EP3130870B1 - Dispositif de réfrigération/climatisation - Google Patents

Dispositif de réfrigération/climatisation Download PDF

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Publication number
EP3130870B1
EP3130870B1 EP16183268.8A EP16183268A EP3130870B1 EP 3130870 B1 EP3130870 B1 EP 3130870B1 EP 16183268 A EP16183268 A EP 16183268A EP 3130870 B1 EP3130870 B1 EP 3130870B1
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EP
European Patent Office
Prior art keywords
discharge temperature
discharge
expansion valve
temperature
compressor
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EP16183268.8A
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German (de)
English (en)
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EP3130870A1 (fr
Inventor
Hiroyuki Yamada
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Mitsubishi Heavy Industries Thermal Systems Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Definitions

  • the present invention relates to a refrigeration / air-conditioning device using a refrigerant whose discharge temperature Td easily increases, e.g., an R32 refrigerant.
  • a liquid floodback to a compressor is prevented by controlling the aperture of an expansion valve so that a degree of suction gas superheat SH becomes constant, to ensure reliability.
  • an R32 refrigerant or a mixed refrigerant rich in R32 refrigerant which has a global warming potential (GWP) as low as approximately one-third that of an R410A refrigerant and an ozone depletion potential (ODP) of zero (hereinafter simply referred to as an R32 refrigerant) has been used in recent years to reduce an environmental load.
  • GWP global warming potential
  • ODP ozone depletion potential
  • the discharge temperature Td of the R32 refrigerant is higher by 10°C to 20°C than that of the R410A refrigerant due to its physical properties.
  • the discharge temperature Td thereof can be controlled to within a temperature range where no breakdown occurs in a compressor motor in a normal utilization range, as illustrated in a Mollier diagram of FIG. 6 .
  • the discharge temperature Td thereof exceeds a temperature at which a breakdown occurs in the compressor motor in control at the predetermined degree of suction gas superheat SH, as illustrated in a Mollier diagram of FIG.
  • Japanese Unexamined Patent Application, Publication No. 2001-174075 discusses a configuration in which the aperture of an electronic expansion valve (EEV) is controlled so that the degree of suction gas superheat SH becomes a predefined temperature while the aperture of the electronic expansion valve (EEV) is controlled based on a discharge temperature Td of a compressor when the discharge temperature Td exceeds an upper-limit value.
  • 2014-190632 discusses a configuration in which the rotational speed of a compressor is adjusted so that the compression ratio of the compressor becomes lower than an upper-limit value to set the degree of drying of a refrigerant at an inlet of the compressor to 0.85 or more while the aperture of an electronic expansion valve (EEV) is adjusted so that a degree of discharge superheat TdSH comes closer to a target value.
  • Document JP2014190632 A discloses a refrigeration / air-conditioning device according to the preamble of claim 1 and claim 3 respectively.
  • the present invention has been made in view of such a circumstance, and is directed to providing a refrigeration / air-conditioning device capable of ensuring an appropriate operation condition for changes in an operation condition and an operation point only by control of the aperture of an electronic expansion valve while ensuring reliability by operating a compressor within a utilization limit.
  • a refrigeration / air-conditioning device adopts the following solutions.
  • a refrigeration / air-conditioning device including a refrigeration cycle in which at least a compressor, a heat source-side heat exchanger, an electronic expansion valve, and a utilization-side heat exchanger are connected via refrigerant piping and which is filled with a refrigerant whose discharge temperature Td more easily increases than that of an R410A refrigerant, a discharge temperature sensor and a suction temperature sensor, and an expansion valve control means which controls the aperture of the electronic expansion valve at a predetermined degree of suction gas superheat SH when the discharge temperature Td is not more than an upper-limit value and controls the aperture of the electronic expansion valve at a predetermined degree of discharge superheat TdSH or a predetermined discharge temperature Td when the discharge temperature Td exceeds the upper-limit value
  • the expansion valve control means includes a target value switching means which switches, when the expansion valve control means is performing the control at the predetermined degree of discharge superheat TdSH while controlling the aperture of the expansion valve
  • the aperture of the electronic expansion valve is controlled at the predetermined degree of suction gas superheat SH when the discharge temperature Td of a refrigerant discharged from the compressor during an operation is not more than a previously set upper-limit value, and the aperture of the electronic expansion valve is controlled at the predetermined degree of discharge superheat TdSH or the predetermined discharge temperature Td when the discharge temperature Td exceeds the upper-limit value.
  • the discharge temperature Td is prevented from exceeding a utilization upper-limit value, and the insulation grade of a compressor motor is made usable as it is so that an increase in cost can be avoided while the discharge temperature Td is made difficult to increase so that refrigerant oil can be prevented from deteriorating.
  • the control at the predetermined degree of discharge superheat TdSH is being performed, the control at the predetermined degree of discharge superheat TdSH is switched to the control at the predetermined degree of discharge superheat TdSH or the control at the predetermined discharge temperature Td using the lower one of the target degree of discharge superheat TdSH obtained by calculation from the rotational speed of the compressor and the high pressure saturation temperature and the upper-limit value of the discharge temperature Td as a target value.
  • the target discharge temperature Td obtained by calculation from the rotational speed of the compressor and the high pressure saturation temperature is compared with the upper-limit value, and the lower one of the target discharge temperature Td and the upper-limit value is adopted as the target discharge temperature Td.
  • the aperture of the electronic expansion valve can be controlled using the lower one of the utilization upper-limit value of the discharge temperature Td to be permitted and the target degree of discharge superheat TdSH plus the high pressure saturation temperature as a target value. Therefore, the discharge temperature Td is suppressed to not more than the utilization upper-limit value of the compressor so that a utilization limit can be reliably protected.
  • the expansion valve control means further includes a target value varying means which varies the target degree of discharge superheat TdSH or the target discharge temperature Td depending on the rotational speed of the compressor.
  • the expansion valve control means further includes the target value varying means which varies the target degree of discharge superheat TdSH or the target discharge temperature Td depending on the rotational speed of the compressor. Therefore, when the rotational speed of the compressor decreases so that the compression ratio decreases while the aperture of the electronic expansion valve is being controlled at the predetermined degree of discharge superheat TdSH or the predetermined discharge temperature Td, the aperture of the electronic expansion valve is excessively throttled. As a result, the degree of suction gas superheat SH becomes too high, resulting in a degraded heat exchange performance.
  • the electronic expansion valve is prevented from being excessively throttled so that an appropriate operation condition can be maintained. Therefore, the degradation of the heat exchange performance occurring because of the degree of suction gas superheat SH becoming too high is suppressed, enabling the refrigeration / air-conditioning device to perform efficient operations.
  • a refrigeration / air-conditioning device including a refrigeration cycle in which at least a compressor, a heat source-side heat exchanger, an electronic expansion valve, and a utilization-side heat exchanger are connected via refrigerant piping and which is filled with a refrigerant whose discharge temperature Td more easily increases than that of an R410A refrigerant, a discharge temperature sensor and a suction temperature sensor, and an expansion valve control means which controls the aperture of the electronic expansion valve at a predetermined degree of suction gas superheat SH when the discharge temperature Td is not more than an upper-limit value and controls the aperture of the electronic expansion valve at a predetermined degree of discharge superheat TdSH or a predetermined discharge temperature Td when the discharge temperature Td exceeds the upper-limit value
  • the expansion valve control means further comprises a target value varying means which varies a target degree of discharge superheat TdSH or a target discharge temperature Td depending on the rotational speed of the compressor.
  • the aperture of the electronic expansion valve is controlled at the predetermined degree of suction gas superheat SH when the discharge temperature Td of a refrigerant discharged from the compressor during an operation is not more than a previously set upper-limit value, and the aperture of the electronic expansion valve is controlled at the predetermined degree of discharge superheat TdSH or the predetermined discharge temperature Td when the discharge temperature Td exceeds the upper-limit value.
  • the discharge temperature Td is prevented from exceeding a utilization upper-limit value, and the insulation grade of a compressor motor is made usable as it is so that an increase in cost can be avoided while the discharge temperature Td is made difficult to increase so that refrigerant oil can be prevented from deteriorating.
  • the aperture of the electronic expansion valve is being controlled at the predetermined degree of discharge superheat TdSH or the predetermined discharge temperature Td, when the rotational speed of the compressor decreases so that the compression ratio decreases, the aperture of the electronic expansion valve is excessively throttled. As a result, the degree of suction gas superheat SH becomes too high, resulting in a degraded heat exchange performance.
  • the electronic expansion valve is prevented from being excessively throttled so that an appropriate operation condition can be maintained. Therefore, the degradation of the heat exchange performance occurring because of the degree of suction gas superheat SH becoming too high is suppressed, enabling the refrigeration / air-conditioning device to perform efficient operations.
  • the increase in cost can be avoided when the discharge temperature Td is prevented from exceeding the utilization upper-limit value and the insulation grade of the compressor motor is made usable as it is while the refrigerant oil can be prevented from deteriorating when the discharge temperature Td is made difficult to increase.
  • the aperture of the electronic expansion valve can be controlled using the lower one of the utilization upper-limit value of the discharge temperature Td to be permitted and the target degree of discharge superheat TdSH plus the high pressure saturation temperature as the target value. Therefore, the discharge temperature Td is suppressed to not more than the utilization upper-limit value of the compressor so that the utilization limit can be reliably protected.
  • the aperture of the electronic expansion valve is excessively throttled.
  • the degree of suction gas superheat SH becomes too high, resulting in the degraded heat exchange performance.
  • the electronic expansion valve is prevented from being excessively throttled so that the appropriate operation condition can be maintained. Therefore, the degradation of the heat exchange performance occurring because of the degree of suction gas superheat SH becoming too high is suppressed, enabling the refrigeration / air-conditioning device to perform efficient operations.
  • FIGS. 1 to 5 An embodiment of the present invention will be described below with reference to FIGS. 1 to 5 .
  • FIG. 1 is a refrigerant circuit diagram of a refrigeration / air-conditioning device according to an embodiment of the present invention.
  • the refrigeration / air-conditioning device 1 includes a heat source-side unit (outdoor unit) 2 installed outdoors, and a utilization-side unit (indoor unit) 3 installed in an indoor space to be air-conditioned, which are connected to each other via liquid-side piping 4 and gas-side piping 5.
  • the heat source-side unit (outdoor unit) 2 includes pieces of equipment such as a compressor 6 which compresses a refrigerant, a four-direction switching valve 7 which switches a circulation direction of the refrigerant, a heat source-side heat exchanger (outdoor heat exchanger) 8 which exchanges heat between the refrigerant and ambient air, an electronic expansion valve for heating (EEVH) 9 which depressurizes the refrigerant during heating, a receiver 10 which temporarily stores a liquid refrigerant, an electronic expansion valve for cooling (EEVC) 11 which depressurizes the refrigerant during cooling, a liquid-side operated valve 12 used to connect the liquid-side piping 4, a gas-side operated valve 13 used to connect the gas-side piping 5, and an accumulator 14 which separates a liquid and sucks only a gas refrigerant into the compressor 6.
  • the pieces of equipment are connected, as illustrated, via refrigerant piping 15, to constitute a heat source-side refrigerant circuit 16.
  • the heat source-side refrigerant circuit 16 in the heat source-side unit 2 is provided with a high pressure opening/closing unit 17 which opens and closes at the predetermined pressure of high pressure refrigerant gas discharged from the compressor 6 and a discharge temperature sensor (Td temperature sensor) 18 which detects the temperature of the high pressure refrigerant gas discharged from the compressor 6 for refrigerant discharge piping 15A from the compressor 6 while being provided with a low pressure sensor 19 which detects the pressure of low pressure refrigerant gas to be sucked into the compressor 6 and a suction temperature sensor 20 which detects the temperature of the low pressure refrigerant gas to be sucked into the compressor 6 for refrigerant suction piping 15B of the compressor 6.
  • Td temperature sensor discharge temperature sensor
  • the heat source-side heat exchanger 8 is provided with a heat exchange temperature sensor 21 which detects the temperature of an intermediate site and a heat exchange temperature sensor 22 which detects the temperature of one end site while being provided with an ambient temperature sensor 23 which detects the temperature of ambient air to be vented via an outdoor air blower (not illustrated) for the heat source-side heat exchanger 8.
  • the utilization-side unit (indoor unit) 3 includes a utilization-side heat exchanger (indoor heat exchanger) 25 which is provided for a utilization-side refrigerant circuit 24 and exchanges heat between a refrigerant and indoor air to be circulated via an indoor air blower (not illustrated) and cools or heats the indoor air, and is served for indoor cooling or heating by blowing out the indoor air cooled or heated by the utilization-side heat exchanger 25 into a room.
  • a utilization-side heat exchanger indoor heat exchanger 25 which is provided for a utilization-side refrigerant circuit 24 and exchanges heat between a refrigerant and indoor air to be circulated via an indoor air blower (not illustrated) and cools or heats the indoor air, and is served for indoor cooling or heating by blowing out the indoor air cooled or heated by the utilization-side heat exchanger 25 into a room.
  • the utilization-side heat exchanger 25 is provided with a heat exchange temperature sensor 26 which detects the temperature of an intermediate site and a heat exchange temperature sensor 27 which detects the temperature of one end site while being provided with a suction temperature sensor 28 which detects the temperature of the indoor air to be sucked into the utilization-side heat exchanger 25 via the indoor air blower.
  • the heat source-side refrigerant circuit 16 and the utilization-side refrigerant circuit 24 are connected to each other by respectively flare-connecting the liquid-side piping 4 and the gas-side piping 5 using the liquid-side operated valve 12 and the gas-side operated valve 13, to constitute a refrigeration cycle 29 serving as a closed cycle, and the refrigeration cycle 29 is filled with a required amount of refrigerant, whose discharge temperature Td more easily increases than that of an R410A refrigerant, like the R32 refrigerant, to constitute the refrigerant and air conditioning apparatus 1.
  • the refrigerant which has been compressed by the compressor 6, is circulated through the heat source-side heat exchanger 8, the receiver 10, the electronic expansion valve for cooling 11, the liquid-side piping 4, the utilization-side heat exchanger 25, the gas-side piping 5, the four-direction switching valve 7, the accumulator 14, and the compressor 6 in this order, as indicated by a solid-line arrow by the four-direction switching valve 7, to form a cooling/air cooling cycle, and the heat source-side heat exchanger 8 and the utilization-side heat exchanger 25 are respectively made to function as a condenser and an evaporator.
  • a cooling/air cooling operation can be performed.
  • the refrigerant which has been compressed by the compressor 6, is circulated through the gas-side piping 5, the utilization-side heat exchanger 25, the liquid-side piping 4, the receiver 10, the electronic expansion valve for heating 9, the liquid-side piping 4, the heat source-side heat exchanger 8, the four-direction switching valve 7, the accumulator 14, and the compressor 6 in this order, as indicated by a broken-line arrow by the four-direction switching valve 7, to form a heating/air heating cycle, and the utilization-side heat exchanger 25 and the heat source-side heat exchanger 8 are respectively made to function as a condenser and an evaporator.
  • a heating/air heating operation can be performed.
  • the heat source-side unit (outdoor unit) 2 and the utilization-side unit (indoor unit) 3 are respectively provided with heat source-side and utilization-side controllers 30 and 31 which respectively control the operations of the units 2 and 3, and the controllers 30 and 31 are connected to each other via the communication line 32.
  • Each of the controllers 30 and 31 controls operations of the refrigeration / air-conditioning device 1 by receiving a detection signal input from each of the aforementioned sensors and controlling ON/OFF and the rotational speed of the compressor 6, switching of the four-direction switching valve 7, ON/OFF and the rotational speed of the outdoor air blower (not illustrated), the respective apertures of the electronic expansion valve for heating 9 and the electronic expansion valve for cooling 11, ON/OFF and the rotational speed of the indoor air blower (not illustrated), and the like, as needed, via a microcomputer or the like according to respective control programs stored in storage sections 33 and 34 based on a detection value of the detection signal and an operation signal, a setting signal, or the like input from a remote control (not illustrated).
  • the heat source-side controller 30 is provided with an expansion valve control means 35 which controls the aperture of the electronic expansion valve for cooling (EEVC) 11 or the electronic expansion valve for heating (EEVH) 9 so that a degree of suction gas superheat SH, which is found from a difference between a detection value by the suction temperature sensor 20 and a detection value by the heat exchange temperature sensor 26 or a saturation temperature at pressure detected by the low pressure sensor 19 during a normal cooling operation while being found from a difference between the detection value by the suction temperature sensor 20 and a detection value by the heat exchange temperature sensor 21 or a saturation temperature at pressure detected by the low pressure sensor 19 during a heating operation, becomes constant.
  • EEVC electronic expansion valve for cooling
  • EVH electronic expansion valve for heating
  • the expansion valve control means 35 has a function of switching control at the predetermined degree of suction gas superheat SH to control at a predetermined degree of discharge superheat TdSH or control at a predetermined discharge temperature Td when the temperature (discharge temperature) Td of the refrigerant discharged from the compressor 6, which is detected by the discharge temperature sensor (Td temperature sensor) 18, exceeds a previously set temperature (e.g., 95°C) during normal cooling and heating operations.
  • a previously set temperature e.g., 95°C
  • the degree of discharge superheat TdSH can be found from a difference between a detection value by the discharge temperature sensor 18 and the detection value by the heat exchange temperature sensor 21 during cooling or the detection value by the heat exchange temperature sensor 26 during heating (if a high pressure sensor is provided, a saturation temperature at pressure detected by the sensor (a high pressure saturation temperature may be used)).
  • the discharge temperature Td may exceed a utilization upper-limit value (a thick one-dot and dash line). If the discharge temperature Td exceeds a previously set temperature (a utilization upper-limit value; e.g., 95°C), control of the aperture of the electronic expansion valve for cooling 11 or the electronic expansion valve for heating 9 is switched to control at the predetermined degree of discharge superheat TdSH or control at the predetermined discharge temperature Td.
  • a utilization upper-limit value e.g., 95°C
  • the aforementioned expansion valve control means 35 is controlling the aperture of the electronic expansion valve for cooling 11 or the electronic expansion valve for heating 9 at the predetermined degree of discharge superheat TdSH or the predetermined discharge temperature Td
  • the operation point may change, as indicated by a broken line in FIG. 3 . Therefore, in this case, even if the degree of discharge superheat TdSH is controlled to be constant, the discharge temperature Td may exceed the utilization upper-limit value.
  • a target value switching means 36 is provided for the expansion valve control means 35.
  • the target value switching means 36 compares, while the control is being performed at the predetermined degree of discharge superheat TdSH or the predetermined discharge temperature Td, a target degree of discharge superheat TdSH obtained by calculation from the rotational speed of the compressor 6 and the high pressure saturation temperature with a utilization upper-limit value of the discharge temperature Td to be permitted as the compressor 6 when the control is being performed at the predetermined degree of discharge superheat TdSH, and switches between the control at the predetermined degree of discharge superheat TdSH and the control at the predetermined discharge temperature Td using the lower one of the values as a target value.
  • the aforementioned target value switching means 36 compares, while the control is being performed at the predetermined degree of discharge superheat TdSH or the predetermined discharge temperature Td, a target discharge temperature Td obtained by calculation from the rotational speed of the compressor 6 and the high pressure saturation temperature with the utilization upper-limit value of the discharge temperature Td to be permitted as the compressor 6 when the control is being performed at the predetermined discharge temperature Td, and performs the control at the predetermined discharge temperature Td using the lower one of the values as a target value.
  • a target value varying means 37 which varies a target value of the degree of discharge superheat TdSH or the discharge temperature Td depending on the rotational speed of the compressor 6 while the aperture of the electronic expansion valve for cooling 11 or the electronic expansion value for heating 9 is being controlled at the predetermined degree of discharge superheat TdSH or the predetermined discharge temperature Td, is provided for the expansion valve control means 35.
  • the degree of suction gas superheat SH may be higher than a control value during the control at the predetermined degree of suction gas superheat SH, as indicated by a fine broken line as a result.
  • the target value varying means 37 which varies the target value of the degree of discharge superheat TdSH or the discharge temperature Td depending on the rotational speed of the compressor 6 is provided, to prevent the electronic expansion valve for cooling 11 or the electronic expansion valve for heating 9 from being excessively throttled.
  • a relationship between the rotational speed of the compressor 6 and the degree of discharge superheat TdSH or the discharge temperature Td may be set so that the target value of the degree of discharge superheat TdSH or the discharge temperature Td linearly varies within a predetermined rotation number range, as illustrated in FIG. 5 . If the degree of discharge superheat TdSH or the discharge temperature Td becomes too low, a liquid floodback state occurs. Therefore, the target value (the degree of discharge superheat TdSH or the discharge temperature Td) which is a predetermined value or more is ensured. When the degree of discharge superheat TdSH or the discharge temperature Td becomes too high, the discharge temperature Td exceeds the utilization upper-limit value. Therefore, the discharge temperature Td is set to remain unchanged at a given value.
  • the control at the predetermined degree of discharge superheat TdSH or the control at the predetermined discharge temperature Td is basically returned to the control at the predetermined degree of suction gas superheat SH.
  • hysteresis may be provided so that the control is not switched until the degree of suction gas superheat SH increases to some extent or the degree of discharge superheat TdSH or the discharge temperature Td decreases by not less than a defined value if the control is switched once.
  • the cooling/air cooling operation can be performed.
  • the heating/air heating operation can be performed.
  • the aperture of the electronic expansion valve for cooling (EEVC) 11 or the electronic expansion valve for heating (EEVH) 9 is controlled so that the degree of suction gas superheat SH becomes constant via the expansion valve control means 35.
  • the control at the predetermined degree of suction gas superheat SH is switched to the control at the predetermined degree of discharge superheat TdSH or the control at the predetermined discharge temperature Td.
  • the discharge temperature Td may change depending on a high pressure level during an operation. For example, when the ambient temperature increases so that the high pressure increases during cooling, the operation point changes with the rotational speed of the compressor 6 remaining the same.
  • the discharge temperature Td may exceed the permitted utilization upper-limit value.
  • the target value switching means 36 compares the target degree of discharge superheat TdSH obtained by calculation from the rotational speed of the compressor 6 and the high pressure saturation temperature with the utilization upper-limit value of the discharge temperature Td to be permitted as the compressor 6 and switches between the control at the predetermined degree of discharge superheat TdSH and the control at the predetermined discharge temperature Td using the lower one of the values as a target value when the control is being performed at the predetermined degree of discharge superheat TdSH.
  • the target value switching means 36 compares the target discharge temperature Td obtained by calculation from the rotational speed of the compressor 6 and the high pressure saturation temperature with the utilization upper-limit value of the discharge temperature Td to be permitted as the compressor 6 and performs the control at the predetermined discharge temperature Td adopting the lower one of the values as a target value when the control is being performed at the predetermined discharge temperature Td.
  • the aperture of the electronic expansion valve for cooling 11 or the electronic expansion valve for heating 9 is controlled using the lower one of the upper-limit value of the discharge temperature Td to be permitted and the target degree of discharge superheat TdSH plus the high pressure saturation temperature as a target value, the discharge temperature Td is suppressed to not more than the utilization upper-limit value of the compressor 6 so that the utilization limit can be protected.
  • the target value varying means 37 which varies the target value of the degree of discharge superheat TdSH or the discharge temperature Td depending on the rotational speed of the compressor 6, is provided for the expansion valve control means 35. More specifically, when the rotational speed of the compressor 6 decreases so that the compression ratio decreases while the aperture of the electronic expansion valve for cooling 11 or the electronic expansion valve for heating 9 is being controlled at the predetermined degree of discharge superheat TdSH or the predetermined discharge temperature Td, the aperture of the electronic expansion valve for cooling 11 or the electronic expansion valve for heating 9 is excessively throttled if the target degree of discharge superheat TdSH or the discharge temperature Td is constant. As a result, the degree of suction gas superheat SH becomes too high, resulting in a degraded heat exchange performance.
  • the target value varying means 37 varies the degree of discharge superheat TdSH or the discharge temperature Td serving as the target value, as illustrated in FIG. 5 , depending on the rotational speed of the compressor 6, efficient operations can be performed with an appropriate operation condition maintained.
  • the present invention is not limited to the invention according to the aforementioned embodiment, and modifications can be made, as needed, without departing from the scope of the present invention.
  • a configuration using a relationship between the high pressure saturation temperature and the target discharge temperature Td as a map may be used without the degree of discharge superheat TdSH being used.
  • the refrigeration cycle 29 may have a basic cycle including a compressor, a heat source-side heat exchanger, an electronic expansion valve, and a utilization-side heat exchanger, is not limited to the refrigeration cycle in the aforementioned embodiment, and may be deformable to cycles having various configurations.

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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)

Claims (3)

  1. Dispositif de réfrigération/climatisation (1) comportant :
    un cycle de réfrigération dans lequel au moins un compresseur (6), un échangeur de chaleur du côté source de chaleur (8), une soupape de détente électronique (9, 11), et un échangeur de chaleur du côté utilisation (25) sont connectés par l'intermédiaire d'une tuyauterie de réfrigération (15) et qui est remplie avec un réfrigérant dont une température de sortie Td augmente plus facilement que celle d'un réfrigérant R410A ;
    un capteur de température de sortie (18) et un capteur de température d'aspiration (20) ; et
    des moyens de commande de soupape de détente (35) qui commandent une ouverture de la soupape de détente électronique (9, 11) à un degré prédéterminé de surchauffe de gaz d'aspiration SH quand la température de sortie Td n'est pas supérieure à une valeur de limite supérieure et commandent l'ouverture de la soupape de détente électronique (9, 11) à un degré prédéterminé de surchauffe de sortie TdSH ou une température de sortie prédéterminée Td quand la température de sortie Td dépasse la valeur de limite supérieure,
    caractérisé en ce que les moyens de commande de soupape de détente (35) comportent des moyens de commutation de valeur cible qui commutent, quand les moyens de commande de soupape de détente (35) réalisent la commande au degré prédéterminé de surchauffe de sortie TdSH tout en commandant l'ouverture de la soupape de détente (9, 11) au degré prédéterminé de surchauffe de sortie TdSH ou à la température de sortie prédéterminée Td, la commande au degré prédéterminé de surchauffe de sortie TdSH à la commande au degré prédéterminé de surchauffe de sortie TdSH ou la commande à la température de sortie prédéterminée Td en utilisant, comme valeur cible, la plus basse d'une valeur de limite supérieure de la température de sortie Td et un degré cible de surchauffe de sortie TdSH obtenu par calcul à partir de la vitesse de rotation du compresseur (6) et d'une température de saturation à haute pression, et comparent, quand les moyens de commande de soupape de détente réalisent la commande à la température de sortie prédéterminée Td, une température de cible sortie Td obtenue par calcul à partir de la vitesse de rotation du compresseur et de la température de saturation à haute pression avec la valeur de limite supérieure et adoptent la plus basse de la température cible de sortie Td et de la valeur de limite supérieure comme température de cible sortie Td.
  2. Dispositif de réfrigération/climatisation selon la revendication 1, dans lequel
    les moyens de commande de soupape de détente comportent en outre des moyens de variation de valeur de cible qui font varier le degré cible de surchauffe de sortie TdSH ou la température cible de sortie Td en fonction de la vitesse de rotation du compresseur.
  3. Dispositif de réfrigération/climatisation (1) comportant :
    un cycle de réfrigération dans lequel au moins un compresseur (6), un échangeur de chaleur du côté source de chaleur (8), une soupape de détente électronique (9, 11), et un échangeur de chaleur du côté utilisation (25) sont connectés par l'intermédiaire d'une tuyauterie de réfrigération (15) et qui est remplie avec un réfrigérant dont une température de sortie Td augmente plus facilement que celle d'un réfrigérant R410A ;
    un capteur de température de sortie (18) et un capteur de température d'aspiration (20) ; et
    des moyens de commande de soupape de détente (35) qui commandent une ouverture de la soupape de détente électronique (9, 11) à un degré prédéterminé de surchauffe de gaz d'aspiration SH quand la température de sortie Td n'est pas supérieure à une valeur de limite supérieure et commandent l'ouverture de la soupape de détente électronique (9, 11) à un degré prédéterminé de surchauffe de sortie TdSH ou une température de sortie prédéterminée Td quand la température de sortie Td dépasse la valeur de limite supérieure,
    caractérisé en ce que les moyens de commande de soupape de détente (35) comportent en outre des moyens de variation de valeur de cible qui font varier un degré cible de surchauffe de sortie TdSH ou une température cible de sortie Td en fonction de la vitesse de rotation du compresseur (6).
EP16183268.8A 2015-08-10 2016-08-08 Dispositif de réfrigération/climatisation Active EP3130870B1 (fr)

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US10955179B2 (en) * 2017-12-29 2021-03-23 Johnson Controls Technology Company Redistributing refrigerant between an evaporator and a condenser of a vapor compression system
KR102067447B1 (ko) * 2018-01-25 2020-01-20 삼성전자주식회사 공기 조화기 및 그 제어 방법
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CN112556127B (zh) * 2019-09-10 2022-03-11 广东美的制冷设备有限公司 空调蓄冷控制方法、装置及计算机可读存储介质
IT201900021534A1 (it) * 2019-11-19 2021-05-19 Carel Ind Spa Apparato frigorifero monovalvola a co2 e metodo di regolazione dello stesso
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CN112710071B (zh) * 2020-12-28 2022-07-26 宁波奥克斯电气股份有限公司 电子膨胀阀的调节速度控制方法、装置及多联机空调系统
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JP6594698B2 (ja) 2019-10-23

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