WO2017208438A1 - Système de climatisation - Google Patents

Système de climatisation Download PDF

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Publication number
WO2017208438A1
WO2017208438A1 PCT/JP2016/066616 JP2016066616W WO2017208438A1 WO 2017208438 A1 WO2017208438 A1 WO 2017208438A1 JP 2016066616 W JP2016066616 W JP 2016066616W WO 2017208438 A1 WO2017208438 A1 WO 2017208438A1
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Prior art keywords
temperature
refrigerant
compressor
difference
control
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PCT/JP2016/066616
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English (en)
Japanese (ja)
Inventor
伊藤　慎一
正樹 豊島
守 濱田
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三菱電機株式会社
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2016/066616 priority Critical patent/WO2017208438A1/fr
Priority to JP2018520317A priority patent/JP6538975B2/ja
Publication of WO2017208438A1 publication Critical patent/WO2017208438A1/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
    • F25B1/00—Compression machines, plants or systems with non-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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle

Definitions

  • an air conditioning system including a refrigerant circuit that performs a vapor compression refrigeration cycle is known.
  • an air conditioner for adjusting the temperature of the indoor space and a humidity control device for adjusting the humidity of the indoor space supply air to the same indoor space.
  • Patent Document 1 discloses an air rhyowa system including a latent heat system refrigerant circuit for processing an indoor latent heat load and a sensible heat system refrigerant circuit for processing an indoor sensible heat load. It is disclosed.
  • Patent Document 1 a generated sensible heat treatment capacity value corresponding to the processing capacity of a sensible heat load processed together with a latent heat treatment in a latent heat system refrigerant circuit is calculated, and the sensible heat system compression mechanism is considered in consideration of the generated sensible heat treatment stress value. Control the operating capacity. Thereby, the sensible heat processing capability in the sensible heat system refrigerant circuit is prevented from becoming excessive.
  • the operating capacity of the sensible heat system compression mechanism is controlled in the direction of decreasing the sensible heat treatment capability by increasing the refrigerant evaporation temperature in accordance with the generated sensible heat treatment stress value.
  • the air conditioning capacity per air volume decreases in the sensible heat system refrigerant circuit by increasing the refrigerant evaporation temperature, the air volume supplied to the indoor space is increased. As a result, there is a possibility that the occupant's comfort is impaired due to the direct hit of the occupants.
  • an air conditioning system including an air conditioner and a ventilator
  • the capacity of the air conditioner is set according to the indoor load
  • the capacity of the ventilator is set according to the ventilator load.
  • it is required that such a highly efficient air conditioning system can be easily constructed with an existing system configuration.
  • the present invention has been made to solve the above-described problems, and an object of the present invention is to provide high operating efficiency and occupancy in an air conditioning system including a plurality of air conditioners targeting the same indoor space. Is to realize the comfort of the elderly.
  • the air conditioning system includes a first air conditioner, a second air conditioner, and a control device.
  • the first air conditioner has a first refrigerant circuit and is configured to supply air to the indoor space.
  • the second air conditioner has a second refrigerant circuit and is configured to supply air to the indoor space.
  • the control device is configured to control the first and second air conditioners.
  • Each of the first and second refrigerant circuits includes a compressor, a condenser, an expansion valve, and an evaporator, and is configured to circulate the refrigerant in the order of the compressor, the condenser, the expansion valve, and the evaporator.
  • the control device By increasing the operating frequency of the compressor in the first refrigerant circuit and decreasing the operating frequency of the compressor in the second refrigerant circuit, the difference between the first refrigerant evaporation temperature and the second refrigerant evaporation temperature is reduced. To do.
  • an air conditioning system including a plurality of air conditioners targeting the same indoor space, it is possible to achieve high operating efficiency and comfort for occupants.
  • the cooperation control discharge superheat degree difference control
  • FIG. 1 is a configuration diagram of an air conditioning system 100 according to an embodiment of the present invention.
  • Air conditioning system 100 includes two air conditioners (a first air conditioner and a second air conditioner) that air-condition the same indoor space.
  • the air conditioning system 100 includes an air conditioner 1 and a ventilator 2 and is configured to air-condition the same room R.
  • one of the two air conditioners does not need to be a ventilator, and both may be air conditioners. That is, the attributes of the two air conditioners are not limited.
  • Detected values by the pipe temperature detectors 11h, 11i, 12h, and 12i are used to calculate the degree of superheat and the degree of supercooling of the refrigerant flowing through the refrigerant circuit 1000.
  • the degree of superheat of the refrigerant is the difference between the evaporation temperature ET and the refrigerant temperature at the evaporator outlet.
  • the degree of supercooling of the refrigerant is the difference between the condensation temperature CT and the temperature of the refrigerant at the condenser outlet.
  • the external air conditioner control unit 21 f adjusts the flow rate of the refrigerant flowing in the refrigerant circuit 2000 by controlling the opening degree of the expansion valve 21. In addition, the external air conditioner control unit 21f controls the amount of air blown by the blower 21g.
  • the outdoor unit controller 10f sets the target value (target condensing temperature CT1 *) of the condensing temperature CT1 based on the outdoor temperature detected by the outdoor temperature detecting unit 1b
  • the outdoor unit controller 10f sets the target air temperature of the blower 10g based on the target condensing temperature CT1 *. Set the air flow.
  • the outdoor unit control part 10f controls the rotational speed of the air blower 10g so that the air flow rate of the air blower 10g becomes the set air volume.
  • Control of ventilation device 2 The outdoor unit control unit 20f and the outdoor conditioner control unit 21f control the ventilator 2 based on the detection value of the control target detection unit 1c.
  • the outdoor unit control unit 20f is configured so that the blown air temperature SA detected by the controlled object detection unit 1c matches the target value (target blown air temperature SA *) set by the controller 30. 2 is controlled. Specifically, the outdoor unit control unit 20f calculates the necessary air conditioning capacity based on the deviation ⁇ 1 of the detected temperature SA of the controlled object detection unit 1c with respect to the target blown air temperature SA * and a preset ventilation air volume. . And the outdoor unit control part 20f controls the operating frequency of the compressor 20a based on the calculated air conditioning capability so that the target blown air temperature SA * can be reached.
  • Steps S01 to S04 in FIG. 5 show processing for determining whether or not to shift from normal control to cooperative control.
  • step S02 it is determined whether or not the operating state of the compressor is stable in each of the air conditioner 1 and the ventilator 2. Specifically, it is determined whether each of the compressors 10a and 20a is continuously operated for a predetermined time (referred to as A time) set in advance.
  • a time a predetermined time
  • the “A time” used for the determination in step S02 is a time set for determining whether or not each of the air conditioner 1 and the ventilator 2 is in a start / stop state in which the operation and the stop are repeated. is there.
  • the A time it is necessary to consider the time until the operation state of the compressor is stabilized when the operation frequency of the compressor or the opening of the expansion valve is changed. For example, the A time is set to about 30 minutes.
  • the air conditioning system 100 transitions from normal control to cooperative control.
  • the operation state is shared between the air conditioner 1 and the ventilator 2.
  • the cooperative control during the cooling operation includes “evaporation temperature difference control”, “high / low pressure temperature difference control”, and “discharge superheat degree difference control”.
  • “Evaporation temperature difference control” is control for reducing the difference between the evaporation temperature ET1 in the air conditioner 1 and the evaporation temperature ET2 in the ventilation device 2.
  • “High / low pressure temperature difference control” refers to the difference between the temperature difference between the condensation temperature CT1 and the evaporation temperature ET1 (high and low pressure temperature difference) in the air conditioner 1 and the temperature difference between the condensation temperature CT2 and the evaporation temperature ET2 in the ventilation device 2. This is control for reducing the size.
  • evaporation temperature difference control is executed as the first mode of the cooperative control executed during the cooling operation.
  • FIG. 8 is a diagram showing the relationship between the evaporation temperature ET in the air conditioner 1 and the ventilator 2 and the power consumption of the air conditioning system 100 as a whole.
  • the horizontal axis indicates the evaporation temperature ET
  • the vertical axis indicates the power consumption of the entire air conditioning system.
  • the relationship indicated by k1 in FIG. 8 is that between the air conditioner 1 and the ventilator 2, the amount of air supplied to the room, the condensation temperature, the heat exchanger performance (heat exchange efficiency), the performance of the compressor (compressor efficiency) and The case where the intake air temperature and humidity are equivalent is assumed.
  • the power consumption of the entire air conditioning system can be calculated from the inverse Carnot cycle in each of the refrigerant circuit 1000 and the refrigerant circuit 2000.
  • FIG. 9 indicates the relationship between the evaporation temperature ET and the power consumption of the entire air conditioning system when the compressor efficiency of the air conditioner 1 is higher than the compressor efficiency of the ventilator 2.
  • FIG. 10 indicates a relationship between the evaporation temperature ET and the power consumption of the entire air conditioning system when the compressor efficiency of the ventilation device 2 is higher than the compressor efficiency of the air conditioner 1.
  • the power consumption is minimized when the evaporation temperature ET2 is slightly lower than the evaporation temperature ET1.
  • the evaporating temperature ET2 is lowered in the ventilator 2 having a high compressor efficiency so that the ventilator 2 handles more load.
  • the power consumption of the whole air conditioning system reduces as a result.
  • the absolute value of the difference between the evaporation temperature ET1 and the evaporation temperature ET2 is also expressed as “evaporation temperature difference ⁇ ET”.
  • the calculated evaporation temperature difference ⁇ ET is compared with the third threshold value (D ° C). If the evaporation temperature difference ⁇ ET is greater than D ° C. (when YES is determined in S05), the process proceeds to step S06. On the other hand, if the evaporation temperature difference ⁇ ET is equal to or less than D ° C. (NO determination in S05), the process proceeds to step S13 in FIG.
  • D ° C.” (third threshold value) used for the determination in step S05 is an index for determining whether or not to start the evaporation temperature difference control.
  • the expansion valve operates to stabilize the refrigeration cycle.
  • the evaporation temperature may fluctuate.
  • the allowable fluctuation range of the evaporation temperature it is determined whether or not the evaporation temperature difference control is started taking into account the temporary fluctuation caused by the expansion valve. can do.
  • “D ° C.” (third threshold value) is “B ° C.” (first threshold value) in step S03 and “C ° C.” in step S04 ( It is preferable to set a value equal to or greater than (second threshold).
  • step S06 Comparison of evaporation temperature If the evaporation temperature difference ⁇ ET is greater than D ° C. (when YES is determined in S05), the magnitudes of the evaporation temperature ET1 and the evaporation temperature ET2 are compared in step S06. Based on the comparison result, the operating frequencies of the compressor 10a of the air conditioner 1 and the compressor 20a of the ventilation device 2 are changed.
  • step S08 Operation for lowering the evaporation temperature of the ventilator
  • the amount of increase in the evaporation temperature ET1 in step S07 and the amount of decrease in the evaporation temperature ET2 in step S08 can be, for example, the magnitude obtained by distributing the evaporation temperature difference ⁇ ET by the ratio of the operating capacities of the compressors 10a and 20a.
  • both the increase amount and the decrease amount can be set to a magnitude obtained by multiplying the evaporation temperature difference ⁇ ET by a predetermined ratio (for example, about 30%).
  • step S10 Operation for lowering the evaporation temperature of the air conditioner
  • step S10 the operating frequency of the compressor 10a of the air conditioner 1 is lowered.
  • the evaporation temperature ET1 in the air conditioner 1 is lowered.
  • step S11 Determination of continuation of evaporation temperature difference control
  • the process proceeds to step S11, and it is determined whether or not the operating state has been changed for either the air conditioner 1 or the ventilator 2. Is done. Specifically, when the set temperature, the set air volume, or the like is changed in either the air conditioner 1 or the ventilator 2 (YES in S11), it is determined that the evaporation temperature difference control cannot be continued. The Therefore, the air conditioning system 100 transitions from cooperative control to normal control.
  • step S11 when neither the air conditioner 1 nor the ventilator 2 has been changed (when NO is determined in S11), the process proceeds to step S12, and the deviation of the detected temperature T by the indoor temperature detector 1a from the target indoor temperature T *. It is determined whether ⁇ 1 is equal to or less than a predetermined threshold value ( ⁇ E ° C.). When the deviation ⁇ 1 is ⁇ E ° C. or less (when YES in S12), the process returns to step S05 to continue the evaporation temperature difference control.
  • ⁇ E ° C. a predetermined threshold value
  • E ° C.” used in the determination in step S12 is an index for determining whether or not to continue the evaporation temperature difference control. In setting this index, it is necessary to take into account a temporary change in room temperature due to a change in the operating frequency of the compressor. Therefore, “E ° C.” is preferably set to a value larger than “B ° C.” (first threshold) in step S03.
  • step S05 If it is determined in step S05 that the evaporation temperature difference ⁇ ET is equal to or lower than D ° C. (at the time of NO determination in S05), next, high / low pressure temperature difference control is executed as a second mode of the cooperative control.
  • the high / low pressure temperature difference control In the high / low pressure temperature difference control, the difference between the high / low pressure temperature difference (CT1-ET1) in the air conditioner 1 and the high / low pressure temperature difference (CT2-ET2) in the ventilator 2 is reduced. Therefore, the operating frequency of the compressor is lowered in order to reduce the high / low pressure temperature difference in the apparatus having the higher high / low pressure temperature difference. On the other hand, in the apparatus with the lower high-low pressure temperature difference, the operating frequency of the compressor is increased in order to increase the high-low pressure temperature difference.
  • the condensation temperature CT1 and the condensation temperature CT2 may be different.
  • the condensation temperature is different between the air conditioner 1 and the ventilator 2
  • the compression ratio in the compressor is different.
  • the amount of refrigerant circulating in the compressor decreases and the work of the compressor increases. Therefore, the air conditioning system 100 is not necessarily in an optimal operating state from the viewpoint of operating efficiency.
  • the condensation temperature is affected by the condenser performance such as the condenser capacity and the amount of air blown to the condenser. Therefore, if the performance of the condenser differs between the air conditioner 1 and the ventilator 2, the condensation temperature also differs.
  • the performance of the condenser is compared between the air conditioner 1 and the ventilator 2 by comparing the high-low pressure difference (CT1-ET1) with the high-low pressure difference (CT2-ET2).
  • CT1-ET1 high-low pressure difference
  • CT2-ET2 high-low pressure difference
  • the absolute value of the calculated difference is compared with a fourth threshold value (F ° C). If the absolute value of the difference is greater than F ° C. (when YES is determined in S13), the process proceeds to step S14. On the other hand, when the absolute value of the difference is equal to or lower than F ° C. (when NO is determined in S13), the process proceeds to step S21 in FIG.
  • F ° C.” (fourth threshold) used in the determination in step S13 is an index for determining whether to start high-low pressure difference control.
  • the high / low pressure temperature difference becomes large.
  • the high / low pressure temperature difference is reduced.
  • the high-low pressure temperature difference changes by changing the operating frequency of the compressor.
  • the operating frequency of the compressors 10a and 20a is changed, so that the high / low pressure temperature difference (CT1-ET1) in the air conditioner 1 and the high / low pressure temperature difference (CT2) in the ventilator 2 are changed.
  • CT1-ET1 high / low pressure temperature difference
  • CT2 high / low pressure temperature difference
  • the difference from -ET2) is increasing. This difference is larger than the evaporation temperature difference ⁇ ET.
  • F ° C.” is preferably set to a value equal to or higher than “D ° C.” (third threshold value), which is a determination index, as to whether or not to start the steam temperature difference control. In this way, since the evaporation temperature difference control can be preferentially executed as compared with the high and low pressure difference control, the cooperative control can be stabilized.
  • step S16 High / low pressure temperature difference increase operation of air conditioner
  • step S16 the operating frequency of the compressor 10a of the air conditioner 1 is increased.
  • CT1-ET1 the high-low pressure temperature difference
  • CT2-ET2 high / low pressure temperature difference
  • CT1-ET1-ET1 high / low pressure temperature difference
  • CT1-Et1 high-low pressure temperature difference
  • CT2-ET2 high / low pressure temperature difference
  • CT1-ET1 high / low pressure temperature difference
  • CT1-ET1 high / low pressure temperature difference
  • S17 high / low pressure temperature difference
  • CT2-ET2 high-low pressure temperature difference
  • step S20 the deviation ⁇ 1 of the indoor temperature detector 1a with respect to the target indoor temperature T * is a predetermined value. It is determined whether or not the threshold value ( ⁇ E ° C.) or less. When the deviation ⁇ 1 is ⁇ E ° C. or less (when YES is determined in S20), the high / low pressure temperature difference control is continued by returning the process to step S13.
  • discharge superheat difference control If it is determined in step S13 that the absolute value of the difference between the high / low pressure temperature difference (CT1-ET1) and the high / low pressure temperature difference (CT2-ET2) is F ° C. or less (NO in S13), then As a third aspect of the cooperative control, discharge superheat degree difference control is executed.
  • the discharge superheat difference control In the discharge superheat difference control, the difference between the discharge superheat degree (Td1-CT1) in the air conditioner 1 and the discharge superheat degree (Td2-CT2) in the ventilator 2 is reduced. Therefore, in the device having the higher discharge superheat degree, the operating frequency of the compressor is lowered in order to lower the discharge temperature. On the other hand, in the apparatus with the lower discharge superheat degree, the operating frequency of the compressor is increased in order to increase the discharge temperature.
  • the difference in the discharge superheat degree represents the difference in the discharge temperature of the compressor. Therefore, the discharge superheat degree is an index indicating the performance of the compressor.
  • the air conditioning system 100 is not necessarily in an optimal operating state from the viewpoint of operating efficiency due to the difference in the performance of the compressor.
  • G ° C.” is preferably set to a value equal to or higher than “F ° C.” (fourth threshold value), which is a determination index for determining whether to start high-low pressure difference control. If it does in this way, since it can prevent that the driving
  • the discharge superheat degree (Td2-CT2) is smaller than the discharge superheat degree (Td1-CT1) (when NO is determined in S22)
  • the discharge superheat degree (Td1-CT1) is reduced (S25), and the discharge superheat degree is set.
  • the operating frequency of the compressors 10a and 20a is changed so as to increase the degree (Td2-CT2) (S26).
  • step S27 When an operation for reducing the difference in discharge superheat degree is performed in steps S21 to S26, the process proceeds to step S27, and it is determined whether or not the operating state has been changed for either the air conditioner 1 or the ventilator 2. Determined. Specifically, when the set temperature, the set air volume, or the like is changed in either the air conditioner 1 or the ventilator 2 (YES in S27), it is determined that the discharge superheat difference control cannot be continued. Is done. Therefore, the air conditioning system 100 transitions from cooperative control to normal control.
  • step S27 if the setting has not been changed in either the air conditioner 1 or the ventilator 2 (NO determination in S27), the process proceeds to step S28, and the deviation of the detected temperature T by the indoor temperature detector 1a with respect to the target indoor temperature T *. It is determined whether ⁇ 1 is equal to or less than a predetermined threshold ( ⁇ E ° C.). When the deviation ⁇ 1 is ⁇ E ° C. or less (when YES is determined in S28), the process returns to step S21 to continue the discharge superheat difference control.
  • ⁇ E ° C. a predetermined threshold
  • step S29 Operation state maintenance operation
  • step S30 it is determined whether or not the operating state setting has been changed for either the air conditioner 1 or the ventilator 2. Specifically, when the set temperature, the set air volume, and the like are changed in either the air conditioner 1 or the ventilator 2 (YES in S30), it is determined that the discharge superheat difference control cannot be continued. Is done. Therefore, the air conditioning system 100 transitions from cooperative control to normal control.
  • step S30 when the setting is not changed in either the air conditioner 1 or the ventilator 2 (NO determination in S30), the process proceeds to step S31, and the deviation of the detected temperature T by the indoor temperature detection unit 1a with respect to the target indoor temperature T *. It is determined whether ⁇ 1 is within a predetermined range ( ⁇ B ° C.). When the deviation ⁇ 1 is ⁇ B ° C. or less (when YES is determined in S31), the process returns to step S29 to continue the discharge superheat difference control.
  • the operation of lowering the operating frequency of one of the compressors is performed. It is preferable to perform an operation for increasing the operating frequency of the other compressor (an operation for increasing the degree of discharge superheat).
  • the evaporation temperature difference control, the high / low pressure temperature difference control, and the discharge are performed as the cooperative control of the two air conditioners (the air conditioner 1 and the ventilator 2). Execute superheat difference control. Thereby, uneven distribution of the processing load between the two air conditioners can be suppressed, and as a result, the operation efficiency of the air conditioning system 100 can be improved.
  • the ventilator 2 continues to operate at a high capacity so that the blown air temperature matches the target blown air temperature.
  • the air conditioner 1 performs an operation at a low capacity because the indoor load is small.
  • the ventilator 2 it is necessary to lower the evaporation temperature ET2 in order to increase the capacity per air volume during high capacity operation, and as a result, the compressor efficiency tends to decrease.
  • the air conditioner 1 since the low capacity operation is performed, the evaporation temperature ET1 can be raised, and there is room for improving the compressor efficiency.
  • the air conditioning capacity per air volume of the air conditioner 1 is reduced, and thus the load that can be processed by the air conditioner 1 is reduced. As a result, the load to be processed by the low-efficiency ventilator 2 further increases, and the operation efficiency of the air conditioning system 100 may be reduced.
  • the operating frequency of the compressor 10a is increased so as to decrease the evaporating temperature ET1, while the operating frequency of the compressor 20a is decreased so as to increase the evaporating temperature ET2.
  • the air conditioner 1 since the air conditioning capability per air volume increases, the load which can be processed increases.
  • the ventilator 2 the compressor efficiency is improved due to the increase in the evaporation temperature ET2.
  • the load which the ventilation apparatus 2 should process decreases by the load which the air conditioner 1 processes increases. As a result, the power consumption of the entire air conditioning system is reduced compared to the power consumption during normal control. Therefore, the operating efficiency of the air conditioning system 100 is improved.
  • the amount of heat processed by each of the air conditioner 1 and the ventilator 2 and the amount of air supplied to the indoor space are not significantly changed. Therefore, both user comfort and energy saving can be achieved.
  • the information necessary for improving the efficiency of the air conditioning system can be limited to information related to the evaporation temperature, even if the characteristics of the devices constituting each air conditioner are not known, it is based on the evaporation temperature.
  • the linkage control can be easily executed. According to this, for example, cooperation control with a device whose characteristic value is unknown, such as a device installed in the past, can be performed. As a result, highly versatile control can be constructed.
  • a third threshold value (D ° C.) that is an index for determining whether or not to start the evaporation temperature difference control is determined whether or not the operating states of the air conditioner 1 and the ventilator 2 are stable.
  • a threshold (E ° C.), which is an index for determining whether to continue the cooperative control, is an index (B) for determining whether the operating state of the air conditioner 1 is stable during normal control.
  • the performance of the heat exchanger that each device has can be Comparison can be made through high and low pressure difference. Thereby, the cooperation control which considered the performance of the heat exchanger can be constructed.
  • the discharge temperatures in the state where the compression ratios of the refrigeration cycles in the air conditioner 1 and the ventilator 2 are equivalent can be compared. Since the discharge temperature in this state is a value that does not depend on the state of the refrigeration cycle, it serves as an index indicating the performance of the compressor. Therefore, cooperative control in consideration of the compressor performance is possible, and as a result, the accuracy of control for efficiency can be improved.
  • FIG. 11 is a diagram illustrating a modification example of the cooperative control executed in the air conditioning system 100 according to the present embodiment.
  • the air conditioner 1 is operated at a high capacity so that the room temperature matches the target room temperature.
  • the ventilator 2 is operating at a low capacity. The control target value has not yet been achieved in the air conditioner 1, and the control target value has been achieved in the ventilator 2.
  • a total heat exchanger that exchanges sensible heat or total heat between the return air and outside air may be installed. If it does in this way, since the temperature of the air which flows in into the heat exchanger of the ventilation apparatus 2 approaches indoor temperature, it can be brought close to the assumption conditions in evaporation temperature difference control. As a result, it is possible to approach the optimum operating state for efficiency by the evaporation temperature difference control.
  • step S05A Determination of start of condensation temperature difference control
  • the absolute value of the difference between the condensation temperature CT1 and the condensation temperature CT2 is also expressed as “condensation temperature difference ⁇ CT”.
  • the calculated condensation temperature difference ⁇ CT is compared with the third threshold (D ° C.).
  • D ° C. the third threshold
  • the process proceeds to step S06A.
  • the condensation temperature difference ⁇ CT is equal to or less than D ° C. (when NO is determined in S05A)
  • the process proceeds to step S13 in FIG.
  • “D ° C.” (third threshold) used for the determination in step S05A is an index for determining whether or not to start the condensation temperature difference control.
  • “D ° C.” (third threshold) is preferably set to a value equal to or higher than “B ° C.” (first threshold) in step S03 and “C ° C.” (second threshold) in step S04.
  • step S08A Operation for increasing the condensation temperature of the air conditioner
  • the condensation temperature CT2 is higher than the condensation temperature CT1 (when YES is determined in S06A)
  • the condensation temperature CT2 is decreased (S07A), and the condensation temperature CT1 is increased (S08A).
  • the operation frequency of each of 20a is changed. Thereby, the condensation temperature difference ⁇ CT is reduced.
  • the amount of decrease in the condensation temperature CT2 in step S07A and the amount of increase in the condensation temperature CT1 in step S08A can be, for example, the magnitude obtained by distributing the condensation temperature difference ⁇ CT by the ratio of the operating capacities of the compressors 10a and 20a.
  • both the increase amount and the decrease amount can be set to a size obtained by multiplying the condensation temperature difference ⁇ CT by a predetermined ratio (for example, about 30%).
  • step S10A Operation for increasing the condensation temperature of the ventilator
  • the condensation temperature CT1 is higher than the condensation temperature CT2 (when NO is determined in S06A)
  • the condensation temperature CT1 is decreased (S09A)
  • the condensation temperature CT2 is increased (S10A).
  • the operation frequency of each of 20a is changed. Thereby, the condensation temperature difference ⁇ CT is reduced.
  • the amount of decrease in the condensation temperature CT1 in step S09A and the amount of increase in the condensation temperature CT2 in step S10A can be, for example, a magnitude obtained by distributing the condensation temperature difference ⁇ CT by the ratio of the operating capacities of the compressors 10a and 20a.
  • both the increase amount and the decrease amount can be set to a size obtained by multiplying the condensation temperature difference ⁇ CT by a predetermined ratio (for example, about 30%).
  • step S11 When an operation for reducing the condensing temperature difference ⁇ CT is performed in steps S07A to S10A, the process proceeds to step S11, and it is determined whether or not the operating state has been changed for either the air conditioner 1 or the ventilator 2. Is done. Specifically, when the set temperature, the set air volume, or the like is changed in either the air conditioner 1 or the ventilator 2 (YES in S11), it is determined that the condensation temperature difference control cannot be continued. The Therefore, the air conditioning system 100 transitions from cooperative control to normal control.
  • step S12 the indoor temperature T deviation ⁇ 1 with respect to the target indoor temperature T * is within a predetermined range ( ⁇ E It is determined whether or not the temperature is within (° C).
  • the process returns to step S05A to continue the condensation temperature difference control.

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

Abstract

Selon l'invention, un premier dispositif de climatisation (1) comprend un premier circuit de fluide frigorigène et alimente en air un espace intérieur. Un second dispositif de climatisation (2) comprend un second circuit de fluide frigorigène et alimente en air l'espace intérieur. Un dispositif de commande (30) commande les premier et second dispositifs de climatisation (1, 2). Les premier et second circuits de fluide frigorigène comprennent chacun un compresseur, un condenseur, un détendeur et un évaporateur, chacun étant conçu de sorte qu'un fluide frigorigène circule, dans l'ordre, à travers le compresseur, le condenseur, le détendeur et l'évaporateur. Pendant le fonctionnement de refroidissement des premier et second dispositifs de climatisation (1, 2), lorsqu'une première température d'évaporation de fluide frigorigène du premier circuit de fluide frigorigène est supérieure à une seconde température d'évaporation de fluide frigorigène du second circuit de fluide frigorigène, le dispositif de commande (30) diminue la différence entre la première température d'évaporation de fluide frigorigène et la seconde température d'évaporation de fluide frigorigène au moyen de l'augmentation de la fréquence de fonctionnement du compresseur dans le premier circuit de fluide frigorigène et de la diminution de la fréquence de fonctionnement du compresseur dans le second circuit de fluide frigorigène.
PCT/JP2016/066616 2016-06-03 2016-06-03 Système de climatisation WO2017208438A1 (fr)

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JP2019163907A (ja) * 2018-03-20 2019-09-26 三菱電機株式会社 空気調和装置及び空気調和システム
JP6739671B1 (ja) * 2019-08-19 2020-08-12 三菱電機株式会社 情報処理装置

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CN112594796B (zh) * 2020-11-27 2022-07-19 重庆海尔空调器有限公司 用于空调出风控制的方法、装置及空调

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JPH0245260A (ja) * 1988-08-05 1990-02-15 Hitachi Ltd 車両用空調装置の制御方法
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JP2019163907A (ja) * 2018-03-20 2019-09-26 三菱電機株式会社 空気調和装置及び空気調和システム
JP7316759B2 (ja) 2018-03-20 2023-07-28 三菱電機株式会社 空気調和装置及び空気調和システム
JP6739671B1 (ja) * 2019-08-19 2020-08-12 三菱電機株式会社 情報処理装置
WO2021033231A1 (fr) * 2019-08-19 2021-02-25 三菱電機株式会社 Dispositif de traitement d'informations

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