WO2009123190A1 - Climatiseur - Google Patents

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Publication number
WO2009123190A1
WO2009123190A1 PCT/JP2009/056655 JP2009056655W WO2009123190A1 WO 2009123190 A1 WO2009123190 A1 WO 2009123190A1 JP 2009056655 W JP2009056655 W JP 2009056655W WO 2009123190 A1 WO2009123190 A1 WO 2009123190A1
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WO
WIPO (PCT)
Prior art keywords
pressure
temperature
expansion valve
refrigerant
heat exchanger
Prior art date
Application number
PCT/JP2009/056655
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English (en)
Japanese (ja)
Inventor
外囿　圭介
傑 鳩村
裕之 森本
Original Assignee
三菱電機株式会社
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2010505935A priority Critical patent/JPWO2009123190A1/ja
Priority to EP09729048.0A priority patent/EP2290304A4/fr
Publication of WO2009123190A1 publication Critical patent/WO2009123190A1/fr

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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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
    • 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
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • 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
    • F25B2600/11—Fan speed control
    • 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
    • F25B2600/2509—Economiser valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/191—Pressures near an expansion valve

Definitions

  • the present invention relates to an air conditioner in which an outdoor unit and a plurality of indoor units are connected by a shunt controller, and one refrigeration cycle is configured using a supercritical fluid.
  • a heat recovery type air conditioner that simultaneously cools and warms using a supercritical fluid such as CO 2 is known.
  • the outdoor unit and the branch kit are mainly connected by three pipes of a high pressure pipe, a low pressure pipe and a high temperature gas pipe.
  • the branch kit from the branch kit to the indoor unit is a two-pipe type.
  • connection pipes it is conceivable to reduce the number of connection pipes by incorporating a branch kit for each indoor unit in one shunt controller in order to reduce the connection pipes.
  • the air conditioner using a supercritical fluid it is most effective to lower the temperature of the fluid sent to the cooling operation indoor unit and raise the temperature of the fluid sent to the heating operation indoor unit. Realized with low fluid flow rate. For this reason, efficiency (here, COP: Coefficient of Performance) in which the numerator is the capacity of the air conditioner (unit: kW) and the denominator is power consumption (unit: kW) is improved. Therefore, the inlet temperature of the indoor unit, that is, the outlet temperature of the heat source side heat exchanger is basically low during cooling and high during heating.
  • -It is necessary to lower the outlet temperature of the heat source side heat exchanger in order to supply a low temperature fluid to the cooling operation indoor unit.
  • -It is necessary to increase the outlet temperature of the heat source side heat exchanger in order to supply a high-temperature fluid to the heating operation indoor unit.
  • the conventional cooling main operation (refrigeration cycle is simultaneous cooling and heating operation in the cooling cycle) is a heat source side heat exchanger with a certain degree of cooling and heating (for example, a pressure of 10 MPa in the supercritical region, around 40 to 50 ° C. in the Mollier diagram).
  • a certain degree of cooling and heating for example, a pressure of 10 MPa in the supercritical region, around 40 to 50 ° C. in the Mollier diagram.
  • the conventional air conditioner has a problem that COP is lowered when it is operated so as to satisfy both the cooling and heating conditions.
  • the present invention has been made in view of the above points, and an object thereof is to obtain an air conditioner that can improve COP in simultaneous cooling and heating operations.
  • the air conditioning apparatus is an air conditioning system in which an outdoor unit and a plurality of indoor units are connected by a shunt controller, and a single refrigeration cycle is configured using a supercritical fluid.
  • the outdoor unit, the shunt controller Are connected by two pipes of a high pressure pipe and a low pressure pipe, and are connected between the branch flow controller and the plurality of indoor units by two pipes of a high pressure pipe and a low pressure pipe, and the branch flow controller is connected to the outdoor unit.
  • the refrigerant from the indoor unit to the indoor unit is branched and the refrigerant decompressed by the first expansion valve and the refrigerant from the indoor unit merge and flow into the indoor unit.
  • a double pipe heat exchanger for exchanging heat with a relatively low-temperature, low-pressure two-phase refrigerant that is branched and decompressed by a second expansion valve to flow out to the outdoor unit.
  • the number of connecting pipes between the outdoor unit and the branch flow controller and between the branch flow controller and each indoor unit can be greatly reduced, and a large enthalpy difference on the cooling operation indoor unit side can be secured.
  • COP in simultaneous cooling and heating is also improved.
  • FIG. FIG. 1 is a refrigerant circuit diagram at the time of cooling main operation of the air-conditioning apparatus according to Embodiment 1 of the present invention.
  • an outdoor unit 100 and a plurality of indoor units 301 to 303 are connected by a shunt controller 200 to constitute one refrigeration cycle using a supercritical fluid.
  • the outdoor unit 100 mainly includes a compressor 110, a four-way valve 120, a heat source unit side heat exchanger 130, and check valves 141 to 147.
  • the indoor units 301 to 303 include use side (load side) heat exchangers 311 to 313 and expansion valves 321 to 323 as expansion devices.
  • the flow dividing controller 200 mainly includes a first expansion valve 211, a second expansion valve 212, check valves 231 to 233, flow path switching valves 221 to 223, and a double pipe heat exchanger 240.
  • the double tube heat exchanger 240 may be a plate heat exchanger or a microchannel heat exchanger.
  • the outdoor unit 100 and the branch flow controller 200 are connected by two pipes, a high pressure pipe 400 and a low pressure pipe 500, and the high pressure pipe 700 and the low pressure pipe 200 are similarly connected between the branch flow controller 200 and each of the indoor units 301 to 303.
  • Two pipes 800 are connected to each other.
  • the cooling operation is mainly performed, and a cooling-main operation (hereinafter abbreviated as a cooling main operation) of a part of the heating operation is described, but the heating main operation (hereinafter abbreviated as a warm main operation) is described as a four-way valve 120,
  • the flow path is switched by check valves 141 to 147.
  • a high pressure detection means 281, an intermediate pressure detection means 282, a first temperature detection means 291, and a second temperature detection means 292 are shown in the shunt controller 200. Is unnecessary, and is used in Embodiment 2 to be described later.
  • the high-pressure and high-temperature fluid compressed by the compressor 110 is heat-exchanged with the surrounding air through the four-way valve 120 in the heat source unit-side heat exchanger 130 and cooled to a temperature that does not reach the ambient air temperature.
  • the degree of dryness of the Mollier diagram (pressure p-enthalpy h) shown in FIG. 2 is cooled to a temperature in the vicinity of 0.5 (point B in FIG. 2), and the outlet of the heat source side heat exchanger 130 is in a high pressure / intermediate temperature state. .
  • the fluid that has exited the heat source unit side heat exchanger 130 flows into the diversion controller 200 via the high-pressure pipe 400, and the cooling operation indoor units 302 and 303 and the heating operation chamber are flown at the flow path switching valves 221 to 223, respectively. Branch to machine 301.
  • the high-pressure / medium-temperature fluid that has flowed into the load-side heat exchanger 311 from the branch port via the flow path switching valve 223 further exchanges heat with room temperature.
  • the temperature becomes medium (point C in FIG. 2), and the pressure is reduced by the expansion valve 321 (point D in FIG. 2).
  • the refrigerant that has exited the heating operation indoor unit 301 via the low-pressure pipe 800 passes between the first expansion valve 211 and the double-pipe heat exchanger 240 via the check valve 231 in the shunt controller 200 in a state of intermediate pressure and intermediate temperature. Join at.
  • the refrigerant toward the cooling operation indoor units 302 and 303 is reduced from the branch port to the intermediate pressure in the supercritical region slightly lower than the high pressure by the first expansion valve 211 (point E in FIG. 2). It flows into the middle temperature side in the double-pipe heat exchanger 240 in the middle temperature state. Furthermore, the medium-pressure / medium-temperature fluid decompressed by the expansion valve 321 of the heating operation indoor unit 301 joins here and flows into the middle temperature side of the double-pipe heat exchanger 240.
  • the partial fluid that has come out from the middle temperature side of the double-pipe heat exchanger 240 is further branched at the branch port, and is further depressurized by the second expansion valve 212 to become a gas-liquid two-phase low-pressure low-temperature (I in FIG. 2). Point) and flows into the low temperature side in the double-tube heat exchanger 240.
  • the low-pressure low-temperature fluid at the low-temperature side becomes a state of low pressure and medium-temperature dryness (point H in FIG. 2).
  • the medium-pressure medium-temperature fluid on the medium-temperature side is further cooled to become a medium-pressure medium-temperature fluid (point D in FIG. 2) in a low enthalpy state.
  • the further cooled medium pressure medium temperature fluid (point D in FIG. 2) is further depressurized by the expansion valves 322 and 323 on the load side to become a gas-liquid two-phase low pressure and low temperature (point G in FIG. 2).
  • the number of connecting pipes between the outdoor unit 100 and the shunt controller 200 and between the shunt controller 200 and each of the indoor units 301 to 303 can be greatly reduced, and the cooling operation indoor units 302 and 303 side can be reduced.
  • COP during simultaneous cooling and heating is improved.
  • FIG. 3 is a refrigerant circuit diagram at the time of heating main operation of the air-conditioning apparatus according to Embodiment 1 of the present invention.
  • the air conditioning apparatus shown in FIG. 3 has the same configuration as that of the first embodiment shown in FIG.
  • FIG. 3 explains the flow in the refrigerant circuit during the warm main operation.
  • the high-pressure and high-temperature fluid compressed by the compressor 110 flows into the shunt controller 200 via the four-way valve 120, the check valve 145 and the high-pressure pipe 400. Further, the high-pressure and high-temperature fluid branches to the cooling operation indoor units 303 and the heating operation indoor units 301 and 302 at the flow path switching valves 221 to 223 in the flow dividing controller 200, respectively. Further, the flow of the first expansion valve 211 is interrupted in a fully closed state.
  • Refrigerant to the heating operation indoor units 301 and 302 side flows into the load-side heat exchangers 311 and 312 from the branch port in the diversion controller 200 via the flow path switching valves 222 and 223 and the high-pressure pipe 700, and the high-pressure intermediate temperature.
  • the fluid further exchanges heat with room temperature, and becomes a high pressure / intermediate temperature substantially equal to the room temperature (point C in FIG. 2).
  • the refrigerant depressurized by the expansion valves 321 and 322 flows into the diversion controller 200 via the low-pressure pipe 800 and exchanges heat with the first expansion valve 211 and the double pipe via the check valves 231 and 232.
  • the medium 240 is joined at a medium pressure and intermediate temperature state.
  • the refrigerant to the cooling operation indoor unit 303 side flows into the load side expansion valve 323 through the following path.
  • the fluid that has flowed from the heating operation indoor units 301 and 302 to the medium pressure / medium temperature side of the double-pipe heat exchanger 240 through the low-pressure pipe 800 and the check valves 231 and 232 is further branched at the branch port, and a part of the flow rate Is further reduced in pressure by the second expansion valve 212 to become a low pressure and low temperature (point I in FIG. 2), and flows into the low temperature side in the double pipe heat exchanger 240.
  • the low-temperature low-pressure low-temperature fluid is in a low-pressure / medium-temperature dryness state (point H in FIG.
  • the further cooled medium-pressure medium-temperature fluid (point D in FIG. 2) is further depressurized by the load-side expansion valve 323 to become low-pressure and low-temperature, and flows into the load-side heat exchanger 313, thereby As a result, heat is exchanged and the dryness of the low pressure medium temperature is large (point H in FIG. 2).
  • the low pressure / medium temperature fluid exiting the low temperature side of the double-pipe heat exchanger 240 and the low pressure / medium temperature fluid exiting the load side heat exchanger 313 merge to form a low pressure pipe 500, a heat source machine side heat exchanger. 130, Return to the outdoor unit 100 side through the four-way valve 120.
  • one outdoor unit 100 and one shunt controller 200 are connected by two pipes, and the shunt controller 200 and a plurality of indoor units 301 to 303 are connected by two pipes. Therefore, the number of connecting pipes from the shunt controller 200 to each of the indoor units 301 to 303 can be greatly reduced, and a large enthalpy difference on the cooling operation indoor units 302 and 303 side can be secured, thereby improving COP in simultaneous cooling and heating operations. To do.
  • an energy saving operation can be realized in a cooling main operation in which the cooling main operation is partly heating operation.
  • FIG. 2 the same configuration as that of the first embodiment shown in FIGS. 1 and 3 is provided. Further, in FIG. 1 and FIG. 3, the high pressure detection means 281, the intermediate pressure detection means 282, the first temperature detection means 291, and the second temperature detection means that are not required in the first embodiment are included in the shunt controller 200. 292 is provided.
  • Table 1 shows an outline of control in each control mode (full cooling, cooling main, total warming, warm main).
  • the first expansion valve 211 When all the indoor units 301 to 303 are in a cooling only operation (hereinafter, abbreviated as “fully cooled”), the first expansion valve 211 is fully opened, and the expansion valves of the indoor units 301 to 303 Only 321 to 323 performs flow control according to the load.
  • temperature sensors 311a, 312a, and 313a for detecting temperature are provided above the load side heat exchangers 311 to 313. Between the load-side heat exchangers 311 to 313 and the load-side expansion valves 321 to 323, temperature sensors 311b, 312b and 313b for detecting temperature and pressure sensors 311c, 312c and 313c for detecting pressure are provided. ing.
  • the temperature difference between the temperature sensors 311a, 312a, and 313a and the temperature sensors 311b, 312b, and 313b is calculated, and the calculation result is defined as a superheat degree (superheat), and the superheat degree is a predetermined value, for example,
  • the opening degree of the expansion valves 321, 322, and 323 on the load side is adjusted so as to be about 2 ° C.
  • differential pressure control which will be described later, using the differential pressures of the high pressure detection means 281 and the intermediate pressure detection means 282 is performed. Even in the cold main operation, when the load-side heat exchanger acts as an evaporator, the load-side expansion valve opening is adjusted to a predetermined degree of superheat while detecting the degree of superheat described above.
  • the first expansion valve 211 When all the indoor units 301 to 303 are in a heating operation that is a heating operation (hereinafter abbreviated as “fully warm”), the first expansion valve 211 is basically in a fully closed state, The flow rate control according to the load is performed only by the expansion valves 321 to 323 of the machine, and the differential pressure control described later using the differential pressure of the high pressure detecting means 281 and the intermediate pressure detecting means 282 is performed.
  • temperature sensors 311b, 312b and 313b for detecting temperature and pressure sensors 311c, 312c and 313c for detecting pressure are provided. Yes.
  • the saturation temperature T sc is calculated from the pressure values detected by the pressure sensors 311c, 312c, and 313c.
  • the calculated saturation temperature is defined as a condensation temperature Tc . It is necessary to prepare a relational expression between the saturation temperature T sc and the pressure P as shown in the formula (1) in advance.
  • T sc f (P) (1)
  • a virtual condensing temperature T c is calculated from the pressure values obtained from the pressure sensors 311b, 312b, and 313b using the equation (1).
  • a difference (T c ⁇ T L ) between the temperature T L obtained from the temperature sensors 311b, 312b, and 313b and the virtual condensing temperature T c is obtained, and this value is set as the degree of supercooling SC (subcool).
  • the opening degree of the expansion valves 321, 322, and 323 on the load side is adjusted so that the degree of supercooling SC becomes a predetermined value, for example, about 5 ° C.
  • the fully closed state is basically set, and the differential pressure between the high pressure detection means 281 and the intermediate pressure detection means 282 is changed.
  • the differential pressure control used later is performed.
  • the first expansion valve 211 is always in a fully opened state, and the flow rate control corresponding to the load is performed only by the expansion valves 321 to 323 of the indoor units.
  • the operation is started from a preset initial opening degree L0 (step S41), and a predetermined time from the start. After a lapse of U (step S42), according to the comparison between the differential pressure ⁇ P of the detected value of the high pressure detecting means 281 and the intermediate pressure detecting means 282 and the preset set values P1, P2 (P1 ⁇ P2) The opening degree of the 1 expansion valve 211 is controlled.
  • the first expansion valve 211 when ⁇ P> P2, the first expansion valve 211 is increased by a predetermined opening degree set in advance (steps S43 ⁇ S44), and when P1 ⁇ ⁇ P ⁇ P2, the first expansion valve 211 is opened at the current opening degree. (Step S43 ⁇ S45 ⁇ S46), and when P1 ⁇ P, the first expansion valve 211 is lowered by a predetermined opening degree (steps S43 ⁇ S45 ⁇ S47 ⁇ S48).
  • the first expansion valve 211 In the “fully warm” operation, the first expansion valve 211 is always in a fully closed state, and the flow rate is controlled according to the load only with the expansion valves 321 to 323 of the indoor unit.
  • the “warm main” operation starts from the fully closed state of the first expansion valve 211 with the start of the compressor 110 as a trigger (step S51), and starts a predetermined time U from the start.
  • the first expansion is performed in accordance with the comparison between the differential pressure ⁇ P between the detection values of the high pressure detection means 281 and the intermediate pressure detection means 282 and preset values P1, P2 (P1 ⁇ P2).
  • the opening degree of the valve 211 is controlled.
  • the first expansion valve 211 is increased by a predetermined opening degree set in advance (steps S53 ⁇ S54), and when P1 ⁇ ⁇ P ⁇ P2, the first expansion valve 211 is currently opened. (Step S53 ⁇ S55 ⁇ S56), and if P1 ⁇ P, the first expansion valve 211 is lowered by a predetermined opening degree (steps S53 ⁇ S55 ⁇ S57 ⁇ S58).
  • the above control ensures the necessary differential pressure to flow the refrigerant flow according to the load on the heating operation indoor unit side, and applies the differential pressure more than necessary, thereby reducing the inlet pressure of the cooling operation indoor unit.
  • the necessary differential pressure sufficient to allow the refrigerant flow rate corresponding to the load to flow in the cooling operation indoor unit can be secured, and as a result, it is possible to suppress a COP decrease.
  • a change in pressure can be suppressed, and the refrigerant can be stably sent to the indoor unit, so that energy saving operation and comfort can be realized.
  • Embodiment 3 FIG. In the third embodiment, the same configuration as the configuration of the first embodiment shown in FIG. 1 and FIG. Further, in FIG. 1 and FIG. 3, the high pressure detection means 281, the intermediate pressure detection means 282, the first temperature detection means 291, and the second temperature detection means that are not required in the first embodiment are included in the shunt controller 200. 292 is provided.
  • the refrigerant flow is the same as in the first embodiment.
  • Table 1 shows an outline of control in each control mode (full cooling, cool main, full warm, warm main).
  • the second expansion valve 212 uses the first temperature detection means 291 and the second temperature detection means 292, which will be described later. Superheat) control is performed, and on the indoor units 301 to 303 side, the expansion valves 321 to 323 perform flow rate control according to the load.
  • the “cooling main” operation in which the cooling and heating operations are performed simultaneously in the cooling cycle state is the same as “full cooling”.
  • the second expansion valve 212 When all the indoor units 301 to 303 are in the “fully warm” operation, which is a heating operation, the second expansion valve 212 is kept fully open, and the flow rate corresponding to the load is set by the expansion valves 321 to 323 of the indoor units.
  • the refrigerant that has been controlled and exchanged heat with the load side flows into the outdoor unit low-pressure line via the second expansion valve 212.
  • the differential pressure between the high pressure detection means 281 and the intermediate pressure detection means 282 is used as the fully closed state. Perform differential pressure control.
  • the “all-cooling” operation starts from the initial opening L0 set in advance by using the start of the compressor 110 as a trigger (step S61), and starts for a predetermined time from the start.
  • the temperature difference ⁇ T (superheat) of the detected values is calculated using the first temperature detecting means 291 and the second temperature detecting means 292, and the temperature difference ⁇ T is set to T1, which is set in advance.
  • the opening degree of the second expansion valve 212 is controlled according to the comparison with T2 (T1 ⁇ T2).
  • the second expansion valve 212 when ⁇ T> T2, the second expansion valve 212 is increased by a predetermined opening degree set in advance (steps S63 ⁇ S64), and when T1 ⁇ ⁇ T ⁇ T2, the second expansion valve 212 is currently opened. (Step S63 ⁇ S65 ⁇ S66), and when T1 ⁇ T, the second expansion valve 212 is lowered by a predetermined opening degree (steps S63 ⁇ S65 ⁇ S67 ⁇ S68).
  • the refrigerant temperature at the cooling operation indoor unit side inlet is cooled, and a necessary enthalpy difference sufficient to satisfy the performance can be secured, so that it is possible to suppress the decrease in COP. Further, even in the cooling main operation in which the cooling main operation is a partial heating operation, a lower temperature refrigerant can be sent to the cooling operation indoor unit, and an energy saving operation can be realized.
  • the second expansion valve 212 In the “fully warm” operation, the second expansion valve 212 is always fully opened, the flow rate is controlled according to the load by the expansion valves 321 to 323 of the indoor units, and the refrigerant exchanging heat with the load side is It flows into the outdoor unit low pressure line through the second expansion valve 212.
  • the “warm main” operation starts from the fully closed state triggered by the start of the compressor 110 (step S71), and after a predetermined time U has elapsed from the start (step S72).
  • the opening degree of the second expansion valve 212 is determined in accordance with a comparison between the pressure difference ⁇ P detected by the high pressure detection means 281 and the intermediate pressure detection means 282 and preset values P1, P2 (P1 ⁇ P2). To control.
  • the second expansion valve 212 is lowered by a predetermined opening degree set in advance (steps S73 ⁇ S74), and if P1 ⁇ ⁇ P ⁇ P2, the second expansion valve 212 is currently opened. (Step S73 ⁇ S75 ⁇ S76), and when P1 ⁇ P, the second expansion valve 212 is increased by a predetermined opening degree (steps S73 ⁇ S75 ⁇ S77 ⁇ S78).
  • the necessary differential pressure that allows the refrigerant flow rate to flow according to the load on the heating operation indoor unit side is secured, and the differential pressure more than necessary is applied (the intermediate pressure approaches low pressure), thereby cooling the system.
  • the inlet pressure of the operating indoor unit approaches a low pressure, and the required differential pressure sufficient to flow the refrigerant flow rate corresponding to the load cannot be secured in the cooling operation indoor unit, and as a result, it is possible to suppress a COP decrease.
  • the heat source machine side heat exchanger 130 acts with a condenser (heat radiator).
  • the cooling load is higher than the heating load, it is necessary to radiate a part of the heat radiation capability with the heat source unit side heat exchanger 130. For that purpose, it is necessary to divide the fan speed and the heat source device side heat exchanger 130 to increase or decrease the heat exchanger capacity.
  • a pressure sensor 900 and a temperature sensor 901 are provided between the heat source device side heat exchanger 130 and the check valve 141, and a temperature sensor 902 is provided at the inlet of the heat source device side heat exchanger 130. . In supercritical, if temperature and pressure are determined, enthalpy is uniquely determined.
  • a is the enthalpy H 1 at the inlet of the heat source machine side heat exchanger 130
  • b is the enthalpy H 2 at the outlet of the heat source machine side heat exchanger 130 (inlet of the load side heat exchanger in the heating operation)
  • c Is the enthalpy H 3 at the inlet of the heat source machine side heat exchanger 130.
  • Equation (3) Equation (3)
  • the enthalpy H 2 at the outlet of the heat source device side heat exchanger is determined.
  • the enthalpy at the heat source side heat exchanger outlet can be obtained from the pressure sensor 900 and the temperature sensor 901.
  • the enthalpy obtained from the equation (3) is set as the target enthalpy H 2m .
  • the enthalpy measured by the pressure sensor 900 and the temperature sensor 901 is assumed to be H 2s .
  • -epsH 2 ⁇ H s ⁇ epsH 2 (where -epsH 2 and epsH 2 indicate the lower limit value and the upper limit value of the error range) to be a predetermined value by the control means by the heat source side fan (blower) Increase or decrease the rotation of.
  • -epsH 2 > ⁇ H s the fan speed is increased, and when ⁇ H s > epsH 2 , the fan speed is decreased.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Climatiseur dont les coefficients de performance de refroidissement et de chauffage sont améliorés. Dans un système de climatisation dans lequel une unité extérieure (100) et des unités intérieures (301 à 303) sont interconnectées par un contrôleur de division de flux (200), et un cycle unique de réfrigération est obtenu en utilisant un fluide supercritique, l'unité de sortie (100) et le contrôleur de division de flux (200) sont interconnectés par deux conduites de canalisation qui sont une canalisation à haute pression (400) et une canalisation à basse pression (500), et le contrôleur de division de flux (200) et les unités intérieures (301 à 303) sont interconnectés par deux conduites de canalisation qui sont une canalisation à haute pression (700) et une canalisation à basse pression (800). Le contrôleur de division de flux (200) possède un échangeur thermique à double tube (240) pour échanger de la chaleur entre un réfrigérant à deux phases à pression intermédiaire et un réfrigérant à deux phases à basse pression. Le réfrigérant à deux phases à pression intermédiaire est un réfrigérant ayant une température relativement haute, et les réfrigérants provenant des unités intérieures et un réfrigérant qui est généré en détournant un réfrigérant depuis l'unité extérieure vers les unités intérieures et en réduisant la pression de ce réfrigérant au moyen d'un premier détendeur (211) sont amenés à fusionner pour donner le réfrigérant à deux phases à pression intermédiaire. Le réfrigérant à deux phases à basse pression est un réfrigérant ayant une température relativement basse et généré en détournant un réfrigérant circulant dans les unités intérieures, en réduisant la pression de ce réfrigérant par un second détendeur (212), et en amenant ce réfrigérant à circuler hors de l'unité extérieure.
PCT/JP2009/056655 2008-03-31 2009-03-31 Climatiseur WO2009123190A1 (fr)

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GB2450755B (en) 2007-07-06 2012-02-29 Greenfield Energy Ltd Geothermal energy system and method of operation
GB2461029B (en) 2008-06-16 2011-10-26 Greenfield Energy Ltd Thermal energy system and method of operation
GB2488797A (en) * 2011-03-08 2012-09-12 Greenfield Master Ipco Ltd Thermal Energy System and Method of Operation
EP2833086B1 (fr) * 2012-03-27 2017-06-21 Mitsubishi Electric Corporation Dispositif de climatisation
JP5759080B2 (ja) * 2012-10-01 2015-08-05 三菱電機株式会社 空気調和装置
JP6413692B2 (ja) * 2014-11-21 2018-10-31 株式会社富士通ゼネラル 空気調和装置
CN104776630B (zh) * 2015-04-28 2017-05-03 广东美的暖通设备有限公司 多联机系统
WO2017179166A1 (fr) * 2016-04-14 2017-10-19 三菱電機株式会社 Dispositif de climatisation
CN109445494B (zh) * 2018-10-10 2020-04-28 珠海格力电器股份有限公司 一种焓差实验室干球工况自动控制方法
JP2024078026A (ja) * 2022-11-29 2024-06-10 パナソニックＩｐマネジメント株式会社 蒸気圧縮式冷凍サイクル装置

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JP2004245480A (ja) * 2003-02-13 2004-09-02 Calsonic Kansei Corp 超臨界冷媒を用いた冷凍サイクルの圧力制御装置及び圧力制御方法

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WO2009122512A1 (fr) 2009-10-08

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