WO2016152552A1 - Dispositif de commande de système de conditionnement d'air, système de conditionnement d'air, programme de commande de conditionnement d'air, et procédé de commande de système de conditionnement d'air - Google Patents

Dispositif de commande de système de conditionnement d'air, système de conditionnement d'air, programme de commande de conditionnement d'air, et procédé de commande de système de conditionnement d'air Download PDF

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Publication number
WO2016152552A1
WO2016152552A1 PCT/JP2016/057550 JP2016057550W WO2016152552A1 WO 2016152552 A1 WO2016152552 A1 WO 2016152552A1 JP 2016057550 W JP2016057550 W JP 2016057550W WO 2016152552 A1 WO2016152552 A1 WO 2016152552A1
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Prior art keywords
pressure
compressor
air conditioning
refrigerant
conditioning system
Prior art date
Application number
PCT/JP2016/057550
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English (en)
Japanese (ja)
Inventor
隆博 加藤
Original Assignee
三菱重工業株式会社
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Filing date
Publication date
Application filed by 三菱重工業株式会社 filed Critical 三菱重工業株式会社
Priority to ES16768455T priority Critical patent/ES2745753T3/es
Priority to EP16768455.4A priority patent/EP3260792B1/fr
Priority to CN201680017419.5A priority patent/CN107614984A/zh
Publication of WO2016152552A1 publication Critical patent/WO2016152552A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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
    • F25B2313/029—Control issues
    • F25B2313/0294—Control issues related to the outdoor fan, e.g. controlling speed
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/195—Pressures of the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/197—Pressures of the evaporator

Definitions

  • the present invention relates to a control device of an air conditioning system, an air conditioning system, a control program of the air conditioning system, and a control method of the air conditioning system.
  • the operating pressure of the refrigerant is made constant regardless of the indoor load, and each load in the plurality of indoor units.
  • pressure constant control Some controls (hereinafter referred to as "pressure constant control") are performed to secure the necessary capacity according to the above.
  • Patent Document 1 one end is connected between the expansion valve and the indoor heat exchanger as a refrigeration cycle that supplies the air conditioning capacity according to the required operating capacity without reducing the compressor operating efficiency
  • the refrigerant circuit includes an injection circuit whose other end is connected to the compressor, and the number of rotations of the compressor falls within the rotation speed range of the down slope in the compressor performance curve, the gas refrigerant is injected into the compressor, and the rotation speed of the compressor is compressed.
  • An air conditioning system is disclosed that does not inject the gas refrigerant into the compressor within the range of the upslope rotational speed in the machine performance curve.
  • control for adjusting the target pressure may be performed in response to the decrease in the indoor load, as opposed to the pressure constant control.
  • the case where the indoor load decreases is, for example, when the indoor suction temperature approaches the set temperature.
  • the adjustment of the target pressure is performed by controlling the number of revolutions of the compressor, and for example, the target low pressure is increased during cooling and the target high pressure is reduced during heating to suppress the necessary capacity. Thereby, reduction of the power consumption of the compressor is realized.
  • Patent Document 1 requires an injection circuit, which complicates the structure of the refrigerant circuit.
  • the compressor may be operated at an operating point deviated from the efficient operating point for the compressor.
  • the present invention has been made in view of such circumstances, and is a control device for an air conditioning system, an air conditioning system, and an air conditioning system that reduce power consumption of the compressor and enable the compressor to operate more efficiently. It is an object of the present invention to provide a control program for a control method of an air conditioning system.
  • a control device of an air conditioning system of the present invention an air conditioning system, a control program of an air conditioning system, and a control method of an air conditioning system adopt the following means.
  • a control device of an air conditioning system includes pressure control means for controlling the number of rotations of a compressor such that the operating pressure of the refrigerant becomes a predetermined target pressure, and control by the pressure control means.
  • pressure ratio control means for controlling a pressure ratio, which is a ratio of the high pressure to the low pressure of the refrigerant, so as to become an operating point to improve the efficiency of the compressor after that.
  • the control device of the air conditioning system according to the present configuration performs, for example, control to make the operating pressure of the refrigerant constant regardless of the indoor load.
  • the number of rotations of the compressor is controlled by the pressure control means so that the operating pressure of the refrigerant becomes a predetermined target pressure. This reduces the power consumption.
  • the control by the pressure control means may cause the compressor to be operated at an operating point deviated from the efficient operating point for the compressor.
  • the pressure ratio control means controls the pressure ratio which is the ratio of the high pressure to the low pressure of the refrigerant so as to be an operating point for improving the efficiency of the compressor compared to that before. Ru.
  • the present configuration reduces the power consumption of the compressor and enables the compressor to be operated more efficiently.
  • the pressure control unit may reduce the number of rotations of the compressor such that the operating pressure becomes the target pressure.
  • the capacity of the air conditioning system is suppressed, and the power consumption of the air conditioning system is further reduced.
  • the pressure ratio control means may control the pressure ratio without changing the rotational speed of the compressor.
  • the pressure ratio is controlled without changing the number of revolutions of the compressor, that is, without performing control on the compressor, and the operating point of the compressor can be easily changed to a desired value.
  • the pressure ratio control means may control the pressure ratio by controlling the rotational speed of a fan provided in the outdoor unit.
  • the operating point of the compressor can be easily changed to a desired value.
  • the pressure ratio control means may control the pressure ratio by controlling the opening degree of the expansion valve provided in the outdoor unit.
  • the operating point of the compressor can be easily changed to a desired value.
  • An air conditioning system includes an outdoor unit, an indoor unit, and the control device described above.
  • a control program of an air conditioning system is a computer comprising: pressure control means for controlling the number of rotations of a compressor such that the operating pressure of the refrigerant becomes a predetermined target pressure; Function as pressure ratio control means for controlling the pressure ratio which is the ratio of the high pressure to the low pressure of the refrigerant so as to become an operating point to improve the efficiency of the compressor compared to that before, after control by means
  • a control method of an air conditioning system in a fourth aspect of the present invention, there is provided a first step of controlling the number of revolutions of a compressor such that the operating pressure of the refrigerant becomes a predetermined target pressure; And a second step of controlling a pressure ratio, which is a ratio of the high pressure to the low pressure of the refrigerant, to become an operating point that improves the efficiency of the compressor compared to that of the former.
  • the power consumption of the compressor can be reduced, and the compressor can be operated more efficiently.
  • FIG. 1 is a refrigerant circuit diagram of a multi-type air conditioning system in which a plurality of indoor units are connected to a single outdoor unit according to an embodiment of the present invention.
  • a plurality of indoor units 3A and 3B are connected in parallel to one outdoor unit 2.
  • the plurality of indoor units 3A, 3B are connected in parallel with each other between the gas side pipe 4 connected to the outdoor unit 2 and the liquid side pipe 5 via the branching unit 6.
  • the outdoor unit 2 includes an inverter-driven compressor 10 for compressing a refrigerant, a four-way switching valve 12 for switching the circulation direction of the refrigerant, an outdoor heat exchanger 13 for heat exchange between the refrigerant and the outside air, and an outdoor heat exchanger 13 A supercooling coil 14 integrally formed, an outdoor expansion valve (EEVH) 15, a receiver 16 for storing liquid refrigerant, a subcooling heat exchanger 17 for supercooling the liquid refrigerant, and supercooling heat exchange A supercooling expansion valve (EEVSC) 18 for controlling the amount of refrigerant diverted to the compressor 17 and an accumulator for separating a liquid component from the refrigerant gas sucked into the compressor 10 and attracting only the gas component to the compressor 10 side A gas side operation valve 20 and a liquid side operation valve 21 are provided.
  • EVH outdoor expansion valve
  • EVSC supercooling expansion valve
  • the above-described devices on the outdoor unit 2 side are sequentially connected via the refrigerant pipe 22 to constitute a known outdoor-side refrigerant circuit 23. Further, the outdoor unit 2 is provided with an outdoor fan 24 for blowing the outside air to the outdoor heat exchanger 13.
  • the gas side pipe 4 and the liquid side pipe 5 are refrigerant pipes connected to the gas side operation valve 20 and the liquid side operation valve 21 of the outdoor unit 2, and are connected to the outdoor unit 2 at the time of installation and construction at the site
  • the pipe length is appropriately set in accordance with the distance between the plurality of indoor units 3A and 3B.
  • a plurality of branching devices 6 are provided in the middle of the gas side piping 4 and the liquid side piping 5, and an appropriate number of indoor units 3A and 3B are connected via the branching devices 6.
  • a closed refrigeration cycle (refrigerant circuit) 7 is configured.
  • the indoor units 3A and 3B heat exchange the indoor air with the refrigerant, cool or heat them, and provide the indoor air conditioning with the indoor heat exchanger 30, the indoor expansion valve (EEVC) 31, and the indoor heat exchanger 30.
  • An indoor fan 32 for circulating indoor air and an indoor controller 33 are provided, and are connected to the branching unit 6 via the branch gas side pipes 4A, 4B and the branch liquid side pipes 5A, 5B on the indoor side.
  • the cooling operation is performed as follows.
  • the high-temperature, high-pressure refrigerant gas compressed and discharged by the compressor 10 is circulated to the outdoor heat exchanger 13 by the four-way switching valve 12 and is heat exchanged with the outside air blown by the outdoor fan 24 by the outdoor heat exchanger 13 It is condensed and liquefied.
  • the liquid refrigerant is further cooled by the subcooling coil 14, passes through the outdoor expansion valve 15, and is temporarily stored in the receiver 16.
  • the liquid refrigerant whose circulation amount has been adjusted by the receiver 16 is partially flowed from the liquid refrigerant piping in the process of being circulated through the liquid refrigerant piping side through the subcooling heat exchanger 17 and adiabatically expanded by the subcooling expansion valve 18
  • the heat is exchanged with the refrigerant to give a degree of subcooling.
  • the liquid refrigerant is led from the outdoor unit 2 to the liquid side pipe 5 through the liquid side operation valve 21 and is branched to the branched liquid side pipes 5A, 5B of the indoor units 3A, 3B through the branching unit 6. .
  • the liquid refrigerant divided into the branched liquid side pipes 5A, 5B flows into the indoor units 3A, 3B, is adiabatically expanded by the indoor expansion valve 31, and flows into the indoor heat exchanger 30 as a gas-liquid two-phase flow. Ru.
  • the indoor heat exchanger 30 the indoor air and the refrigerant circulated by the indoor fan 32 exchange heat, and the indoor air is cooled and provided for indoor cooling.
  • the refrigerant is gasified, passes through the branch gas side pipes 4A, 4B, and reaches the branch 6, and is merged with the refrigerant gas from other indoor units by the gas side pipe 4.
  • the refrigerant gas joined in the gas side pipe 4 returns to the outdoor unit 2 again, passes through the gas side operation valve 20 and the four-way switching valve 12 and is joined with the refrigerant gas from the subcooling heat exchanger 17. Introduced to In the accumulator 19, the liquid contained in the refrigerant gas is separated, and only the gas is drawn into the compressor 10. The refrigerant is compressed again in the compressor 10, and the cooling operation is performed by repeating the above cycle.
  • the heating operation is performed as follows.
  • the high-temperature, high-pressure refrigerant gas compressed and discharged by the compressor 10 is circulated to the gas-side operation valve 20 via the four-way switching valve 12.
  • the high pressure gas refrigerant is led from the outdoor unit 2 through the gas side operation valve 20 and the gas side pipe 4 and passes through the branching unit 6 and the branch gas side pipes 4A and 4B on the indoor side to a plurality of indoor units 3A and 3B. be introduced.
  • the high temperature / high pressure refrigerant gas introduced into the indoor units 3A, 3B is heat exchanged with the indoor air circulated through the indoor fan 32 by the indoor heat exchanger 30, and the indoor air heated by this is blown out into the room It is served for heating.
  • the refrigerant condensed and liquefied by the indoor heat exchanger 30 passes through the indoor expansion valve 31 and the branch liquid side pipes 5A and 5B to reach the branch 6, and is merged with the refrigerant from the other indoor units. And return to the outdoor unit 2.
  • the degree of opening of the indoor expansion valve 31 is the indoor controller so that the refrigerant outlet temperature or the degree of refrigerant supercooling of the indoor heat exchanger 30 functioning as a condenser becomes the control target value. It is controlled via 33.
  • the refrigerant returned to the outdoor unit 2 passes through the liquid side operation valve 21 to reach the subcooling heat exchanger 17, and after being subcooled as in the case of cooling, flows into the receiver 16 and is temporarily stored. Thus, the circulation amount is adjusted.
  • the liquid refrigerant is supplied to the outdoor expansion valve 15 and adiabatically expanded, and then flows into the outdoor heat exchanger 13 through the subcooling coil 14.
  • the refrigerant exchanges heat with the outside air blown from the outdoor fan 24, and the refrigerant absorbs heat from the outside air to be vaporized and gasified.
  • the refrigerant is introduced from the outdoor heat exchanger 13 through the four-way switching valve 12 to the refrigerant gas from the subcooling heat exchanger 17 and then introduced into the accumulator 19.
  • the liquid contained in the refrigerant gas is separated, and only the gas is drawn into the compressor 10 and compressed again in the compressor 10.
  • the heating operation is performed by repeating the above cycle.
  • FIG. 2 is a block diagram showing an electrical configuration of the air conditioner control device 40 that controls the multi-type air conditioning system 1 according to the present embodiment.
  • the air conditioner control device 40 is configured of, for example, a central processing unit (CPU), a random access memory (RAM), a read only memory (ROM), a computer readable storage medium, and the like. Then, a series of processes for realizing various functions are stored in the form of a program, for example, in a storage medium or the like in the form of a program, and the CPU reads this program into a RAM or the like to execute information processing and arithmetic processing. Thus, various functions are realized.
  • CPU central processing unit
  • RAM random access memory
  • ROM read only memory
  • the program may be installed in advance in a ROM or other storage medium, may be provided as stored in a computer-readable storage medium, or may be distributed via a wired or wireless communication means. Etc. may be applied.
  • the computer readable storage medium is a magnetic disk, a magneto-optical disk, a CD-ROM, a DVD-ROM, a semiconductor memory or the like. Further, the air conditioner control device 40 is provided in the outdoor unit 2.
  • the air conditioner controller 40 includes a pressure control unit 42, a pressure ratio control unit 44, and a storage unit 46.
  • the pressure control unit 42 performs constant pressure control to keep the operating pressure of the refrigerant constant regardless of the indoor load.
  • the constant pressure control secures the necessary capacity of the compressor 10 by controlling the rotational speed of the compressor 10 such that the operating pressure of the refrigerant becomes a predetermined target pressure. More specifically, in the constant pressure control, when the initial number of revolutions of the compressor 10 is determined, the target pressure is set by the model capacity, the number of revolutions (operating frequency), etc. During heating (low pressure) and heating, the discharge pressure (high pressure) is detected as a pressure detection value by a pressure sensor. And pressure fixed control compares this target pressure and a pressure detection value, and controls the number of rotations of compressor 10. FIG.
  • constant pressure control reduces the rotational speed of the compressor 10 when target pressure> pressure detection value during cooling, and raises the rotational speed of the compressor 10 when target pressure ⁇ pressure detection value.
  • constant pressure control raises the rotational speed of the compressor 10 when the target pressure is higher than the detected pressure value during heating, and lowers the rotational speed of the compressor 10 when the target pressure is lower than the detected pressure value.
  • the rotational speed of the compressor 10 is constant, so that the suction pressure is constant during cooling and the discharge pressure is constant during heating.
  • the pressure ratio control unit 44 sets the pressure ratio (high pressure to high pressure to low pressure) of the refrigerant so as to be an operation point that improves the efficiency of the compressor 10 compared to that after the control by the pressure control unit 42. Control (hereinafter referred to as "pressure ratio control").
  • the storage unit 46 stores compressor efficiency distribution information indicating the efficiency distribution of the compressor 10 obtained from the rotational speed and pressure ratio of the compressor 10.
  • FIG. 3 is an efficiency map showing an example of compressor efficiency distribution information, in which the horizontal axis is the number of revolutions of the compressor 10, the vertical axis is the pressure ratio, and the efficiency of the compressor 10 is shown by a solid line Is represented. That is, the efficiency of the compressor 10 is higher as the center of the efficiency map shown in FIG. 3 (inner side of the contour line).
  • the compressor efficiency distribution information is not limited to the efficiency map as shown in FIG. 3 but may be stored in the storage unit 46 in the form of a function or a table.
  • constant pressure control and pressure ratio control executed by the air conditioner control device 40 according to the present embodiment will be described in detail.
  • constant pressure control and pressure ratio control are collectively referred to as high efficiency control.
  • the constant pressure control is to make the operating pressure of the refrigerant constant regardless of the indoor load. Furthermore, the constant pressure control according to the present embodiment, for example, reduces the rotational speed of the compressor 10 so that the pressure of the refrigerant reaches the newly adjusted target pressure when the indoor load decreases. Energy saving control to reduce the ability of
  • the decrease in indoor load is when the indoor suction temperature and the set temperature approach a predetermined range.
  • the difference between the indoor suction temperature and the set temperature of half or more of the indoor units 3 is within 1 ° C.
  • Indoor load is reduced.
  • the pressure control unit 42 decreases the rotational speed of the compressor 10 by raising the target pressure (target low pressure) until then.
  • target pressure target high pressure
  • the target pressure is adjusted stepwise, and in each case, the difference between the indoor suction temperature and the set temperature is detected. And if this difference becomes large, the capacity of the compressor 10 becomes insufficient with respect to the indoor load, so the adjustment of the target pressure ends.
  • the change of the operating point of the compressor 10 when the energy saving control according to the present embodiment is performed will be described with reference to FIG. 3.
  • the operating point indicated by point A is the operating point during normal control before the target pressure is adjusted, that is, before energy saving control is performed.
  • point B is an operating point after energy saving control is performed.
  • the operating point B of the energy saving control is not necessarily an efficient operating point for the compressor 10.
  • a region where the pressure ratio is high is a more efficient operating point.
  • an operating point (the point C in the example of FIG. 3 and hereinafter referred to as “optimum optimum operating point”) which improves the efficiency of the compressor 10 compared to that before.
  • the pressure ratio is controlled.
  • Table 1 shows the adjustment of the operating point of the compressor 10 during cooling and heating.
  • pressure ratio control is performed by controlling the high pressure
  • energy saving control is performed by controlling high pressure during heating
  • pressure ratio control is performed by controlling low pressure.
  • the control purpose is different between the high pressure and the low pressure of the refrigerant between the cooling time and the heating time.
  • the pressure ratio control part 44 which concerns on this embodiment performs pressure ratio control by changing the rotation speed of the outdoor fan 24 as an example. Specifically, when the pressure ratio after the energy saving control is lower than the efficiency optimum operating point, the rotational speed of the outdoor fan 24 is reduced. As a result, while the high pressure of the refrigerant rises during cooling, the low pressure of the refrigerant falls during heating. Therefore, the pressure ratio is increased, and the operating point approaches the efficiency optimum operating point. On the other hand, when the pressure ratio after the energy saving control is higher than the efficiency optimum operating point, the rotational speed of the outdoor fan 24 is increased. As a result, while the high pressure of the refrigerant drops during cooling, the low pressure of the refrigerant rises during heating. Therefore, the pressure ratio is lowered, and the operating point approaches the efficiency optimum operating point.
  • pressure ratio control performs pressure ratio control without changing the rotation speed of the compressor 10. That is, the pressure ratio control is to control the pressure ratio without controlling the compressor 10, and it is easy to change the operating point of the compressor 10 to a desired value.
  • the efficiency optimum operating point is, for example, predetermined as a pressure ratio that provides the best efficiency with respect to the rotational speed of the compressor 10, and may have a certain width with respect to the pressure ratio increase / decrease direction .
  • FIG. 4 is a flowchart showing the flow of the high efficiency control process executed by the air conditioner control device 40.
  • a program (high efficiency control program) for executing this process is stored in advance in a predetermined area of the storage unit 46. It is memorized. Note that, before the high efficiency control process is performed, the air conditioner control device 40 performs constant pressure control (normal control) without energy saving control.
  • step 100 it is determined whether or not the indoor load has decreased to a level at which the energy saving control can be started. If the determination is positive, the process proceeds to step 102. In the case of a negative determination, normal control is continued.
  • step 102 normal control is ended, and setting is made to start energy saving control.
  • the target pressure is adjusted to perform energy saving control.
  • the target pressure target low pressure
  • the target pressure target high pressure
  • step 106 it is determined whether or not the operating pressure matches the adjusted target pressure, and in the case of a positive determination, the process proceeds to step 110, and in the case of a negative determination, the process proceeds to step 108.
  • step 108 the rotational speed of the compressor 10 is controlled so that the operating pressure matches the target pressure, and the process returns to step 106 to compare the operating pressure with the adjusted target pressure. Specifically, when the low pressure is lower than the target low pressure during cooling, or when the high pressure is higher than the target high pressure during heating, the rotational speed of the compressor 10 is reduced. On the other hand, when the low pressure is higher than the target low pressure during cooling, or when the high pressure is lower than the target high pressure during heating, the rotational speed of the compressor 10 is increased.
  • step 110 the efficiency optimum operating point is set according to the rotational speed of the compressor 10.
  • step 112 it is determined whether the actual pressure ratio and the pressure ratio of the efficiency optimum operating point coincide with each other. If the determination is negative, the process proceeds to step 114. If the determination is affirmative, the process returns to step 106, and the energy saving control and the pressure ratio control are repeatedly continued.
  • step 114 the rotational speed of the outdoor fan 24 is controlled so that the actual pressure ratio and the pressure ratio at the efficiency optimum operating point coincide with each other, and the process returns to step 112 again, and the pressure ratio at the actual pressure ratio and the efficiency optimum operating point Compare with.
  • the actual pressure ratio is lower than the pressure ratio at the efficiency optimum operating point, the number of rotations of the outdoor fan 24 is reduced. As a result, the high pressure is increased during cooling, the low pressure is decreased during heating, and the actual pressure ratio is increased.
  • the actual pressure ratio is higher than the pressure ratio at the efficiency optimum operating point, the rotation speed of the outdoor fan 24 is increased. As a result, the high pressure is lowered at the time of cooling, the low pressure is raised at the time of heating, and the actual pressure ratio is lowered.
  • the air conditioner control device 40 controls the number of rotations of the compressor 10 so that the operating pressure of the refrigerant becomes a predetermined target pressure, and after this control, the compression is performed.
  • the pressure ratio which is the ratio of the high pressure to the low pressure of the refrigerant, is controlled so as to be an operating point that improves the efficiency of the machine 10 compared to that of the past.
  • the air conditioner control device 40 reduces the power consumption of the compressor 10 and enables the compressor 10 to operate more efficiently.
  • the present invention is not limited to this.
  • the opening degree of the expansion valve 15 may be controlled.
  • the outdoor expansion valve 15 is throttled.
  • the high pressure is increased during cooling, the low pressure is decreased during heating, and the actual pressure ratio is increased.
  • the outdoor expansion valve 15 is opened.
  • the high pressure is lowered at the time of cooling, the low pressure is raised at the time of heating, and the actual pressure ratio is lowered.
  • both the rotation speed of the outdoor fan 24 and the opening degree of the outdoor expansion valve 15 may be controlled.
  • a plurality of refrigerant circuits each provided with a throttle and a solenoid valve are provided in parallel, and by changing the flow path of the refrigerant by opening and closing the solenoid valve to change the throttle amount, pressure The ratio may be controlled.
  • the pressure ratio may be controlled by providing a plurality of outdoor heat exchangers 13 and changing the number (capacity) of the outdoor heat exchangers 13 through which the refrigerant flows.
  • pressure ratio control may be performed after energy saving control
  • pressure ratio control may be performed without energy saving control. Also good.
  • pressure ratio control may be performed after the normal control (operating point A) so that the operating point of the compressor 10 becomes the more efficient operating point C. .
  • the air-conditioner controller 40 performs constant pressure control to keep the operating pressure of the refrigerant constant regardless of the indoor load
  • the present invention is not limited to this. Energy saving control may be performed without performing pressure constant control.
  • the present invention is not limited to this, and the present invention is not limited to the case where the indoor load decreases. Even when the setting change by the user (administrator) of the air conditioning system 1, for example, the reduction setting of the rotational speed of the compressor 10, the change setting of the target pressure of the refrigerant, etc., energy saving control is performed. Good.

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  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

Cette invention concerne un dispositif de commande de conditionnement d'air, qui commande un système de conditionnement d'air à plusieurs blocs de sorte que la pression de travail du fluide frigorigène reste constante quelle que soit la charge intérieure. Ledit dispositif de commande de conditionnement d'air commande la vitesse de rotation d'un compresseur, de sorte que la pression de travail du fluide frigorigène atteigne une pression cible prédéterminée, et ensuite après cette commande, il commande un rapport de pression, qui est le rapport de la haute pression du fluide frigorigène à la basse pression du fluide frigorigène, de sorte que le rendement du compresseur se trouve à un point de fonctionnement où le rendement est amélioré. Ainsi, ledit dispositif de commande de conditionnement d'air peut réduire la consommation d'énergie du compresseur et permettre au compresseur de fonctionner plus efficacement.
PCT/JP2016/057550 2015-03-26 2016-03-10 Dispositif de commande de système de conditionnement d'air, système de conditionnement d'air, programme de commande de conditionnement d'air, et procédé de commande de système de conditionnement d'air WO2016152552A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
ES16768455T ES2745753T3 (es) 2015-03-26 2016-03-10 Dispositivo de control para un sistema de acondicionamiento de aire, un sistema de acondicionamiento de aire, un programa de control de acondicionamiento de aire y un método de control para un sistema de acondicionamiento de aire
EP16768455.4A EP3260792B1 (fr) 2015-03-26 2016-03-10 Dispositif de commande de système de conditionnement d'air, système de conditionnement d'air, programme de commande de conditionnement d'air, et procédé de commande de système de conditionnement d'air
CN201680017419.5A CN107614984A (zh) 2015-03-26 2016-03-10 空调系统的控制装置、空调系统、空调系统的控制程序以及空调系统的控制方法

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JP2015064074A JP6495064B2 (ja) 2015-03-26 2015-03-26 空調システムの制御装置、空調システム、空調システムの制御プログラム、及び空調システムの制御方法
JP2015-064074 2015-03-26

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JP2018179370A (ja) * 2017-04-10 2018-11-15 日立ジョンソンコントロールズ空調株式会社 冷凍装置
JP7208063B2 (ja) * 2019-03-05 2023-01-18 三菱重工サーマルシステムズ株式会社 輸送用冷凍機械
CN111076350B (zh) * 2019-12-30 2021-09-21 宁波奥克斯电气股份有限公司 一种压缩机启动的控制方法、装置及空调器
CN113446706B (zh) * 2020-03-25 2022-08-19 青岛海尔空调电子有限公司 空调器控制方法和空调器
CN111895627B (zh) * 2020-07-14 2022-01-04 Tcl空调器(中山)有限公司 一种空调室外风机转速控制方法、空调及存储介质
CN112665133B (zh) * 2021-01-21 2022-05-17 广东美的暖通设备有限公司 多联机耗电量检测方法、热回收多联机、存储介质及装置

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JP2000018685A (ja) * 1998-07-02 2000-01-18 Matsushita Refrig Co Ltd 多室型空気調和機
JP2003254589A (ja) * 2002-02-28 2003-09-10 Matsushita Electric Ind Co Ltd 空気調和機
JP2003262385A (ja) * 2002-03-12 2003-09-19 Hitachi Ltd 空気調和機
JP2008190759A (ja) * 2007-02-02 2008-08-21 Daikin Ind Ltd 空気調和装置
WO2014156313A1 (fr) * 2013-03-27 2014-10-02 日立アプライアンス株式会社 Climatiseur et procédé de mise en œuvre d'un climatiseur

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CN107614984A (zh) 2018-01-19
JP2016183817A (ja) 2016-10-20
EP3260792A1 (fr) 2017-12-27
EP3260792B1 (fr) 2019-07-31
ES2745753T3 (es) 2020-03-03
EP3260792A4 (fr) 2018-03-14

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