WO2010116496A1 - Conditionneur d'air de refroidissement et procédé d'introduction de frigorigène à cet effet - Google Patents

Conditionneur d'air de refroidissement et procédé d'introduction de frigorigène à cet effet Download PDF

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Publication number
WO2010116496A1
WO2010116496A1 PCT/JP2009/057159 JP2009057159W WO2010116496A1 WO 2010116496 A1 WO2010116496 A1 WO 2010116496A1 JP 2009057159 W JP2009057159 W JP 2009057159W WO 2010116496 A1 WO2010116496 A1 WO 2010116496A1
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WIPO (PCT)
Prior art keywords
refrigerant
compressor
heat source
heat exchanger
refrigerating
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PCT/JP2009/057159
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English (en)
Japanese (ja)
Inventor
修 森本
博幸 岡野
航祐 田中
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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 JP2011508134A priority Critical patent/JP5306450B2/ja
Priority to PCT/JP2009/057159 priority patent/WO2010116496A1/fr
Priority to GB201109605A priority patent/GB2481128B/en
Publication of WO2010116496A1 publication Critical patent/WO2010116496A1/fr
Priority to HK12102312.3A priority patent/HK1162068A1/xx

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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
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • 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
    • 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
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way 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
    • 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
    • F25B2345/00—Details for charging or discharging refrigerants; Service stations therefor
    • F25B2345/001—Charging refrigerant to a 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
    • F25B2345/00—Details for charging or discharging refrigerants; Service stations therefor
    • F25B2345/003—Control issues for charging or collecting refrigerant to or from a 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
    • F25B2600/00—Control issues
    • F25B2600/21—Refrigerant outlet evaporator temperature

Definitions

  • the present invention relates to a refrigerating and air-conditioning apparatus in which an outdoor unit and an indoor unit are connected by a refrigerant pipe, and more particularly to a technique for automatically filling a refrigerant.
  • Patent Documents 1 and 2 Conventionally, a technique for charging a refrigerant by estimating an excess or deficiency of the amount of refrigerant in the refrigerant circuit of the refrigeration air conditioner from the operation state of the refrigeration cycle has been proposed (for example, Patent Documents 1 and 2).
  • This invention responds to the above-mentioned problems, and proposes a refrigeration air conditioner that can complete refrigerant charging more quickly and more accurately.
  • This invention is a refrigeration air conditioner comprising at least a compressor, a condenser, a throttle device and an evaporator, A refrigerant circuit branched from the discharge side of the compressor and connected to the suction side of the compressor via opening / closing means, and a refrigerant charging switch between the opening / closing means and the suction side of the compressor And a refrigerant charging port connected thereto.
  • At least a compressor, a heat source side heat exchanger, a heat source side unit composed of a four-way valve, a load side unit composed of at least an expansion device and a load side heat exchanger, the heat source side unit, and the load side unit Is a refrigeration air conditioner that is connected by existing refrigerant pipes, A refrigerant circuit branched from the discharge side of the compressor and connected to the suction side of the compressor via opening / closing means, and a refrigerant charging switch between the opening / closing means and the suction side of the compressor And a refrigerant charging port connected thereto.
  • a heat source side unit composed of at least a compressor, a heat source side heat exchanger, a four-way valve and a check valve, a load side unit composed of at least a throttling device and a load side heat exchanger, and at least a gas-liquid separator
  • a diversion controller having a circuit for bypassing from the liquid part to the low pressure part via an opening / closing means for switching between high and low pressure and a throttling device for bypass, and the heat source side unit and the load side unit via the diversion controller
  • a refrigerating and air-conditioning apparatus connected by refrigerant piping, A refrigerant circuit branched from the discharge side of the compressor and connected to the suction side of the compressor via an opening / closing means; A refrigerant filling port connected via a refrigerant filling switch between the opening / closing means and the suction side of the compressor;
  • the heat source side unit and the load side unit are connected to the heat source side heat exchanger and the load side heat exchanger so as to be able to switch between a high pressure pipe and a low pressure pipe via a diversion kit, and the heat source is connected by a liquid pipe.
  • a refrigerating and air-conditioning apparatus formed by connecting a side throttle device and the load side throttle device, A refrigerant circuit branched from the discharge side of the compressor and connected to the suction side of the compressor via opening / closing means, and connected via a refrigerant charging switch between the opening / closing means and the suction side of the compressor And a refrigerant filling port.
  • the liquid refrigerant filled with the heat of the hot gas is evaporated by joining the liquid refrigerant to be charged with the discharged refrigerant (hot gas) discharged from the compressor. Since the main refrigerant circuit is filled in this state, the refrigerant filling can be completed promptly and accurately without taking time to determine the amount of refrigerant in the refrigeration air conditioner.
  • FIG. 1 is a refrigerant circuit diagram of a refrigeration air conditioner according to Embodiment 1 of the present invention.
  • the flowchart of control of the expansion apparatus of the refrigeration air conditioning apparatus which concerns on Embodiment 1 of this invention.
  • coolant automatic charging of the refrigerating and air-conditioning apparatus which concerns on Embodiment 1 of this invention.
  • the refrigerant circuit figure of the refrigerating and air-conditioning apparatus which concerns on Embodiment 2 of this invention.
  • coolant automatic charging of the refrigerating and air-conditioning apparatus which concerns on Embodiment 2 of this invention.
  • FIG. 6 is a refrigerant circuit diagram of a refrigeration air conditioner according to Embodiment 4 of the present invention.
  • cooling operation of the refrigerating air conditioning apparatus which concerns on Embodiment 4 of this invention.
  • the refrigerant circuit figure of the refrigerating and air-conditioning apparatus which concerns on Embodiment 5 of this invention.
  • cooling operation of the refrigerating air conditioning apparatus which concerns on Embodiment 5 of this invention.
  • the refrigerant circuit figure of the refrigerating air-conditioning apparatus which concerns on Embodiment 6 of this invention.
  • coolant automatic filling of the refrigerating air conditioner which concerns on Embodiment 6 of this invention.
  • FIG. 1 shows a refrigerant circuit diagram of a refrigerating and air-conditioning apparatus according to Embodiment 1 of the present invention.
  • 1 is a compressor
  • 2 is a condenser
  • 3 is an expansion device
  • 4 is an evaporator, and these constitute a main refrigerant circuit.
  • a hot gas bypass circuit (refrigerant circuit) is formed which branches the discharge side of the compressor 1 and reaches the intake of the compressor via an on-off valve 5 as a flow path opening / closing means.
  • a refrigerant circuit between the on-off valve 5 on the hot gas bypass circuit and the suction side of the compressor is branched, and a refrigerant filling port 7 is connected via a refrigerant filling on-off valve 6.
  • Reference numeral 8 denotes a pressure sensor that detects a pressure at a high-pressure portion on the discharge side of the compressor 1
  • reference numeral 9 denotes a first temperature sensor that detects a refrigerant temperature on the discharge side of the compressor 1.
  • Reference numeral 10 denotes a second temperature sensor that detects the temperature of the refrigerant at the outlet of the condenser 2
  • reference numerals 11 and 12 denote third and fourth temperature sensors that detect the temperature of the refrigerant at the inlet / outlet of the evaporator 4.
  • FIG. 2 is a flowchart showing an example of the control algorithm of the diaphragm device 3.
  • the operation is started in STEP 1 and the control interval is taken in STEP 2, so that a predetermined time elapses and the process proceeds to STEP 3 after the predetermined time elapses.
  • the inlet / outlet temperature of the evaporator 4 is measured by the third and fourth temperature sensors.
  • the difference SH between the evaporator inlet temperature Tein and the evaporator outlet temperature Teout is calculated.
  • the opening correction value ⁇ LEV of the expansion device 3 is determined according to the difference between the SH calculated in STEP 4 and the target value SHm, and the setting is performed.
  • it is determined whether or not to end the operation is determined. If the operation is ended, the process proceeds to STEP 7 and the operation is ended. If the operation is not ended, the process returns to STEP 2.
  • FIG. 3 is a flowchart showing an algorithm when the refrigerant is automatically charged.
  • STEP 1 in a state where the refrigerant supply cylinder containing the refrigerant is connected to the refrigerant charging port 7, in STEP 1, an operation for adjusting the refrigerant amount is started.
  • a start trigger a service switch provided in the outdoor unit, a remote controller, an external contact input, a control signal from a personal computer or the like is used.
  • the process waits until a predetermined time elapses, and proceeds to STEP3 after the predetermined time elapses.
  • the discharge pressure Pd of the compressor 1 and the refrigerant temperature Tcout at the outlet of the condenser 2 are detected.
  • the difference SC between the saturation temperature Tsat (Pd) of the discharge pressure Pd and the refrigerant temperature Tcout at the outlet of the condenser 2 is calculated.
  • the calculated SC is compared with the SCm of the target value. If SC ⁇ SCm, the process proceeds to STEP6 and the refrigerant amount adjustment is finished.
  • the routine proceeds to STEP 7 where the refrigerant filling on-off valve 6 is opened for a predetermined time, and the refrigerant is filled into the refrigerant circuit from the refrigerant supply cylinder through the refrigerant filling port 7. At the same time, the on-off valve 5 is opened. After filling the refrigerant for a predetermined time in STEP 7, proceed to STEP 2.
  • the refrigerant amount adjustment use a service display, remote control, personal computer for control, lamp display with electrical signals, etc. to notify the outside that the refrigerant amount adjustment has been completed. Good.
  • the on-off valve 5 is also opened so that the high-temperature gas refrigerant discharged from the compressor 1 flows into the hot gas bypass circuit, and the liquid filled from the refrigerant supply cylinder. After mixing with the refrigerant and evaporating it, it merges with the refrigerant flowing through the main circuit on the compressor 1 suction side. For this reason, the liquid refrigerant when the refrigerant is charged can be quickly evaporated without liquid back, so that the determination of the refrigerant amount can also be completed quickly. Moreover, since the dilution of the lubricating oil in the compressor 1 and liquid compression do not occur, a highly reliable system can be achieved.
  • FIG. FIG. 4 shows a refrigerant circuit diagram according to Embodiment 2 of the present invention.
  • the refrigerant filling port 7 has a flow rate control between the on-off valve 5 on the hot gas bypass circuit and the suction side of the compressor 1 instead of the refrigerant filling on-off valve 6. It is connected through a possible second diaphragm device 46.
  • FIG. 5 is a flowchart showing an algorithm when the refrigerant is automatically charged.
  • the operation for adjusting the refrigerant amount is started in STEP 1.
  • STEP2 in order to take a control interval, the process waits until a predetermined time elapses, and proceeds to STEP3 after the predetermined time elapses.
  • STEP 3 the discharge pressure Pd of the compressor 1 and the refrigerant temperature Tcout at the outlet of the condenser 2 are detected.
  • the difference SC between the saturation temperature Tsat (Pd) of the discharge pressure Pd and the outlet refrigerant temperature Tcout of the condenser 2 is calculated.
  • the calculated SC is compared with the SCm of the target value. If SC ⁇ SCm, the process proceeds to STEP6 and the refrigerant amount adjustment is finished.
  • SC ⁇ SCm the process proceeds to STEP 7 where the second expansion device 46 is opened, and the refrigerant is charged into the refrigerant circuit from the refrigerant supply cylinder through the refrigerant filling port 7.
  • the on-off valve 5 is opened.
  • the discharge pressure Pd of the compressor 1 and the discharge refrigerant temperature Td of the compressor 1 are detected.
  • the difference SHd between the discharge refrigerant temperature Td of the compressor 1 and the saturation temperature Tsat (Pd) of the discharge pressure Pd of the compressor 1 is calculated.
  • the opening of the second expansion device 46 is corrected based on ⁇ LEV2 in accordance with the difference between the calculated SHd and the target value SHdm, and the process proceeds to STEP11.
  • STEP 11 if the predetermined time has elapsed, the process returns to STEP 2, and if the predetermined time has not elapsed, the process returns to STEP 7.
  • the liquid flow back to the compressor 1 is controlled by adjusting the charging flow rate with the second throttle device 46 according to the discharge state of the compressor 1.
  • the throttle opening can be increased and the charging flow rate can be maximized within an appropriate range, so that quick refrigerant charging is possible.
  • the method for controlling the flow rate of the refrigerant charged from the refrigerant supply cylinder so that the superheat degree of the refrigerant discharged from the compressor 1 becomes a predetermined target value determined in advance has been described. The same effect can be obtained by using the superheat degree of the refrigerant sucked into the machine 1 as an index.
  • FIG. 6 is a flowchart showing an algorithm for automatic refrigerant charging according to Embodiment 3 of the present invention.
  • the configuration of the refrigerant circuit here is the same as in the first embodiment.
  • STEP 1 in a state where the refrigerant supply cylinder is connected to the refrigerant filling port 7, in STEP 1, an operation for adjusting the refrigerant amount is started.
  • STEP2 in order to take a control interval, the process waits until a predetermined time elapses, and proceeds to STEP3 after the predetermined time elapses.
  • the discharge pressure Pd of the compressor 1 and the refrigerant temperature Tcout at the condenser outlet are detected.
  • STEP 4 the difference SCi between the saturation temperature Tsat (Pd) of the discharge pressure Pd of the compressor 1 and the outlet refrigerant temperature Tcout of the condenser 2 is calculated.
  • STEP 5 the difference ⁇ SC between the SCi calculated this time and the previous calculation result SCi-1 is calculated. However, since there is no previous value for the first time, the previous value is set to 0.
  • STEP 6 it is determined whether or not ⁇ SC is “0”. If “0” is equal to or greater than the predetermined number of times, the refrigerant is not charged, so that the refrigerant supply cylinder is empty or not connected.
  • STEP 7 Proceed to, and issue cylinder replacement signal.
  • FIG. 7 shows a refrigerant circuit diagram of a refrigerating and air-conditioning apparatus according to Embodiment 4 of the present invention.
  • 1 is a compressor
  • 21 is a four-way valve
  • 22 is a heat source side heat exchanger
  • 23 is an accumulator
  • 24 is a refrigerant heat exchanger
  • 26 is an outdoor expansion device
  • 14 is an on-off valve.
  • the main refrigerant circuit of the unit 51 is configured.
  • Reference numeral 13 denotes an on-off valve on a circuit that bypasses the refrigerant heat exchanger 24.
  • the refrigerant heat exchanger and the on-off valve 14 are branched, and a refrigerant circuit between the gas pipe 102 on the gas side and the refrigerant heat exchanger 24 is connected via the expansion device 17. Merge.
  • the pipe branched from the discharge pipe of the compressor 1 is joined to the refrigerant circuit between the four-way valve 21 and the accumulator 23 via the on-off valve 5 and branched between the junction and the on-off valve 5 to provide a refrigerant filling on-off valve.
  • the refrigerant charging port 7 is connected through 6.
  • the pipe connected to the bottom of the accumulator 23 is connected to the recovery device 25 via the on-off valve 15, and the upper portion of the recovery device 25 is connected to the refrigerant circuit between the four-way valve 21 and the accumulator 23 via the on-off valve 16.
  • the piping connected to the bottom of the accumulator 23 branches off from the on-off valve 15 and is connected to the refrigerant circuit between the accumulator 23 and the compressor 1 through the on-off valve 19.
  • 8 is a pressure sensor that detects the pressure at the high-pressure section on the discharge side of the compressor 1
  • 9 is a first temperature sensor that detects the temperature of the refrigerant on the discharge side of the compressor 1.
  • Reference numeral 10 denotes a second temperature sensor that detects the temperature of the refrigerant at the outlet of the heat source side heat exchanger 22.
  • Reference numeral 18 denotes a refrigerant circuit between the four-way valve 21 and the accumulator 23.
  • the fifth temperature sensor is installed downstream of the junction of the hot gas bypass circuit that merges via the on-off valve 5 and detects the refrigerant temperature.
  • Reference numeral 20 denotes a second pressure sensor for detecting the pressure of the refrigerant passing through the liquid pipe 101
  • reference numeral 28 denotes a third pressure sensor for detecting the pressure of the refrigerant passing through the refrigerant circuit between the four-way valve 21 and the accumulator 23.
  • the heat source side unit 51 is configured as described above.
  • 3a and 3b are expansion devices, and 27a and 27b are load-side heat exchangers.
  • 11a and 11b are third temperature sensors that detect the temperature of the refrigerant between the expansion devices 3a and 3b and the load side heat exchangers 27a and 27b, and 12a and 12b are between the load side heat exchanger and the gas pipe 102. It is a 4th temperature sensor which detects the temperature of a refrigerant
  • coolant constitute load-side units 52a and 52b.
  • the subscripts a and b indicate multi-type air conditioners to which a plurality of indoor units are connected.
  • 101 is a liquid pipe
  • 102 is a gas pipe, and these can be pipes embedded in the back of the ceiling used in the existing unit.
  • the liquid pipe 101 and the gas pipe 102 connect the heat source side unit 51 and the load side units 52a and 52b to constitute a refrigerant circuit.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 reaches the heat source side heat exchanger 22 via the four-way valve 21 and is condensed and liquefied.
  • the condensed and liquefied liquid refrigerant is squeezed by the outdoor expansion device 26 so that the detected value of the second pressure sensor 20 is equal to or lower than the pressure resistance of the existing refrigerant pipe, and becomes an intermediate-pressure liquid refrigerant. It is cooled by the heat exchanger 24 and flows to the liquid pipe 101 via the on-off valve 14.
  • the liquid refrigerant that has flowed to the liquid pipe 101 flows to the load side unit while stripping off the foreign matter in the liquid pipe 101 with the flow of the refrigerant.
  • the liquid refrigerant containing the foreign matter flowing to the load side unit is throttled to a low pressure by the expansion devices 3a and 3b, takes heat from the surroundings by the load side heat exchangers 27a and 27b, evaporates and cools itself, and is itself a liquid refrigerant.
  • the refrigerant flows into the gas pipe 102.
  • the gas-liquid two-phase refrigerant that has flowed to the gas pipe 102 flows to the heat source unit 51 while stripping off foreign matter in the gas pipe 102.
  • the gas-liquid two-phase refrigerant containing the foreign material that has returned to the heat source side unit 51 exchanges heat with the high-pressure liquid refrigerant in the refrigerant heat exchanger 24 to become a complete gas refrigerant, and the accumulator via the four-way valve 21. It flows to 23.
  • the gas refrigerant containing the foreign matter flowing into the accumulator 23 is separated in the accumulator 23, and the gas refrigerant returns to the compressor 1.
  • the foreign matter separated in the accumulator 23 flows to the recovery device 25 via the on-off valve 15 and is stored in the recovery device 25.
  • the pressure in the recovery device 25 becomes lower than the pressure of the accumulator 23 by opening the on-off valve 16, and thus the differential pressure Accordingly, the flow of foreign matter from the accumulator 23 to the recovery device 25 occurs.
  • the degree of superheat of the refrigerant at the suction portion of the accumulator 23 calculated from the fifth temperature sensor 18 and the third pressure sensor 28 is determined. This is carried out by controlling the expansion devices 3a and 3b so as to be constant.
  • the control of the refrigeration air conditioner is changed as follows, and the refrigerant amount is confirmed.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 reaches the heat source side heat exchanger 22 via the four-way valve 21 and is condensed and liquefied.
  • the condensed and liquefied liquid refrigerant is squeezed by the outdoor expansion device 26 so that the detected value of the second pressure sensor 20 is equal to or lower than the pressure resistance of the existing refrigerant pipe, and becomes an intermediate-pressure liquid refrigerant.
  • the gas is gasified by being controlled to flow to the gas pipe 102.
  • the gas refrigerant that has flowed to the gas pipe 102 flows to the heat source side unit 51.
  • the gas refrigerant that has returned to the heat source side unit 51 merges with the low-temperature gas-liquid two-phase refrigerant that has flowed through the bypass circuit having the expansion device 17, and then exchanges heat with the high-pressure liquid refrigerant in the refrigerant heat exchanger 24.
  • the state of the refrigerant in the liquid pipe 101 becomes a complete liquid
  • the state of the refrigerant in the gas pipe 102 becomes a complete gas refrigerant, and air conditioning operation is performed. Therefore, the refrigerant amount can be accurately determined.
  • the foreign substance recovery operation is started and the compressor 1 is started.
  • the temperature Td of the refrigerant discharged from the compressor 1 is detected.
  • the refrigerant circuit is filled with only the refrigerant that has been charged in the heat source side unit in advance and the refrigerant for the load side unit that has been filled after evacuation. Therefore, the detected discharge temperature Td is compared with the preset upper limit value Tdmax of the discharge temperature, and when Td> Tdmax, it is determined that the refrigerant is insufficient.
  • the filling on-off valve 6 is opened and filled with refrigerant. If Td ⁇ Tdmax in STEP 3, the process proceeds to STEP 4 to determine whether a predetermined time has elapsed. If the predetermined time has elapsed in STEP4, the process proceeds to STEP6, and if the predetermined time has not elapsed, the process returns to STEP2. In STEP 6, as described above, the control method is changed, and the operation of heating the refrigerant at the load side unit outlet is performed. In STEP 7, it is determined again whether the predetermined time has elapsed.
  • the process proceeds to STEP 8, where the refrigerant discharge pressure Pd discharged from the compressor 1 and the heat source side heat exchanger 22 Detect outlet temperature Tcout.
  • STEP 9 the difference SC between the saturation temperature Tsat (Pd) of Pd and Tcout is calculated, and in STEP 10, the SC and SC target value SCm are compared, and if SC ⁇ SCm, the process proceeds to STEP 11 and the foreign matter collecting operation is completed. If SC ⁇ SCm, the process proceeds to STEP 12, and after opening and closing the on-off valve 5 and the refrigerant filling on-off valve 6 for a predetermined time, the refrigerant is charged from the refrigerant filling port 7, and then the process returns to STEP 7.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 flows into the refrigerant heat exchanger 24 via the four-way valve 21, is cooled by the refrigerant heat exchanger 24, becomes a high-pressure gas-liquid two-phase refrigerant, and enters the gas pipe 102. Flowing. At this time, the high pressure is controlled to a pressure equal to or lower than the pressure resistance of the existing piping by the capacity control of the compressor 1 or the like.
  • the gas-liquid two-phase refrigerant that has flowed to the gas pipe 102 flows to the load-side unit while stripping off foreign matters in the gas pipe 102 with the flow of the refrigerant.
  • the gas-liquid two-phase refrigerant containing foreign matter that has flowed to the load-side unit radiates heat to the surroundings by the load-side heat exchangers 27a and 27b, condenses and heats it, and liquefies itself before being intermediated by the expansion devices 3a and 3b. It is squeezed to a pressure and flows into the liquid pipe 101 as a two-phase refrigerant containing foreign matter.
  • the gas-liquid two-phase refrigerant that has flowed to the liquid pipe 101 flows to the heat source unit 51 while stripping off foreign matter in the liquid pipe 101.
  • the gas-liquid two-phase refrigerant containing the foreign matter that has returned to the heat source side unit 51 flows into the refrigerant heat exchanger 24 via the on-off valve 14 and exchanges heat with the high-pressure gas refrigerant to produce a two-phase refrigerant having a high degree of dryness.
  • the gas refrigerant containing the foreign matter flowing into the accumulator 23 is separated in the accumulator 23, and the gas refrigerant returns to the compressor 1.
  • the foreign matter separated in the accumulator 23 flows to the recovery device 25 via the on-off valve 15 and is stored in the recovery device 25.
  • the pressure in the recovery device 25 becomes lower than the pressure of the accumulator 23 by opening the on-off valve 16, and thus the differential pressure Accordingly, the flow of foreign matter from the accumulator 23 to the recovery device 25 occurs.
  • the degree of superheat of the refrigerant at the outlet of the heat source side heat exchanger 22 is controlled by the outdoor expansion device 26.
  • the control of the refrigeration air conditioner is changed as follows to check the refrigerant amount.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 flows through the four-way valve 21 to the refrigerant heat exchanger 24.
  • the refrigerant does not flow to the low-pressure side, it remains in the state of superheated gas without heat exchange. It flows to the gas pipe 102.
  • the high pressure is controlled to a pressure equal to or lower than the pressure resistance of the existing piping by the capacity control of the compressor 1 or the like.
  • the high-temperature gas refrigerant that has flowed to the gas pipe 102 flows to the load side unit.
  • the high-temperature gas refrigerant that has flowed to the load-side unit radiates heat to the surroundings by the load-side heat exchangers 27a and 27b, condenses and heats it, liquefies itself, and then is throttled to the intermediate pressure by the expansion devices 3a and 3b. Then, the refrigerant flows into the liquid pipe 101 as a two-phase refrigerant containing foreign substances.
  • the gas-liquid two-phase refrigerant that has flowed to the liquid pipe 101 flows to the heat source side unit 51.
  • the gas-liquid two-phase refrigerant containing foreign matter that has returned to the heat source side unit 51 flows so as to bypass the refrigerant heat exchanger 24 via the on-off valve 13, and after being throttled to a low pressure by the outdoor throttling device 26, It flows through the exchanger 22 where it is completely vaporized and flows to the accumulator 23 via the four-way valve 21.
  • the state of the refrigerant in the liquid pipe 101 becomes the same as that in the normal heating operation or slightly close to the liquid, and the state of the refrigerant in the gas pipe 102 is complete. Since the refrigerant becomes a gas refrigerant and is in a distribution state of the refrigerant when the air-conditioning operation is performed, the refrigerant amount can be accurately determined.
  • STEP 1 the foreign substance recovery operation is started and the compressor 1 is started.
  • STEP2 the temperature Td of the refrigerant discharged from the compressor 1 is detected.
  • STEP 3 particularly in the initial state, the refrigerant circuit is filled with only the refrigerant previously charged in the heat source side unit 51 and the refrigerant for the load side unit filled after evacuation.
  • the detected discharge temperature Td is compared with the preset upper limit value Tdmax of the discharge temperature, and if Td> Tdmax, it is determined that the refrigerant is insufficient, and the process proceeds to STEP 5 together with the on-off valve 5.
  • the refrigerant filling on-off valve 6 is opened and the refrigerant is filled from the refrigerant filling port 7. If Td ⁇ Tdmax in STEP 3, the process proceeds to STEP 4 to determine whether a predetermined time has elapsed. If the predetermined time has elapsed in STEP4, the process proceeds to STEP6, and if the predetermined time has not elapsed, the process returns to STEP2.
  • STEP 6 as described above, the control method is changed, and the operation of bypassing the refrigerant heat exchanger 24 on the low pressure side is performed.
  • STEP 7 it is determined again whether the predetermined time has elapsed. If the predetermined time has elapsed, the process proceeds to STEP 8, and the refrigerant discharge pressure Pd discharged from the compressor 1 and the load-side heat exchanger 27a, The average value Tcout_ave of the outlet temperature 27b is detected and calculated.
  • STEP 9 the difference SC between the saturation temperature Tsat (Pd) of Pd and Tcout_ave is calculated.
  • the SC and SC target value SCm are compared. If SC ⁇ SCm, the process proceeds to STEP 11 and the foreign matter recovery operation is completed.
  • the unit when the unit is updated using the existing refrigerant pipe, the unit itself can correctly determine the refrigerant amount and fill the refrigerant even when the shape of the existing pipe is embedded in the wall or ceiling. Therefore, the construction time can be shortened, and the refrigerant amount can be determined regardless of cooling or heating. Therefore, it can be set as the reliable system with respect to the amount of refrigerant
  • FIG. 11 shows a refrigerant circuit diagram of a refrigerating and air-conditioning apparatus according to Embodiment 5 of the present invention.
  • This apparatus includes a heat source side unit 51, load side units 52 a and 52 b, and a shunt controller 53.
  • the configuration of the heat source side unit 51 will be described. 1 is a compressor, 21 is a four-way valve, 22 is a heat source side heat exchanger, 23 is an accumulator, 32a, 32b, 32c and 32d are check valves, which are connected to the main refrigerant circuit of the heat source side unit 51 Configure.
  • the pipe branched from the discharge pipe of the compressor 1 is joined to the refrigerant circuit between the four-way valve 21 and the accumulator 23 via the on-off valve 5, and the junction between the junction and the on-off valve 5 is branched to fill the refrigerant.
  • a refrigerant charging port 7 is connected via the on-off valve 6.
  • Reference numeral 8 denotes a pressure sensor that detects pressure at the high-pressure portion on the discharge side of the compressor 1
  • 9 denotes a first temperature sensor that detects the temperature of the refrigerant on the discharge side of the compressor 1.
  • 3a and 3b are expansion devices, and 27a and 27b are load-side heat exchangers.
  • 11a and 11b are third temperature sensors that detect the temperature of the refrigerant between the expansion devices 3a and 3b and the load side heat exchangers 27a and 27b, and 12a and 12b are between the load side heat exchanger and the gas pipe. It is a 4th temperature sensor which detects the temperature of a refrigerant
  • load-side units 52a and 52b constitute load-side units 52a and 52b.
  • the subscripts a and b indicate multi-type air conditioners to which a plurality of indoor units are connected.
  • Reference numeral 33 denotes a gas-liquid separator.
  • the upper part of the gas-liquid separator 33 is connected to the high-pressure on-off valves 41 a and 41 b, and the lower part of the gas-liquid separator 33 is connected to the first refrigerant heat exchanger 35.
  • the other end of the first refrigerant heat exchanger 35 is connected to the check valves 39a and 39b and the second refrigerant heat exchanger 36 via the expansion device 34.
  • the other end of the second refrigerant heat exchanger 36 is connected to check valves 40a and 40b connected to the expansion devices 3a and 3b of the load side unit.
  • a refrigerant circuit (bypass circuit) branched from between the second refrigerant heat exchanger 36 and the check valves 40a and 40b is connected to the second refrigerant heat exchanger 36 and the first refrigerant via the expansion device 37. After being connected to the low pressure side of the heat exchanger 35, it is connected to the inlet of the low pressure pipe 104. Further, the gas side pipes of the load side heat exchangers 27a and 27b are connected to the upper pipe of the gas-liquid separator 33 via the high pressure on / off valves 41a and 41b, and low pressure via the low pressure on / off valves 42a and 42b. A tube 104 is also connected.
  • the heat source side unit 51 and the load side units 52 a and 52 b are connected via a shunt controller 53. At this time, the heat source side unit 51 and the diversion controller 53 are connected by the high pressure pipe 103 and the low pressure pipe 104, and the diversion controller 53 and the load side units 52a and 52b are connected via the liquid pipe and the gas pipe.
  • the flow of the refrigerant when the refrigerant amount is adjusted and the refrigerant is automatically charged as necessary in the multi-system having this configuration will be described.
  • all indoor units are operated so as to perform cooling.
  • the compressor 1 when the compressor 1 is operated, the high-temperature and high-pressure gas refrigerant is condensed and vaporized in the heat source side heat exchanger 22 via the four-way valve 21 to be in a liquid state.
  • the high-pressure pipe 103 has a large pipe diameter in consideration of the pressure loss during heating, and it is often impossible to enclose the refrigerant to the extent that the entire pipe is filled with liquid, so at the outlet of the condenser (heat source side heat exchanger 22).
  • the refrigerant is not overcooled.
  • the gas-liquid two-phase refrigerant containing some gas flows through the high-pressure pipe 103 and flows into the gas-liquid separator 33.
  • the gas-liquid two-phase refrigerant that has flowed to the gas-liquid separator 33 flows from the lower part of the gas-liquid separator 33 to the first refrigerant heat exchanger 35, and is throttled to an intermediate pressure via the throttle device 34. It is cooled in the heat exchanger 36 until it is completely condensed.
  • a part of the refrigerant is throttled to a low pressure via a throttle device 37, flows through the low pressure side of the second refrigerant heat exchanger 36 and the first refrigerant heat exchanger 35, and has an intermediate pressure gas-liquid two flowing through the high pressure side. It heat-exchanges with the phase refrigerant, evaporates and vaporizes itself, merges with the refrigerant flowing through the main circuit, and flows to the low pressure pipe 104.
  • the expansion device 37 uses the temperature difference between the temperature sensor 44 installed at the inlet of the second refrigerant heat exchanger 36 and the temperature sensor 45 installed on the outlet side of the first refrigerant heat exchanger 35 to generate a refrigerant.
  • the degree of superheat is detected and controlled so that the degree of superheat is constant.
  • the remaining liquid refrigerant supercooled by the second refrigerant heat exchanger 36 flows to the load side unit via the check valves 40a and 40b.
  • the pressure is reduced to a low pressure by the expansion devices 11a and 11b, the heat is removed from the surroundings by the load side heat exchangers 27a and 27b, and the air is evaporated and vaporized.
  • the flow returns to the heat source side unit 51.
  • the gas refrigerant that has returned to the heat source side unit 51 returns to the compressor 1 via the check valve 32 b, the four-way valve 21, and the accumulator 23.
  • FIG. 12 in a state where the refrigerant supply cylinder is connected to the refrigerant filling port 7, the operation for adjusting the refrigerant amount is started in STEP1.
  • a start trigger a service switch provided in the outdoor unit, a remote controller, an external contact input, a control signal from a personal computer or the like is used.
  • STEP2 in order to take a control interval, the process waits until a predetermined time elapses, and proceeds to STEP3 after the predetermined time elapses.
  • the intermediate pressure Pm of the flow dividing controller 53 and the refrigerant temperature Trout in the second refrigerant heat exchanger 36 are detected.
  • the difference SC between the saturation temperature Tsat (Pm) of Pm and the outlet refrigerant temperature Trout of the second refrigerant heat exchanger 36 is calculated.
  • the calculated SC is compared with the SCm of the target value. If SC ⁇ SCm, the process proceeds to STEP6 and the refrigerant amount adjustment is finished.
  • the routine proceeds to STEP 7, where the refrigerant filling on-off valve 6 is opened for a predetermined time, and the refrigerant is filled into the refrigerant circuit from the refrigerant supply cylinder through the refrigerant filling port 7. At the same time, the on-off valve 5 is opened. After filling the refrigerant at STEP 7 for a predetermined time, proceed to STEP 2.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 condenses in the heat source side heat exchanger 22 and then reaches the gas-liquid separator 33 in the diversion controller 53 via the check valve 32 a and the high-pressure pipe 103.
  • the liquid refrigerant that has reached the gas-liquid separator 33 flows from the lower part of the gas-liquid separator 33 to the first refrigerant heat exchanger 35, and is squeezed to an intermediate pressure through the expansion device 34, and then the second refrigerant heat exchange.
  • the vessel 36 It is cooled by the vessel 36 to increase the degree of supercooling, and part of it reaches the load side units 52a and 52b via the check valves 40a and 40b.
  • the liquid refrigerant reaching the load-side units 52a and 52b is throttled to a low pressure by the expansion devices 3a and 3b, flows into the load-side heat exchangers 27a and 27b as a low-temperature gas-liquid two-phase refrigerant, and takes heat from the surroundings. While cooling, it evaporates and vaporizes itself and flows to the low-pressure pipe 104 via the on-off valves 42a and 42b.
  • the remaining liquid refrigerant whose degree of supercooling has been increased by the second refrigerant heat exchanger 36 is throttled by the expansion device 37 to become a low-temperature gas-liquid two-phase refrigerant and the second refrigerant heat exchanger 36 and the second refrigerant heat exchanger 36.
  • the gas refrigerant that has flowed into the first refrigerant heat exchanger 35 exchanged heat with the liquid refrigerant that has flowed from the other flow path in the gas-liquid separator 33, and evaporated and vaporized, and evaporated and vaporized in the load-side heat exchangers 27a and 27b. And then flows through the low-pressure pipe 104 and returns to the compressor 1 via the check valve 32 b, the four-way valve 21 and the accumulator 23.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 is partially condensed in the heat source side heat exchanger 22 to become a high-temperature and high-pressure gas-liquid two-phase refrigerant, and then the check valve 32a and the high-pressure pipe 103 are connected.
  • the gas-liquid separator 33 in the diversion controller 53 it is assumed that the load side unit 52a is in the heating operation and the load side unit 52b is in the cooling operation.
  • the gas-liquid two-phase refrigerant reaching the gas-liquid separator 33 is separated from the gas refrigerant from the upper part of the gas-liquid separator 33 and flows to the load-side heat exchanger 27a via the on-off valve 41a to dissipate heat to the surroundings. While heating, it condenses and liquefies itself, is throttled to an intermediate pressure via the throttle device 3a, and returns to the diversion controller 53.
  • the liquid refrigerant that has returned to the diversion controller 53 is separated by the gas-liquid separator 33, increases supercooling by the first refrigerant heat exchanger 35, and merges with the liquid refrigerant that has been throttled to the intermediate pressure by the throttling device 34.
  • the second refrigerant heat exchanger 36 After the degree of supercooling is further increased by the second refrigerant heat exchanger 36, a part thereof flows to the load side unit 52 b via the check valve 40 b, and the remaining liquid refrigerant flows to the expansion device 37.
  • the liquid refrigerant that has flowed to the load-side unit 52b is throttled to a low pressure by the expansion device 3b, becomes a low-temperature gas-liquid two-phase refrigerant, flows to the load-side heat exchanger 27b, takes heat from the surroundings, and cools itself. Evaporates and vaporizes, and flows to the low-pressure pipe 104 through the on-off valve 42b.
  • the liquid refrigerant that has flowed to the expansion device 37 is throttled by the expansion device 37 and becomes a low-temperature gas-liquid two-phase refrigerant, and then flows to the second refrigerant heat exchanger 36 and the first refrigerant heat exchanger 35 to be gas-liquid.
  • the refrigerant flows through the check valve 32b, the four-way valve 21 and the accumulator 23. Return to Compressor 1.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 flows to the high-pressure pipe 103 via the four-way valve 21 and the check valve 32 c and reaches the gas-liquid separator 33 in the branch controller 53.
  • the load side unit 52a is in the heating operation and the load side unit 52b is in the cooling operation.
  • the high-temperature and high-pressure gas refrigerant that has reached the gas-liquid separator 33 flows from the upper part of the gas-liquid separator 33 to the load-side heat exchanger 27a via the on-off valve 41a, radiates heat to the surroundings, and heats itself.
  • the remaining liquid refrigerant returned to the diversion controller 53 is throttled to a low pressure by the expansion device 37, and then merged with the gas refrigerant evaporated and gas-liquid at the load side heat exchanger 52b, flows through the low pressure pipe 104, and a check valve. It evaporates and vaporizes in the heat source side heat exchanger 22 through 32d, and returns to the compressor 1 through the four-way valve 21 and the accumulator 23.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 flows to the high-pressure pipe 103 via the four-way valve 21 and the check valve 32 c and reaches the gas-liquid separator 33 in the branch controller 53.
  • the high-temperature and high-pressure gas refrigerant that has reached the gas-liquid separator 33 flows from the upper part of the gas-liquid separator 33 to the load-side heat exchangers 27a and 27b via the on-off valves 41a and 41b. At the same time, it condenses and liquefies itself, is throttled to an intermediate pressure via the throttle devices 3a and 3b, and returns to the diversion controller 53.
  • the liquid refrigerant returned to the diversion controller 53 is throttled to a low pressure by the expansion device 37, and then merged with the gas refrigerant evaporated and vaporized by the load side heat exchanger 52b, flows through the low pressure pipe 104, and passes through the check valve 32d. Then, it evaporates and vaporizes in the heat source side heat exchanger 22 and returns to the compressor 1 through the four-way valve 21 and the accumulator 23.
  • FIG. 13 shows a refrigerant circuit diagram of a refrigerating and air-conditioning apparatus according to Embodiment 6 of the present invention.
  • This apparatus includes a heat source side unit 51, load side units 52a and 52b, and diversion kits 54a and 54b.
  • the configuration of the heat source side unit 51 is as follows.
  • Reference numeral 1 denotes a compressor
  • 22 denotes a heat source side heat exchanger
  • 23 denotes an accumulator
  • 26 denotes an outdoor expansion device.
  • the discharge pipe of the compressor 1 is connected to the heat source side heat exchanger 22 via the on-off valve 29b, and is branched in the middle to be connected to the high pressure pipe 103.
  • the inflow pipe of the accumulator 23 is connected to the refrigerant circuit between the on-off valve 29b and the heat source side heat exchanger 22 via the on-off valve 29a, and is branched in the middle to be connected to the low-pressure pipe 104.
  • the other end of the heat source side heat exchanger 22 is connected to the liquid pipe 101.
  • the pipe branched from the discharge pipe of the compressor 1 is joined to the refrigerant circuit between the four-way valve 21 and the accumulator 23 via the opening / closing valve 5, and the refrigerant filling opening / closing is performed between the junction and the opening / closing valve 5.
  • a refrigerant charging port 7 is connected through the valve 6.
  • Reference numeral 8 denotes a pressure sensor that detects pressure at the high-pressure portion on the discharge side of the compressor 1
  • 9 denotes a first temperature sensor that detects the temperature of the refrigerant at the high-pressure portion on the discharge side of the compressor 1.
  • 3a and 3b are expansion devices, and 27a and 27b are load-side heat exchangers.
  • 11a and 11b are third temperature sensors for detecting the temperature of the refrigerant between the expansion devices 3a and 3b and the load side heat exchangers 27a and 27b
  • 12a and 12b are load side heat exchangers 27a and 27b and a diversion kit 54a.
  • 54b is a fourth temperature sensor that detects the temperature of the refrigerant.
  • load-side units 52a and 52b constitute load-side units 52a and 52b.
  • the subscripts a and b indicate multi-type air conditioners to which a plurality of indoor units are connected.
  • the heat source side unit 51 and the load side unit 52 configured as described above are connected to the heat source side heat exchanger 22 and the expansion devices 3a and 3b via the liquid pipe 101, and the load side heat exchangers 27a and 27b are connected to the diversion kit 54a. , 54b to the high pressure pipe 103 and the low pressure pipe 104.
  • the diversion kits 54a and 54b the high-pressure pipe 103 and the load-side heat exchangers 27a and 27b are connected via the on-off valves 30a and 30b, and the low-pressure pipe 104 and the load-side heat exchange are connected via the on-off valves 31a and 31b.
  • Devices 27a and 27b are connected.
  • the flow of the refrigerant when the refrigerant amount is adjusted and the refrigerant is automatically charged as necessary in the multi-system having the above configuration will be described.
  • the operation mode will be described first in the case where all the load side units perform cooling.
  • the compressor 1 when the compressor 1 is operated, the high-temperature and high-pressure gas refrigerant flows into the heat source side heat exchanger 22 via the on-off valve 29b, and is condensed and liquefied.
  • the liquefied liquid refrigerant flows through the liquid pipe 101, flows to the load side units 52a and 52b, is throttled to a low pressure by the expansion devices 3a and 3b, and cools by taking heat from the surroundings by the load side heat exchangers 27a and 27b.
  • the load side unit 52a performs heating and the load side unit 52b performs cooling.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 flows to the heat source side heat exchanger 22 through the on-off valve 29b and flows to the load side unit through the high pressure pipe 103.
  • the gas refrigerant flowing to the heat source side heat exchanger 22 dissipates heat, condenses and liquefies, and the liquefied refrigerant is throttled to an intermediate pressure by the outdoor expansion device 26, flows through the liquid pipe 101, and flows toward the load side unit. .
  • the gas refrigerant that has flowed through the high-pressure pipe 103 flows to the load-side heat exchanger 27a through the on-off valve 30a, dissipates heat to the surroundings, heats it, condenses and liquefies itself, and then expands to an intermediate pressure by the expansion device 3a.
  • the liquid refrigerant that has flowed to the load side unit 52b is throttled to a low pressure by the expansion device 3b, takes heat from the surroundings by the load side heat exchanger 27b, cools, and evaporates and vaporizes itself through the on-off valve 31b. It flows into the low pressure pipe 104 and returns to the heat source side unit 51 and returns to the compressor 1 via the accumulator 23.
  • the operation when the operation mode is a mixture of cooling and heating and a large heating load will be described.
  • the load side unit 52a performs heating and the load side unit 52b performs cooling.
  • the compressor 1 When the compressor 1 is operated, the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 flows through the high-pressure pipe 103 toward the load side unit.
  • the gas refrigerant that has flowed through the high-pressure pipe 103 flows to the load-side heat exchanger 27a via the on-off valve 30a, dissipates heat to the surroundings, heats it, condenses and liquefies itself, and then throttles to an intermediate pressure by the expansion device 3a A part of the liquid refrigerant flows toward the load side unit 52 b, and the remaining liquid refrigerant flows through the liquid pipe 101 to the heat source side unit 51.
  • the liquid refrigerant that has flowed to the load side unit 52b is throttled to a low pressure by the expansion device 3b, takes heat from the surroundings by the load side heat exchanger 27b, cools, and evaporates and vaporizes itself through the on-off valve 31b.
  • the liquid refrigerant that has flowed through the liquid pipe 101 and returned to the heat source side unit 51 is throttled to a low pressure by the outdoor expansion device 26, and is evaporated and vaporized by exchanging heat with the outside air by the heat source side heat exchanger 22.
  • the gas refrigerant that has flowed through the low-pressure pipe 104 passes through and is returned to the compressor 1 through the accumulator 23.
  • FIG. 14 in a state where the refrigerant supply cylinder is connected to the refrigerant filling port 7, the operation for adjusting the refrigerant amount is started in STEP1.
  • a start trigger a service switch provided in the outdoor unit, a remote controller, an external contact input, a control signal from a personal computer or the like is used.
  • STEP2 in order to take a control interval, the process waits until a predetermined time elapses, and proceeds to STEP3 after the predetermined time elapses.
  • the discharge pressure Pd of the compressor 1 and the refrigerant temperature Tcout at the outlet of the heat source side heat exchanger 22 are detected.
  • the difference SC between the saturation temperature Tsat (Pd) of Pd and the refrigerant temperature Tcout at the outlet of the heat source side heat exchanger 22 is calculated.
  • the calculated SC is compared with the SCm of the target value. If SC ⁇ SCm, the process proceeds to STEP6 and the refrigerant amount adjustment is finished.
  • the routine proceeds to STEP 7 where the refrigerant filling on-off valve 6 is opened for a predetermined time, and the refrigerant is filled into the refrigerant circuit from the refrigerant supply cylinder through the refrigerant filling port 7. At the same time, the on-off valve 5 is opened. After filling the refrigerant at STEP 7 for a predetermined time, proceed to STEP 2.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

L'invention porte sur un procédé d'introduction de frigorigène pour un conditionneur d'air de refroidissement comportant un compresseur (1) pour aspirer un frigorigène et évacuer le frigorigène après compression de celui-ci. Le frigorigène évacué du compresseur (1) est ramené au côté aspiration du compresseur (1) par l'intermédiaire d'une soupape tout ou rien (5), et un frigorigène est introduit entre la soupape tout ou rien (5) et le côté aspiration du compresseur (1), à partir d'un orifice d'introduction de frigorigène (7), par l'intermédiaire d'un dispositif tout ou rien d'introduction de frigorigène (6).
PCT/JP2009/057159 2009-04-08 2009-04-08 Conditionneur d'air de refroidissement et procédé d'introduction de frigorigène à cet effet WO2010116496A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2011508134A JP5306450B2 (ja) 2009-04-08 2009-04-08 冷凍空調装置およびその冷媒充填方法
PCT/JP2009/057159 WO2010116496A1 (fr) 2009-04-08 2009-04-08 Conditionneur d'air de refroidissement et procédé d'introduction de frigorigène à cet effet
GB201109605A GB2481128B (en) 2009-04-08 2009-04-08 Refrigeration air-conditioning apparatus and refrigerant charging method therefor
HK12102312.3A HK1162068A1 (en) 2009-04-08 2012-03-07 Refrigeration air-conditioning apparatus and refrigerant charging method therefor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2009/057159 WO2010116496A1 (fr) 2009-04-08 2009-04-08 Conditionneur d'air de refroidissement et procédé d'introduction de frigorigène à cet effet

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Cited By (3)

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JP2012132601A (ja) * 2010-12-20 2012-07-12 Samsung Yokohama Research Institute Co Ltd 冷媒量検知装置
WO2012098582A1 (fr) * 2011-01-20 2012-07-26 三菱電機株式会社 Appareil à cycle de réfrigération
CN103528288A (zh) * 2013-10-24 2014-01-22 Tcl空调器(中山)有限公司 对具有快速接头的空调器充放制冷剂的装置

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CN102788403A (zh) * 2012-07-30 2012-11-21 广东美的电器股份有限公司 检测空调器缺冷媒的方法及空调器
JP2015135192A (ja) * 2014-01-16 2015-07-27 株式会社富士通ゼネラル 空気調和装置

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JP2000028208A (ja) * 1998-07-09 2000-01-28 Komatsu Ltd 冷凍装置の制御装置
JP2003130503A (ja) * 2001-10-22 2003-05-08 Mitsubishi Electric Corp 冷凍・空調システムのリプレース方法
JP2003279203A (ja) * 2002-03-19 2003-10-02 Mitsubishi Electric Building Techno Service Co Ltd 冷媒液チャージ装置及び液冷媒チャージ方法
WO2007049372A1 (fr) * 2005-10-25 2007-05-03 Mitsubishi Electric Corporation Appareil de climatisation, procede de remplissage de refrigerant dans un appareil de climatisation et procede de nettoyage de remplissage/conduite de refrigerant pour climatiseur

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JPH06101940A (ja) * 1992-09-22 1994-04-12 Nippondenso Co Ltd 冷媒封入方法
JP2000028208A (ja) * 1998-07-09 2000-01-28 Komatsu Ltd 冷凍装置の制御装置
JP2003130503A (ja) * 2001-10-22 2003-05-08 Mitsubishi Electric Corp 冷凍・空調システムのリプレース方法
JP2003279203A (ja) * 2002-03-19 2003-10-02 Mitsubishi Electric Building Techno Service Co Ltd 冷媒液チャージ装置及び液冷媒チャージ方法
WO2007049372A1 (fr) * 2005-10-25 2007-05-03 Mitsubishi Electric Corporation Appareil de climatisation, procede de remplissage de refrigerant dans un appareil de climatisation et procede de nettoyage de remplissage/conduite de refrigerant pour climatiseur

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Publication number Priority date Publication date Assignee Title
JP2012132601A (ja) * 2010-12-20 2012-07-12 Samsung Yokohama Research Institute Co Ltd 冷媒量検知装置
WO2012098582A1 (fr) * 2011-01-20 2012-07-26 三菱電機株式会社 Appareil à cycle de réfrigération
JP5762441B2 (ja) * 2011-01-20 2015-08-12 三菱電機株式会社 冷凍サイクル装置
EP2905562A1 (fr) * 2011-01-20 2015-08-12 Mitsubishi Electric Corporation Appareil de circuit de réfrigération
CN103528288A (zh) * 2013-10-24 2014-01-22 Tcl空调器(中山)有限公司 对具有快速接头的空调器充放制冷剂的装置

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JPWO2010116496A1 (ja) 2012-10-11
HK1162068A1 (en) 2012-08-17
GB2481128A (en) 2011-12-14
GB2481128B (en) 2015-04-29
GB201109605D0 (en) 2011-07-20

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