EP3260792B1 - Klimatisierungssystemsteuerungsvorrichtung, klimatisierungssystem, klimatisierungsteuerungsprogramm und klimatisierungssystemsteuerungsverfahren - Google Patents

Klimatisierungssystemsteuerungsvorrichtung, klimatisierungssystem, klimatisierungsteuerungsprogramm und klimatisierungssystemsteuerungsverfahren Download PDF

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Publication number
EP3260792B1
EP3260792B1 EP16768455.4A EP16768455A EP3260792B1 EP 3260792 B1 EP3260792 B1 EP 3260792B1 EP 16768455 A EP16768455 A EP 16768455A EP 3260792 B1 EP3260792 B1 EP 3260792B1
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EP
European Patent Office
Prior art keywords
pressure
control
refrigerant
compressor
conditioning system
Prior art date
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Application number
EP16768455.4A
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English (en)
French (fr)
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EP3260792A4 (de
EP3260792A1 (de
Inventor
Takahiro Kato
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Mitsubishi Heavy Industries Thermal Systems Ltd
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Classifications

    • 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 for an air-conditioning system, an air-conditioning system, a control program for an air-conditioning system, and a control method for an air-conditioning system.
  • the refrigerant operation pressure is regulated independently of the indoor load and control (hereinafter referred to as "pressure regulating control”) is given for ensuring performances needed for the respective loads in the plurality of indoor units.
  • Patent Citation 1 discloses an air-conditioning system including an injection circuit having one terminal connected between an expansion valve and an indoor heat exchanger, and another terminal connected to a compressor, as a refrigerating cycle for providing an air-conditioning performance corresponding to a needed work capacity without decreasing compressor work efficiency.
  • Patent Citation 1 when a rotation speed of the compressor is in a rotation speed range of the compressor performance curve in a down grade, a gas refrigerant is injected to the compressor, and when the rotation speed of the compressor is in a rotation speed range of the compressor performance curve in an up grade, a gas refrigerant is not injected to the compressor.
  • control for adjusting the target pressure with a decrease in indoor load is performed.
  • a decrease in indoor load occurs, for example, when the indoor suction temperature approaches a set temperature.
  • the target pressure is adjusted by controlling the rotation speed of the compressor. For example, needed performance is suppressed by increasing the target low pressure during cooling, and decreasing the target high pressure during heating. This leads to a reduction in the power consumption of the compressor.
  • Patent Citation 1 Japanese Unexamined Patent Application, Publication No. 2013-119957
  • EP 1956320A1 discloses a refrigeration system, which includes a refrigerant circuit including a low-pressure stage compressor variable in displacement and a high-pressure stage compressor variable in displacement and operating in a two-stage compression refrigeration cycle; and a controller for controlling the operation of the refrigeration system.
  • the controller includes a first control section and a second control section.
  • the first control section controls the operating capacity of the low-pressure stage compressor to adapt to the load of the refrigeration capacity.
  • the second control section controls the operating capacity of the high-pressure stage compressor so that the ratio between a first pressure ratio, which is the ratio of the discharge pressure of the low-pressure stage compressor to the suction pressure thereof, and a second pressure ratio, which is the ratio of the discharge pressure of the high-pressure stage compressor to the suction pressure thereof, is 1:1.
  • JP 2000 018685 A1 is directed to improving of an efficiency in accordance with the load condition in a room and permitting air-conditioning operation under the good condition of comfortable property by a method wherein a first control means, controlling the capacity of a compressor by a set value, and a second compressor control means, changing the operating frequency of the compressor into a value determined by a compressor operating amount determining means, are provided.
  • WO 2014 156 313 A1 discloses an air conditioner that uses R32 as a refrigerant and that can reduce the load on a compressor, and a method for operating an air conditioner.
  • the air conditioner has a refrigeration cycle in which at least a compressor, an outdoor heat exchanger, an indoor heat exchanger, an outdoor expansion valve, and an indoor expansion valve are connected, and refrigerant containing 70 wt% or more of R32 is circulated; and a controller.
  • the controller has the characteristic of adjusting the rotational speed of the compressor so that the pressure ratio is less than the upper limit.
  • Patent Citation 1 requires an injection circuit, which complicates the configuration of the refrigerant circuit.
  • adjusting the target pressure may cause the compressor to operate at an operational point deviated from an operational point that is efficient for the compressor.
  • a control device for an air-conditioning system includes: a pressure control means that controls a rotation speed of a compressor such that an operation pressure of a refrigerant becomes a predetermined target pressure; and a compression ratio control means that controls a pressure ratio between high pressure and low pressure of the refrigerant after control by the pressure control means, in order to provide an operational point that improves efficiency of the compressor.
  • a control device for an air-conditioning system performs, for example, control for regulating the operation pressure of the refrigerant to be constant, independently of the indoor load.
  • the rotation speed of the compressor is controlled such that the operation pressure of the refrigerant becomes a predetermined target pressure. This leads to a reduction in power consumption.
  • control by the pressure control means may cause the compressor to operate at an operation position deviated from an operation position that is efficient for the compressor.
  • a pressure ratio which is a ratio between the high pressure and low pressure of the refrigerant is controlled to provide an operational point that improves the efficiency of the compressor.
  • this aspect reduces the power consumption of the compressor and allows the compressor to operate more efficiently.
  • the pressure control means may decrease the rotation speed of the compressor such that the operation pressure becomes the target pressure.
  • the performance of the air-conditioning system is suppressed and the power consumption of the air-conditioning system is reduced.
  • the compression ratio control means may control the pressure ratio without changing the rotation speed of the compressor.
  • the rotation speed of the compressor is not changed.
  • the control of the pressure ratio is achieved without controlling the compressor, thereby easily changing the operational point of the compressor to a desired value.
  • the compression ratio control means may control the pressure ratio by controlling the rotation speed of a fan provided to an outdoor unit.
  • the operational point of the compressor can easily be changed to a desired value.
  • the compression ratio control means may control the pressure ratio by controlling the degree of opening of an expansion valve provided to an outdoor unit.
  • the operational point of the compressor can easily be changed to a desired value.
  • the air-conditioning system includes an outdoor unit; an indoor unit; and the control device described above.
  • a control program for an air-conditioning system causes a computer to function as: a pressure control means that controls a rotation speed of a compressor such that an operation pressure of a refrigerant becomes a predetermined target pressure; and a compression ratio control means that controls a pressure ratio between high pressure and low pressure of the refrigerant after control by the pressure control means, in order to provide an operational point that improves efficiency of the compressor.
  • a control method for an air-conditioning system includes: a first step of controlling a rotation speed of a compressor such that an operation pressure of a refrigerant becomes a predetermined target pressure; and a second step of controlling a pressure ratio between high pressure and low pressure of the refrigerant after control by the first step, in order to provide an operational point that improves efficiency of the compressor.
  • the present invention provides advantageous effects of a reduction in the power consumption of a compressor and efficient operation of the compressor.
  • FIG. 1 is a diagram of a refrigerant circuit of a multi-type air-conditioning system in which one outdoor unit according to one embodiment of the present invention is connected to a plurality of indoor units.
  • a plurality of indoor units 3A and 3B are parallel-connected to one outdoor unit 2.
  • the plurality of indoor units 3A and 3B are parallel-connected to each other through a branching unit 6 between gas-side piping 4 and liquid-side piping 5 connected to the outdoor unit 2.
  • the outdoor unit 2 is provided with an inverter-driven compressor 10 that compresses a refrigerant; a four-way switching valve 12 that switches the circulation direction of the refrigerant; an outdoor heat-exchanger 13 that exchanges heat between the refrigerant and outside air; a supercooling coil 14 that is formed integrally with the outdoor heat-exchanger 13; an outdoor expansion valve (EEVH) 15; a receiver 16 that accumulates a liquid refrigerant; a supercooling heat exchanger 17 that subjects the liquid refrigerant to supercooling; a supercooling expansion valve (EEVSC) 18 that controls the amount of refrigerant flowing into the supercooling heat exchanger 17; an accumulator 19 that separates a liquid component from refrigerant gas to be suctioned into the compressor 10, thus allowing only a gaseous component to be suctioned into the compressor 10; a gas-side operation valve 20; and a liquid-side operation valve 21.
  • an inverter-driven compressor 10 that compresses
  • the above-described devices in the outdoor unit 2 are sequentially connected via a refrigerant pipe 22, thus configuring a known outdoor-side refrigerant circuit 23. Furthermore, the outdoor unit 2 is provided with an outdoor fan 24 that blows outside air toward 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, respectively, and, at the time of installation at a site, the pipe lengths are appropriately set according to the distances from the outdoor unit 2 to the plurality of indoor units 3A and 3B to be connected to the outdoor unit 2.
  • the plurality of branching units 6 are provided at intermediate points in the gas-side pipe 4 and the liquid-side pipe 5, and the appropriate number of indoor units 3A and 3B are connected via the branching units 6. Accordingly, a single closed refrigeration cycle (refrigerant circuit) 7 is configured.
  • the indoor units 3A and 3B are each provided with an indoor heat exchanger 30 that subjects indoor air to heat exchange with the refrigerant, thus cooling or heating the indoor air and making it available for indoor air-conditioning; an indoor expansion valve (EEVC) 31; an indoor fan 32 that circulates indoor air via the indoor heat exchanger 30; and an indoor controller 33.
  • the indoor units 3A and 3B are connected to the branching units 6 via branched gas-side pipes 4A and 4B and branched liquid-side pipes 5A and 5B, which are provided at the indoor sides.
  • High-temperature, high-pressure refrigerant gas that has been compressed at the compressor 10 and discharged therefrom is circulated to the outdoor heat-exchanger 13 by the four-way switching valve 12 and is condensed to liquid at the outdoor heat-exchanger 13 through heat exchange with outside air blown by the outdoor fan 24.
  • This liquid refrigerant is further cooled at the supercooling coil 14, then passes through the outdoor expansion valve 15, and is temporarily accumulated in the receiver 16.
  • the liquid refrigerant whose circulation amount is adjusted at the receiver 16, is partially branched from a liquid refrigerant pipe, while flowing in the liquid refrigerant pipe via the supercooling heat exchanger 17, and is subjected to supercooling through heat exchange with the refrigerant that has been adiabatically expanded at the supercooling expansion valve 18.
  • This liquid refrigerant is guided from the outdoor unit 2 to the liquid-side pipe 5 via the liquid-side operation valve 21 and is branched, via the branching unit 6, into the branched liquid-side pipes 5A and 5B of the indoor units 3A and 3B.
  • the indoor heat exchanger 30 heat exchange is performed between indoor air circulated by the indoor fan 32 and the refrigerant, thus cooling the indoor air and making it available for indoor cooling.
  • the refrigerant is gasified, flows into the branching unit 6 via the corresponding branched gas-side pipe 4A or 4B, and joins, in the gas-side pipe 4, the refrigerant gas flowing from the other indoor unit.
  • the refrigerant gas joining 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, joins refrigerant gas flowing from the supercooling heat exchanger 17, and is then guided to the accumulator 19.
  • the liquid component contained in the refrigerant gas is separated, and only the gaseous component is suctioned into the compressor 10. This refrigerant is compressed again at the compressor 10, and the above-described cycle is repeated, thereby performing the cooling operation.
  • High-temperature, high-pressure refrigerant gas that has been compressed at the compressor 10 and discharged therefrom is circulated to the gas-side operation valve 20 via the four-way switching valve 12.
  • This high-pressure gas refrigerant is guided from the outdoor unit 2 via the gas-side operation valve 20 and the gas-side pipe 4 and is guided to the plurality of indoor units 3A and 3B via the branching unit 6 and the branched gas-side pipes 4A and 4B, which are provided at the indoor sides.
  • the high-temperature, high-pressure refrigerant gas guided to each of the indoor units 3A and 3B is subjected, at the indoor heat exchanger 30, to heat exchange with the indoor air circulated via the indoor fan 32, and the thus-heated indoor air is blown into the room for heating.
  • the refrigerant condensed to liquid at the indoor heat exchanger 30 reaches the branching unit 6 via the indoor expansion valve 31 and the corresponding branched liquid-side pipe 5A or 5B, joins the refrigerant flowing from the other indoor unit, and returns to the outdoor unit 2 via the liquid-side pipe 5.
  • the degree of opening of the indoor expansion valve 31 is controlled via the indoor controller 33 so that the refrigerant outlet temperature or the degree of supercooling of the refrigerant at the indoor heat exchanger 30, which functions as a condenser, becomes a control target value.
  • the refrigerant that has returned to the outdoor unit 2 reaches the supercooling heat exchanger 17 via the liquid-side operation valve 21, is subjected to supercooling as in the case of cooling, and then flows into the receiver 16, where it is temporarily accumulated, thus adjusting the circulation amount.
  • This liquid refrigerant is supplied to the outdoor expansion valve 15, thus being adiabatically expanded, and flows into the outdoor heat-exchanger 13 via the supercooling coil 14.
  • FIG. 2 is a block diagram showing the electrical configuration of an air conditioner control device 40 that is responsible for the control of the multi-type air-conditioning system 1 according to this embodiment. It should be noted that FIG. 2 shows functions related to the pressure regulating control and compression ratio control which will be described later in detail.
  • the air conditioner control device 40 includes, for example, a central processing unit (CPU), a random access memory (RAM), a read only memory (ROM), and a computer-readable storage medium.
  • CPU central processing unit
  • RAM random access memory
  • ROM read only memory
  • a process of a series of steps for achieving various functions is stored in the storage medium in the form of a program which is read out by the CPU into the RAM or the like to subject information to processing and computation, thereby achieving various functions.
  • the program can be installed in advance to the ROM or other storage media, provided while being stored in the computer-readable storage medium, or distributed through communication means in a wired or wireless manner, for example.
  • Examples of the computer-readable storage medium include a magnetic disc, a magneto-optical disc, a CD-ROM, a DVD-ROM, and a semiconductor memory.
  • the air conditioner control device 40 is provided to the outdoor unit 2.
  • the air conditioner control device 40 includes a pressure control unit 42, a pressure ratio control unit 44, and a storage 46.
  • the pressure control unit 42 performs pressure regulating control for regulating the operation pressure of the refrigerant to be constant independently of the indoor load.
  • pressure regulating control the rotation speed of the compressor 10 is controlled such that the operation pressure of the refrigerant becomes a predetermined target pressure, thereby ensuring the needed performance of the compressor 10.
  • the pressure regulating control Upon determination of the initial rotation speed of the compressor 10, the pressure regulating control sets the target pressure according to the machine capacity, the rotation speed (operation frequency), and the like. In addition, the suction pressure (low pressure) is detected by a compression sensor during cooling, and the ejection pressure (high pressure) is detected by the compression sensor during heating, as pressure detection values.
  • the pressure regulating control performs comparison between the target pressure and the pressure detection value and controls the rotation speed of the compressor 10. To be specific, the pressure regulating control during cooling decreases the rotation speed of the compressor 10 when the target pressure > the pressure detection value, and increases the rotation speed of the compressor 10 when the target pressure ⁇ the pressure detection value.
  • the pressure regulating control during heating increases the rotation speed of the compressor 10 when the target pressure > the pressure detection value, and decreases the rotation speed of the compressor 10 when the target pressure ⁇ the pressure detection value.
  • the rotation speed of the compressor 10 is regulated, so that the suction pressure is regulated during cooling and the ejection pressure is regulated during heating.
  • the pressure ratio control unit 44 After the control by the pressure control unit 42, the pressure ratio control unit 44 performs the control of a pressure ratio (high pressure/low pressure) which is a ratio between the high pressure and low pressure of the refrigerant (hereinafter referred to as "compression ratio control") to provide an operational point that improves the efficiency of the compressor 10.
  • a pressure ratio high pressure/low pressure
  • compression ratio control a pressure ratio between the high pressure and low pressure of the refrigerant
  • the storage 46 stores compressor efficiency distribution information that indicates the distribution of the efficiency of the compressor 10 obtained from the rotation speed of the compressor 10 and the pressure ratio.
  • FIG. 3 is an efficiency map showing an example of compressor efficiency distribution information.
  • the horizontal axis indicates the rotation speed of the compressor 10
  • the vertical axis indicates the pressure ratio
  • the solid contour lines indicate the efficiency of the compressor 10.
  • Compressor efficiency distribution information may be stored in storage 46 in the form of a function, a table, or the like independently of an efficiency map like that of FIG. 3 .
  • Pressure regulating control and compression ratio control executed by the air conditioner control device 40 according to this embodiment will now be explained.
  • pressure regulating control and compression ratio control are collectively referred to as efficiency-enhancing control.
  • pressure regulating control regulates the operation pressure of the refrigerant independently of the indoor load.
  • the rotation speed of the compressor 10 is reduced such that the pressure of the refrigerant becomes a newly adjusted target pressure, thereby performing energy-saving control for suppressing the performance of the compressor 10.
  • a decrease in indoor load refers to the approach of the indoor suction temperature and the set temperature to a predetermined range. If plurality of indoor units 3 are connected like in the multi-type air-conditioning system 1 according to this embodiment, for example, when the difference between the indoor suction temperature and the set temperature of more than half of the indoor units 3 is less than or equal to 1°C, the indoor load is regarded as decreasing.
  • the pressure control unit 42 increases the current target pressure (target low pressure) to reduce the rotation speed of the compressor 10. On the contrary, if the indoor load decreases during heating, the pressure control unit 42 reduces the current target pressure (target high pressure) to reduce the rotation speed of the compressor 10.
  • the target pressure is adjusted step by step and the difference between the indoor suction temperature and the set temperature is detected upon each adjustment. When the difference increases, the performance of the compressor 10 becomes insufficient for the indoor load, so that the adjustment of the target pressure terminates.
  • the operational point represented by the point A is an operational point given under normal control before adjustment of the target pressure, i.e., before execution of energy-saving control.
  • the point B is an operational point given after execution of energy-saving control.
  • the operational point B given after energy-saving control is not necessarily an operational point efficient for the compressor 10.
  • a region with a high pressure ratio e.g., a region containing a point C
  • a region with a high pressure ratio is an operational point with higher efficiency.
  • compression ratio control controls the pressure ratio to provide an operational point (the point C in the example of FIG. 3 and hereinafter referred as "efficiency optimum operational point") that improves the efficiency of the compressor 10.
  • Table 1 shows the adjustment of the operational point of the compressor 10 during cooling and heating.
  • compression ratio control is performed by controlling the high pressure (ejection pressure) of the refrigerant during cooling
  • energy-saving control is performed by controlling the low pressure (suction pressure) of the refrigerant.
  • energy-saving control is performed by controlling the high pressure of the refrigerant during heating
  • compression ratio control is performed by controlling the low pressure of the refrigerant.
  • the pressure ratio control unit 44 performs compression ratio control by changing the rotation speed of an outdoor fan 24, for example.
  • compression ratio control can be achieved without changing the rotation speed of the compressor 10.
  • compression ratio control achieves the control of the pressure ratio without controlling the compressor 10 and easily changes the operational point of the compressor 10 to a desired value.
  • the efficiency optimum operational point is predetermined to be, for example, a pressure ratio that provides the highest efficiency for the rotation speed of the compressor 10, and may have a certain width in the scale direction of the pressure ratio.
  • FIG. 4 is a flow chart of an efficiency-enhancing control process executed by the air conditioner control device 40.
  • a program for executing this process (an efficiency-enhancing control program) is stored in advance in a predetermined region in the storage 46. It should be noted that before execution of the efficiency-enhancing control process, pressure regulating control (normal control) without energy-saving control is performed in the air conditioner control device 40.
  • Step S100 whether the indoor load has decreased to a level at which energy-saving control can be started is determined. If yes, the process proceeds to Step S102. If no, normal control is continued.
  • Step S102 normal control is terminated and settings are made to start energy-saving control.
  • the target pressure is adjusted to perform energy-saving control. It should be noted that during cooling, the target pressure (target low pressure) is increased, and during heating, the target pressure (target high pressure) is decreased.
  • Step S106 whether the operation pressure matches the adjusted target pressure is determined. If yes, the process proceeds to Step S110. If no, the process proceeds to Step S108.
  • Step S108 the rotation speed of the compressor 10 is controlled such that the operation pressure and the target pressure match.
  • the process returns to Step S106 in which the operation pressure is compared with the adjusted target pressure.
  • the rotation speed of the compressor 10 is decreased.
  • the low pressure suction pressure
  • the high pressure ejection pressure
  • Step S110 the efficiency optimum operational point depending on the rotation speed of the compressor 10 is set.
  • Step S112 whether the actual pressure ratio and a pressure ratio at the efficiency optimum operational point match is determined. If no, the process proceeds to Step S114. If yes, the process returns to Step S106 and energy-saving control and compression ratio control are repeatedly continued.
  • Step S114 the rotation speed of the outdoor fan 24 is controlled such that the actual pressure ratio and the pressure ratio at the efficiency optimum operational point match.
  • the process returns again to Step S112 in which the pressure ratio is compared with the pressure ratio at the efficiency optimum operational point.
  • the rotation speed of the outdoor fan 24 is decreased. Accordingly, during cooling, the high pressure increases, and during heating, the low pressure decreases, so that the actual pressure ratio increases.
  • the actual pressure ratio is higher than the pressure ratio at the efficiency optimum operational point, the rotation speed of the outdoor fan 24 is increased. Accordingly, during cooling, the high pressure decreases, and during heating, the low pressure increases, so that the actual pressure ratio decreases.
  • the air conditioner control device 40 controls the rotation speed of the compressor 10 such that the operation pressure of the refrigerant becomes a predetermined target pressure and, after this control, controls the pressure ratio between the high pressure and low pressure of the refrigerant to provide an operational point that improves the efficiency of the compressor 10.
  • the air conditioner control device 40 reduces the power consumption of the compressor 10 and allows the compressor 10 to operate more efficiently.
  • the rotation speed of the outdoor fan 24 is controlled to control the pressure ratio according to the description of the above embodiment, the present invention is not limited to this, and the degree of opening of the outdoor expansion valve 15 may be controlled to control the pressure ratio.
  • Step S114 if the actual pressure ratio is lower than the pressure ratio at the efficiency optimum operational point, the outdoor expansion valve 15 is closed. Accordingly, during cooling, the high pressure increases, and during heating, the low pressure decreases, so that the actual pressure ratio increases. On the contrary, if the actual pressure ratio is higher than the pressure ratio at the efficiency optimum operational point, the outdoor expansion valve 15 is opened. Accordingly, during cooling, the high pressure decreases, and during heating, the low pressure increases, so that the actual pressure ratio decreases.
  • both the rotation speed of the outdoor fan 24 and the degree of opening of the outdoor expansion valve 15 may be controlled to control the pressure ratio.
  • parallel-connected multiple refrigerant circuits each including a throttle and an electromagnetic valve may be provided and the degree of throttling may be changed by changing the flow path of the refrigerant by opening and closing the electromagnetic valve, thereby controlling the pressure ratio.
  • a plurality of outdoor heat-exchangers 13 may be provided and the pressure ratio may be controlled by changing the number (capacity) of outdoor heat-exchangers 13 carrying the refrigerant.
  • compression ratio control is performed after energy-saving control according to the description of the above embodiment, the present invention is not limited to this and compression ratio control may be performed without energy-saving control.
  • compression ratio control may be performed to make the operational point of the compressor 10 be the operational point C with higher efficiency.
  • the air conditioner control device 40 performs pressure regulating control for regulating the operation pressure of the refrigerant to be constant independently of the indoor load according to the description of the above embodiment, the present invention is not limited to this and energy-saving control may be performed without pressure regulating control.
  • energy-saving control is performed when the indoor load decreases according to the description of the above embodiment, the present invention is not limited to this and energy-saving control may be performed not only when the indoor load decreases but also when the user (manager) of the multi-type air-conditioning system 1 changes settings, for example, a setting for decreasing the rotation speed of the compressor 10 or a setting for changing the target pressure of the refrigerant.

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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)

Claims (6)

  1. Steuervorrichtung für eine Klimaanlage, die ausgestaltet ist, zum Erfassen eines niedrigen Drucks eines Kühlmittels während des Kühlens und eines hohen Drucks des Kühlmittels während des Heizens durch einen Kompressorsensor, jeweils als Druck-Erfassungswert, und zum Durchführen einer Druckregelsteuerung zum Regeln des Druck-Erfassungswertes durch Steuerung der Rotationsgeschwindigkeit eines Kompressors (10), so dass diese konstant ist, so dass der Druck-Erfassungswert unabhängig von einer Innenraumlast ein vorgegebener Zielwert wird, wobei die Steuervorrichtung umfasst:
    ein Drucksteuermittel (42), das ausgestaltet ist, um eine Energiesparsteuerung durchzuführen, um eine Rotationsgeschwindigkeit des einen Kompressors (10) zu verringern, wenn die Innenraumlast abnimmt, so dass der Druck-Erfassungswert ein neu eingestellter Zieldruck wird; und
    ein Kompressionsverhältnissteuermittel (44), das ausgestaltet ist, um den hohen Druck des Kühlmittels während des Kühlens und den niedrigen Druck des Kühlmittels während des Heizens zu steuern, um ein Druckverhältnis zwischen dem hohen Druck und dem niedrigen Druck des Kühlmittels zu steuern, nach dem Steuern des Drucksteuermittels (42), um einen Betriebspunkt bereitzustellen, der die Effizienz des Kompressors verbessert, wobei die Steuervorrichtung ausgestaltet ist, so dass:
    während des Kühlens das Kompressionsverhältnissteuermittel (44) den hohen Druck des Kühlmittels steuert, und das Drucksteuermittel den niedrigen Druck des Kühlmittels steuert, und während des Heizens das Drucksteuermittel (42) hohen Druck des Kühlmittels steuert und das Kompressionsverhältnissteuermittel (44) den niedrigen Druck des Kühlmittels steuert; und
    das Kompressionsverhältnissteuermittel (44) das Druckverhältnis durch Steuern einer Rotationsgeschwindigkeit eines Gebläses (24) steuert, das an einer Außeneinheit (2) vorgesehen ist, und/oder das Öffnungsausmaß eines Expansionsventils (15) steuert, das an einer Außeneinheit (2) vorgesehen ist.
  2. Steuervorrichtung für eine Klimaanlagen nach Anspruch 1, bei dem das Drucksteuermittel (42) ausgeschaltet ist, um die Rotationsgeschwindigkeit des Kompressors (10) so zu verringern, dass der Betriebsdruck gleich dem Zieldruck wird.
  3. Steuervorrichtung für eine Klimaanlagen nach Anspruch 1 oder 2, bei dem das Kompressionsverhältnissteuermittel (44) ausgeschaltet ist, um das Druckverhältnis zu steuern, ohne die Rotationsgeschwindigkeit des Kompressors (10) zu ändern.
  4. Klimaanlagensystem mit:
    einer Außeneinheit (2);
    einer Inneneinheit (3A,3B); und
    einer Steuervorrichtung (40) nach einem der Ansprüche 1 bis 3.
  5. Steuerverfahren für ein Klimaanlagensystem, das einen niedrigen Druck eines Kühlmittels während des Kühlens und einen hohen Druck des Kühlmittels während des Heizens erfasst, jeweils als einen Druck-Erfassungswert, und das eine Druckregelsteuerung zum Regeln des Druck-Erfassungswertes durchführt, so dass dieser konstant wird, so dass der Druck-Erfassungswert unabhängig von der Innenraumlast ein vorgegebener Zieldruck wird, wobei das Steuerverfahren umfasst:
    einen ersten Schritt zum Durchführen einer Energiesparsteuerung zur Verringerung der Rotationsgeschwindigkeit eines Kompressors (10), wenn die Innenraumlast abnimmt, so dass der Druck-Erfassungswert ein neu eingestellter Zieldruck wird; und
    einen zweiten Schritt zum Steuern des hohen Drucks des Kühlmittels während des Kühlens und des niedrigen Drucks des Kühlmittels während des Heizens, zum Steuern eines Druckverhältnisses zwischen dem hohen Druck und dem niedrigen Druck des Kühlmittels nach dem Steuern des ersten Schritts, um einen Betriebspunkt bereitzustellen, der die Effizienz des Kompressors verbessert; wobei
    während des Kühlens der zweite Schritt den hohen Druck des Kühlmittels steuert und der erste Schritt den niedrigen Druck des Kühlmittels steuert, und während des Heizens der erste Schritt den hohen Drucks des Kühlmittels steuert und der zweite Schritt den niedrigen Druck des Kühlmittels steuert; und
    wobei der erste Schritt das Druckverhältnis durch Steuern einer Rotationsgeschwindigkeit eines Gebläses steuert, das an einer Außeneinheit vorgesehen ist, und/oder durch das Öffnungsausmaßes eines Expansionsventils steuert, das an einer Außeneinheit vorgesehen ist.
  6. Steuerprogramm für ein Klimaanlagensystem nach einem der Ansprüche 1 bis 4, bei dem das Steuerprogramm einen Computer veranlasst, das Verfahren nach Anspruch 5 auszuführen.
EP16768455.4A 2015-03-26 2016-03-10 Klimatisierungssystemsteuerungsvorrichtung, klimatisierungssystem, klimatisierungsteuerungsprogramm und klimatisierungssystemsteuerungsverfahren Active EP3260792B1 (de)

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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
PCT/JP2016/057550 WO2016152552A1 (ja) 2015-03-26 2016-03-10 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

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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
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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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