conditioner 500A executes the cooling only operation mode.
- FIG. 9 is a diagram showing a refrigerant flow when the air-conditioning apparatus 500A according to Embodiment 2 of the present invention is in the cooling main operation mode.
- the load-side unit 300 that performs cooling and the load-side unit 300 that performs heating are mixed, and the load related to cooling is larger than the load related to heating, the operation in the cooling main operation mode is performed.
- the operation of the air conditioner 500A in the cooling main operation mode will be described.
- the operation in the cooling main operation mode when the load side unit 300a performs cooling and the load side unit 300b performs heating will be described.
- Compressor 101 compresses a low-temperature and low-pressure refrigerant and discharges a high-temperature and high-pressure gas refrigerant.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 101 flows into the heat source side heat exchanger 103 via the four-way switching valve 102. Since the heat source side heat exchanger 103 works as a condenser, the refrigerant exchanges heat with the surrounding air to condense and make two-phase. Thereafter, the gas-liquid two-phase refrigerant that has flowed out of the heat source side heat exchanger 103 flows out of the heat source side unit 100A through the high-pressure pipe 404, the check valve 113, and the like.
- the gas-liquid two-phase refrigerant that has flowed out of the heat source side unit 100A flows into the gas-liquid separator 211 of the relay unit 200.
- the gas-liquid two-phase refrigerant that has flowed into the gas-liquid separator 211 is separated into a gas refrigerant and a liquid refrigerant by the gas-liquid separator 211.
- the gas refrigerant flows out from the gas-liquid separator 211 and then flows into the connection pipe 221.
- the gas refrigerant that has flowed into the connection pipe 221 flows through the gas branch pipe 401b via the first on-off valve 212b, and then flows into the load side unit 300b.
- the gas refrigerant that has flowed into the load-side unit 300b heats the air-conditioned space by radiating heat to the surroundings by the load-side heat exchanger 312b, and condenses and liquefies itself and flows out from the load-side heat exchanger 312b.
- the liquid refrigerant that has flowed out of the load-side heat exchanger 312b is throttled to an intermediate pressure by the expansion device 311b.
- the liquid refrigerant of intermediate pressure throttled by the throttle device 311b flows through the liquid branch pipe 402b and passes through the check valve 219b.
- the liquid refrigerant that has passed through the check valve 219b is separated by the gas-liquid separator 211 and merged with the liquid refrigerant that has passed through the first refrigerant heat exchanger 216 and the first expansion device 214, and then the second refrigerant heat exchange.
- the liquid refrigerant that has flowed into the second refrigerant heat exchanger 217 further increases the degree of supercooling and flows out of the second refrigerant heat exchanger 217.
- the refrigerant flowing out from the second refrigerant heat exchanger 217 is divided into two, one passing through the check valve 218a, flowing through the liquid branch pipe 402a, flowing out from the relay unit 200, and the other as the second expansion device. Head to 215.
- the liquid refrigerant flowing out from the relay unit 200 flows into the load side unit 300a.
- the liquid refrigerant that has flowed into the load-side unit 300a is throttled by the throttle device 311a, and becomes a low-temperature gas-liquid two-phase refrigerant.
- This low-temperature gas-liquid two-phase refrigerant flows into the load-side heat exchanger 312a, cools the air-conditioned space by taking heat away from the surroundings, evaporates and vaporizes itself, and flows out from the load-side heat exchanger 312a. To do.
- the gas refrigerant that has flowed out of the load-side heat exchanger 312a flows through the gas branch pipe 401a and out of the load-side unit 300a, and then flows into the relay unit 200.
- the refrigerant that has flowed into the relay unit 200 passes through the second on-off valve 213a.
- the refrigerant that has passed through the second on-off valve 213a merges with the refrigerant that has flowed through the connection pipe 220 via the first expansion device 214 and the second expansion device 215 in order to take supercooling in the second refrigerant heat exchanger 217.
- the refrigerant flowing through the low pressure pipe 403 flows out of the relay unit 200 and then returns to the heat source side unit 100A.
- the gas refrigerant that has returned to the heat source side unit 100 ⁇ / b> A is again sucked into the compressor 101 via the check valve 112, the four-way switching valve 102, and the accumulator 104.
- the air conditioner 500A executes the cooling main operation mode.
- FIG. 10 is a refrigerant circuit diagram illustrating a refrigerant flow in the heating only operation mode of the air-conditioning apparatus 500A according to Embodiment 2 of the present invention. Based on FIG. 10, the operation
- the low-temperature and low-pressure refrigerant is compressed by the compressor 101 and discharged as a high-temperature and high-pressure gas refrigerant.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 101 passes through the four-way switching valve 102 and flows to the high-pressure pipe 404 via the check valve 115. Thereafter, the refrigerant flows out from the heat source side unit 100A.
- the high-temperature and high-pressure gas refrigerant that has flowed out of the heat source unit 100A passes through the gas-liquid separator 211 of the relay unit 200, passes through the connection pipe 221 and passes through the first on-off valves 212a and 212b.
- the high-temperature and high-pressure gas refrigerant that has passed through the first on-off valves 212a and 212b reaches the load-side units 300a and 300b through the gas branch pipes 401a and 401b.
- the liquid refrigerant depressurized by the expansion devices 311a and 311b flows through the liquid branch pipes 402a and 402b, flows out of the load side units 300a and 300b, and then flows into the relay unit 200.
- the liquid refrigerant flowing into the relay unit 200 passes through the check valves 219a and 219b, flows into the pipe between the first expansion device 214 and the second refrigerant heat exchanger 217, and passes through the second refrigerant heat exchanger 217. After passing, the low pressure pipe 403 is reached via the connection pipe 220 via the second expansion device 215.
- the refrigerant flowing through the low pressure pipe 403 flows out of the relay unit 200 and then returns to the heat source side unit 100A.
- the refrigerant that has returned to the heat source side unit 100 ⁇ / b> A passes through the second connection pipe 121 and reaches the heat source side heat exchanger 103 via the check valve 114. Since the heat source side heat exchanger 103 functions as an evaporator, the refrigerant exchanges heat with the surrounding air, and the refrigerant evaporates and gasifies. Thereafter, the refrigerant flowing out of the heat source side heat exchanger 103 flows into the accumulator 104 via the four-way switching valve 102. The compressor 101 sucks the refrigerant in the accumulator 104 and circulates it in the refrigerant circuit, so that a refrigeration cycle is established. With the above flow, the air conditioner 500A executes the heating only operation mode.
- FIG. 11 is a refrigerant circuit diagram illustrating a refrigerant flow in the heating main operation mode of the air-conditioning apparatus 500A according to Embodiment 2 of the present invention. Based on FIG. 11, the operation
- the heating main operation mode when there is a heating request from the load side unit 300a and a cooling request from the load side unit 300b will be described.
- requirement is the same as the time of all heating operation mode, description is abbreviate
- the liquid refrigerant passing through the load-side unit 300a having the heating request and passing through the liquid branch pipe 402a passes through the check valve 219a, and is then supercooled by the second refrigerant heat exchanger 217 to generate the second refrigerant heat. It flows out of the exchanger 217.
- the liquid refrigerant that has flowed out of the second refrigerant heat exchanger 217 is divided into two, one passing through the check valve 218b and reaching the load side unit 300b that requires cooling through the liquid branch pipe 402b, and the other Goes to the second diaphragm 215.
- the refrigerant flowing into the load side unit 300b is decompressed by the expansion device 311b.
- the refrigerant decompressed by the expansion device 311b flows into the load-side heat exchanger 312b.
- the load side heat exchanger 312b works as an evaporator, the refrigerant evaporates and gasifies by exchanging heat with the surrounding air. At this time, the refrigerant cools the room by absorbing heat from the surroundings. Thereafter, the gas refrigerant that has flowed out of the load-side heat exchanger 312b flows through the gas branch pipe 401b, out of the load-side unit 300b, and then flows into the relay unit 200. The refrigerant that has flowed into the relay unit 200 passes through the second on-off valve 213b.
- the refrigerant that has passed through the second on-off valve 213 b merges with the refrigerant that has flowed through the connection pipe 220 via the second expansion device 215 to be supercooled by the second refrigerant heat exchanger 217, and reaches the low-pressure pipe 403. .
- the refrigerant flowing through the low pressure pipe 403 flows out of the relay unit 200 and then returns to the heat source side unit 100A.
- the refrigerant returned to the heat source side unit 100A reaches the heat source side heat exchanger 103 via the check valve 114. Since the heat source side heat exchanger 103 functions as an evaporator, the refrigerant exchanges heat with the surrounding air, and the refrigerant evaporates and gasifies. Thereafter, the refrigerant flowing out of the heat source side heat exchanger 103 flows into the accumulator 104 via the four-way switching valve 102. The compressor 101 sucks the refrigerant in the accumulator 104 and circulates it in the system, so that a refrigeration cycle is established. With the above flow, the air conditioner 500A executes the heating main operation mode.
- the present invention can also be applied to the air conditioner 500A in which the operation mode described above is performed. That is, the refrigerant cooling control shown in the flowchart of FIG. 5 can also be applied to the air conditioner 500A. Thereby, also in the air conditioning apparatus 500A of the second embodiment, the same effect as in the first embodiment can be obtained.
- the connection position of one end on the high-pressure side among the both ends of the bypass pipe 608 is the high-pressure pipe 611, whereas in the bypass pipe 608A of the second embodiment, the high-pressure pipe is connected. In 404, it is downstream of the junction b. Therefore, the refrigerant flow in the refrigerant cooling control is slightly different.
- the flow of the refrigerant in the refrigerant cooling control will be described. Note that the flow of the refrigerant in the refrigerant cooling control is the same in any operation mode, and therefore, here, a description will be given with reference to a diagram illustrating the flow of the refrigerant in the cooling main operation mode.
- FIG. 12 is a refrigerant circuit diagram illustrating a refrigerant flow in the refrigerant cooling control when the air-conditioning apparatus 500A according to Embodiment 2 of the present invention is in the cooling only operation mode.
- the expansion device 602 when the expansion device 602 is opened, a part of the refrigerant from the junction b to the relay unit 200 in the high-pressure pipe 404 is bypassed to the bypass pipe 608A.
- the refrigerant flow after being bypassed to the bypass pipe 608A is the same as that of the bypass pipe 608 of the first embodiment. That is, the refrigerant bypassed to the bypass pipe 608A flows into the precooling heat exchanger 601.
- the liquid refrigerant flowing into the precooling heat exchanger 601 is cooled by exchanging heat with the air from the heat source side fan 106.
- the liquid refrigerant cooled to the low pressure by the pre-cooling heat exchanger 601 is reduced in pressure by the expansion device 602 and further reduced in pressure, and then flows into the refrigerant cooler 603.
- the refrigerant cooler 603 the refrigerant exchanges heat with the control device 118 and evaporates. At this time, the refrigerant absorbs heat from the control device 118 to cool the control device 118.
- the refrigerant that has cooled the control device 118 becomes a gas refrigerant or a two-phase refrigerant, flows through the low-pressure pipe 610, and flows into the accumulator 104.
- an example of the air conditioner 500A having one heat source side unit 100A, one relay unit 200, and two load side units 300 is shown. It is not limited.
- the refrigeration cycle apparatus has been described as an air conditioner.
- the refrigeration apparatus may be a cooling apparatus that cools a refrigerated warehouse or the like.
Abstract
Description
図1は、本発明の実施の形態1に係る空気調和装置500の冷媒回路構成の一例を示す概略構成図である。冷媒冷却の説明の前に、冷凍サイクルでの冷媒の流れについて説明する。本説明では、図1に基づいて、空気調和装置500の冷媒回路構成について説明する。この空気調和装置500は、例えばビル、マンション等に設置され、冷媒を循環させる冷凍サイクル(ヒートポンプサイクル)を利用して、冷房運転又は暖房運転を実行できるものである。
熱源側ユニット100は、負荷側ユニット300に冷熱又は温熱を供給する機能を有している。
負荷側ユニット300は、冷房負荷又は暖房負荷に対し、熱源側ユニット100からの冷熱又は温熱を供給する。例えば、図1では、「負荷側ユニット300a」に備えられている各機器の符号の後に「a」を付加し、「負荷側ユニット300b」に備えられている各機器の符号の後に「b」を付加して図示している。そして、以下の説明においては、符号の後の「a」、「b」を省略する場合があるが、負荷側ユニット300a、負荷側ユニット300bの何れにも各機器が備えられている。
空気調和装置500においては、例えば室内等に設置されたリモートコントローラ等からの冷房要求、暖房要求を受信する。空気調和装置500は、要求に応じて2つの運転モードのうち、何れかの空気調和動作を行う。2つの運転モードとして、冷房運転モードと暖房運転モードとがある。
図2は、本発明の実施の形態1に係る空気調和装置500の冷房運転モード時の冷媒の流れを示す図である。図2に基づいて、冷房運転モード時における空気調和装置500の運転動作について説明する。
図3は、本発明の実施の形態1に係る空気調和装置500の暖房運転モード時の冷媒の流れを示す冷媒回路図である。図3に基づいて、空気調和装置500の暖房運転モード時の運転動作について説明する。
次に、本実施の形態1の特徴部分である冷媒冷却制御について説明する。
冷媒冷却制御では、高圧配管611を通る高圧ガス冷媒の一部がバイパス配管608へバイパスされ、予冷熱交換器601に流入する。予冷熱交換器601に流入した液冷媒は、熱源側ファン106からの空気と熱交換して冷却される。予冷熱交換器601で冷却されて低圧となった液冷媒は、絞り装置602で減圧されて更に低圧となった後、冷媒冷却器603に流入する。冷媒冷却器603において冷媒は制御装置118と熱交換して蒸発する。このとき、冷媒は制御装置118から吸熱することによって制御装置118を冷却する。制御装置118を冷却した冷媒はガス冷媒又は二相冷媒となり、低圧配管610を流れ、アキュムレータ104へ流入する。
(1)温度センサ606と低圧センサ142とのそれぞれの検知値から算出される、冷媒冷却器603出口の過熱度が予め設定した設定値(例えば、2℃)以下
(2)制御装置温度センサ605の検知温度が一定値(E)(例えば、70℃)以下
図7は、本発明の実施の形態2に係る空気調和装置500Aの冷媒回路構成の一例を示す概略構成図である。以下、本実施の形態2の空気調和装置500Aが、図1に示した実施の形態1の空気調和装置500と相違する部分を中心に説明する。
本実施の形態2の空気調和装置500Aは、図1に示した実施の形態1の空気調和装置500の熱源側ユニット100と複数の負荷側ユニット300との間に、中継ユニット200が更に接続された構成を有する。負荷側ユニット300の構成は、実施の形態1と同様である。
中継ユニット200は、冷房運転を実施する負荷側ユニット300には低温冷媒を分配し、暖房運転を実施する負荷側ユニット300には高温冷媒を分配するように、負荷側ユニット300の運転状況に応じて冷媒の流れを切替えるものである。ここで、図7では、中継ユニット200が有するいくつかの機器の符号の後に「a」又は「b」を付加している。これは、「負荷側ユニット300a」に接続しているか、「負荷側ユニット300b」に接続しているかを表している。そして、以下の説明においては、符号の後に付加した添字「a」又は「b」を省略する場合がある。省略した場合は「負荷側ユニット300a」又は「負荷側ユニット300b」に接続されている何れの機器の場合も含んで説明している。
空気調和装置500Aにおいては、例えば室内等に設置されたリモートコントローラ等からの冷房要求、暖房要求を受信する。空気調和装置500Aは、要求に応じて4つの運転モードのうち、何れかの空気調和動作を行う。4つの運転モードは以下の通りである。
(1)負荷側ユニット300が全て冷房運転要求である全冷房運転モード
(2)冷房運転要求と暖房運転要求とが混在しており、かつ冷房運転により処理すべき負荷が多いと判断される冷房主体運転モード
(3)冷房運転要求と暖房運転要求とが混在しており、かつ暖房負荷が多いと判断される暖房主体運転モード
(4)全ての負荷側ユニット300が全て暖房運転要求である全暖房運転モード
図8は、本発明の実施の形態2に係る空気調和装置500Aの全冷房運転モード時の冷媒の流れを示す図である。図8に基づいて、全冷房運転モード時における空気調和装置500Aの運転動作について説明する。図8の第1開閉弁212及び第2開閉弁213において黒塗りは閉、白塗りは開を示している。この点は、後述の各図においても同様である。
図9は、本発明の実施の形態2に係る空気調和装置500Aの冷房主体運転モード時の冷媒の流れを示す図である。冷房を行う負荷側ユニット300と暖房を行う負荷側ユニット300とが混在しており、かつ冷房に係る負荷の方が暖房に係る負荷よりも大きい場合、冷房主体運転モードによる運転を行う。図9に基づいて、冷房主体運転モード時における空気調和装置500Aの運転動作について説明する。ここでは、負荷側ユニット300aが冷房を行い、負荷側ユニット300bが暖房を行う場合の冷房主体運転モードの運転について説明する。
図10は、本発明の実施の形態2に係る空気調和装置500Aの全暖房運転モード時の冷媒の流れを示す冷媒回路図である。図10に基づいて、空気調和装置500Aの全暖房運転モード時の運転動作について説明する。
図11は、本発明の実施の形態2に係る空気調和装置500Aの暖房主体運転モード時の冷媒の流れを示す冷媒回路図である。図11に基づいて、空気調和装置500Aの暖房主体運転モード時の運転動作について説明する。ここでは、負荷側ユニット300aから暖房要求、負荷側ユニット300bから冷房要求があったときの暖房主体運転モードを説明する。なお、熱源側ユニット100Aの圧縮機101から暖房要求のある負荷側ユニット300aまでの冷媒の流れは全暖房運転モード時と同じであるため説明を省略する。
本実施の形態2では、絞り装置602が開かれた場合、高圧配管404において合流部bから中継ユニット200に向かう冷媒の一部が、バイパス配管608Aへバイパスされる。バイパス配管608Aへバイパスされた後の冷媒の流れは実施の形態1のバイパス配管608と同様である。すなわち、バイパス配管608Aへバイパスされた冷媒は、予冷熱交換器601に流入する。予冷熱交換器601に流入した液冷媒は、熱源側ファン106からの空気と熱交換して冷却される。予冷熱交換器601で冷却されて低圧となった液冷媒は、絞り装置602で減圧されて更に低圧となった後、冷媒冷却器603に流入する。冷媒冷却器603において冷媒は制御装置118と熱交換して蒸発する。このとき、冷媒は制御装置118から吸熱することによって制御装置118を冷却する。制御装置118を冷却した冷媒はガス冷媒又は二相冷媒となり、低圧配管610を流れ、アキュムレータ104へ流入する。
Claims (11)
- 圧縮機と熱源側熱交換器と第1絞り装置と負荷側熱交換器とを備え、冷媒が循環する冷媒回路と、
前記冷媒回路を制御する制御装置と、
前記圧縮機から前記第1絞り装置に至る高圧配管から分岐して前記圧縮機の吸入側の低圧配管に接続されたバイパス配管と、
前記バイパス配管に設けられ、前記バイパス配管にバイパスされた冷媒を冷却する予冷熱交換器と、
前記バイパス配管に設けられ、前記予冷熱交換器で冷却された冷媒を減圧する第2絞り装置と、
前記バイパス配管に設けられ、前記第2絞り装置で減圧された冷媒を用いて前記制御装置を冷却する冷媒冷却器と
を備えた冷凍サイクル装置。 - 前記制御装置の温度を検知する制御装置温度センサを更に備え、
前記制御装置は、前記制御装置温度センサの検知温度が予め設定した開始温度以上になると、前記第2絞り装置の開度を開く
請求項1記載の冷凍サイクル装置。 - 前記制御装置は、前記第2絞り装置が開いている状態で、前記制御装置温度センサの検知温度が前記開始温度よりも低い温度に設定された終了温度以下になると、前記第2絞り装置の開度を閉じる
請求項2記載の冷凍サイクル装置。 - 外気温度を検知する外気温度センサを更に備え、
前記制御装置は、前記第2絞り装置が開いている状態で、前記制御装置温度センサの検知温度が前記外気温度センサの検知温度以下になると、前記第2絞り装置の開度を閉じる
請求項2又は請求項3記載の冷凍サイクル装置。 - 前記制御装置は、前記第2絞り装置が開いている状態で、前記制御装置温度センサの検知温度が前記外気温度センサの検知温度よりも高く、且つ、予め設定した目標温度以下の場合、前記第2絞り装置の開度を絞る
請求項4記載の冷凍サイクル装置。 - 前記冷媒冷却器の出口の過熱度を検知する過熱度検知装置を備え、
前記制御装置は、前記第2絞り装置が開いている状態で、前記過熱度検知装置で検知された過熱度に応じて前記第2絞り装置の開度を制御する
請求項2~請求項5の何れか一項に記載の冷凍サイクル装置。 - 前記制御装置は、前記第2絞り装置が開いている状態で、前記制御装置温度センサの検知温度が予め設定した目標温度よりも高く、且つ、前記過熱度検知装置で検知された過熱度が予め設定した設定値より高い場合、前記第2絞り装置の開度を開く
請求項6記載の冷凍サイクル装置。 - 前記制御装置は、前記第2絞り装置が開いている状態で、前記過熱度検知装置で検知された過熱度が予め設定した設定値以下となると、前記第2絞り装置の開度を絞る
請求項6記載の冷凍サイクル装置。 - 前記圧縮機から吐出された冷媒の流れ方向を前記熱源側熱交換器又は前記負荷側熱交換器に切替える流路切替え装置を更に備え、
前記バイパス配管の両端のうちの高圧側の一端が、前記圧縮機と前記流路切替え装置との間の配管に接続されている
請求項1~請求項8の何れか一項に記載の冷凍サイクル装置。 - 前記圧縮機と前記熱源側熱交換器とを有する熱源側ユニットと、
前記第1絞り装置と前記負荷側熱交換器とを有する複数の負荷側ユニットと、
前記熱源側ユニットと複数の前記負荷側ユニットとの間に接続され、冷房運転を実施する前記負荷側ユニットには低温冷媒を分配し、暖房運転を実施する前記負荷側ユニットには高温冷媒を分配する中継ユニットと
を備えた請求項1~請求項8の何れか一項に記載の冷凍サイクル装置。 - 前記圧縮機から吐出された冷媒の流れ方向を前記熱源側熱交換器又は前記負荷側熱交換器に切替える流路切替え装置と、
前記熱源側ユニットと前記中継ユニットとを接続する2本の配管のそれぞれにおける冷媒の流れ方向を、冷房運転及び暖房運転にかかわらず一方向にする整流装置とを備え、
前記バイパス配管の両端のうちの高圧側の一端が、前記2本の配管のうち高圧側の配管において前記整流装置の下流側に接続されている
請求項10記載の冷凍サイクル装置。
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