WO2018211612A1 - Dispositif de climatisation - Google Patents

Dispositif de climatisation Download PDF

Info

Publication number
WO2018211612A1
WO2018211612A1 PCT/JP2017/018463 JP2017018463W WO2018211612A1 WO 2018211612 A1 WO2018211612 A1 WO 2018211612A1 JP 2017018463 W JP2017018463 W JP 2017018463W WO 2018211612 A1 WO2018211612 A1 WO 2018211612A1
Authority
WO
WIPO (PCT)
Prior art keywords
air
fan
compressor
operating frequency
air volume
Prior art date
Application number
PCT/JP2017/018463
Other languages
English (en)
Japanese (ja)
Inventor
一平 篠田
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2017/018463 priority Critical patent/WO2018211612A1/fr
Publication of WO2018211612A1 publication Critical patent/WO2018211612A1/fr

Links

Images

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
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits

Definitions

  • the present invention relates to an air conditioner having an evaporator and a fan for supplying air in an air-conditioned space to the evaporator.
  • the air conditioner installed in the data center mainly performs cooling operation, and most of the cooling load is sensible heat load.
  • the indoor temperature and humidity be adjusted to be constant. If the air conditioner performs cooling operation and excessively dehumidifies the room, it must be humidified, and on the other hand, extra energy is consumed. Therefore, the data center is required to have high sensible heat cooling that suppresses latent heat treatment and preferentially performs sensible heat treatment.
  • the air conditioner when performing high sensible heat cooling, the air conditioner must increase the air volume of the fan on the evaporator side, and the energy is low under a load with a sufficiently high sensible heat ratio and a low cooling load. It will be wasted.
  • an air conditioning system that controls the evaporation temperature to be equal to or higher than the dew point temperature by lowering the air volume of the fan on the evaporator side with the dew point temperature as a target with respect to the dry bulb temperature of the air in the air conditioning target space (for example, Patent Document 1).
  • an air-conditioning indoor unit is disclosed that determines a lower limit value of the rotation speed of a fan of an indoor unit based on an evaporation temperature when cooling indoor air (see, for example, Patent Document 2).
  • the present invention has been made to solve the above-described problems, and provides an air conditioner that saves energy while preventing the occurrence of condensation in an evaporator.
  • An air conditioner includes a refrigerant circuit in which a compressor, a condenser, an expansion device, and an evaporator are connected in order through a refrigerant pipe, a fan that supplies air sucked from a space to be conditioned to the evaporator, A dry bulb temperature sensor that measures the dry bulb temperature of the air in the air-conditioned space, an evaporation temperature sensor that measures the evaporation temperature in the evaporator, and an operating frequency of the compressor so that the dry bulb temperature becomes a set temperature. And a controller that controls the air volume of the fan, and the controller controls the air volume of the fan when the operating frequency is equal to or lower than a set value and the evaporation temperature is higher than a dew point temperature. It is controlled according to the size of.
  • the cooling capacity it is determined whether or not the cooling capacity can be lowered based on the operating frequency of the compressor that operates corresponding to the dry bulb temperature of the air-conditioning target space, and the compressor is maintained while the evaporation temperature is maintained higher than the dew point temperature. Since the air volume of the fan is controlled according to the operating frequency, it is possible to prevent the occurrence of dew condensation in the evaporator and to reduce the energy consumption.
  • FIG. 1 is a refrigerant circuit diagram illustrating a configuration example of the air-conditioning apparatus according to Embodiment 1 of the present invention.
  • the air conditioner 1 includes a heat source side unit 10 and a load side unit 20.
  • the load side unit 20 is installed in the air conditioning target space.
  • the heat source side unit 10 includes a compressor 11 that compresses and discharges the refrigerant, and a condenser 12 that exchanges heat between the refrigerant and the outside air.
  • the load-side unit 20 includes an expansion device 21 that expands the flowing refrigerant, an evaporator 22 that exchanges heat between the flowing refrigerant and the air in the air conditioning target space, and an evaporator 22 that sucks air from the air conditioning target space. And a fan 23 to be supplied.
  • the load unit 20 is provided with a dry bulb temperature sensor 25 that measures the dry bulb temperature of the air sucked from the air-conditioning target space.
  • An evaporation temperature sensor 24 for measuring the evaporation temperature is provided on the refrigerant outlet side of the evaporator 22.
  • the compressor 11, the condenser 12, the expansion device 21 and the evaporator 22 are connected in order by refrigerant piping, and the refrigerant circuit 30 is configured.
  • the heat source unit 10 is provided with a controller 15 that controls the compressor 11, the expansion device 21, and the fan 23.
  • the compressor 11 is a variable capacity compressor.
  • the control unit 15 is connected to the compressor 11, the expansion device 21, the fan 23, the evaporation temperature sensor 24, and the dry bulb temperature sensor 25 via signal lines.
  • FIG. 2 is a diagram illustrating a configuration example of the control unit illustrated in FIG.
  • the control unit 15 is, for example, a microcomputer.
  • the control unit 15 includes a memory 151 that stores a program, and a CPU (Central Processing Unit) 152 that executes processing according to the program.
  • the memory 151 stores set temperature and target relative humidity input by the user.
  • the memory 151 stores a maximum value of the capacity of the compressor 11 and a maximum value of the rotational speed of the fan 23.
  • the memory 151 stores a table showing a correspondence relationship with the lower limit value of the air volume of the fan 23 corresponding to the capacity of the compressor 11. This table is used for fan airflow suppression control in the first embodiment.
  • the control unit 15 controls the capacity of the compressor 11 and the opening degree of the expansion device 21 so that the dry bulb temperature measured by the dry bulb temperature sensor 25 approaches the set temperature.
  • the control unit 15 controls the operating frequency as the capacity control of the compressor 11
  • the control unit 15 controls the air volume of the fan 23 based on the dry bulb temperature of the air-conditioning target space, the evaporation temperature, and the operating frequency of the compressor 11. Details of the control executed by the control unit 15 will be described later.
  • control unit 15 is provided in the heat source side unit 10 is illustrated in FIG. 1, it may be provided in the load side unit 20.
  • a fan that blows outside air may be provided in the condenser 12.
  • the air conditioning apparatus 1 may be an apparatus that can perform not only cooling operation but also heating operation.
  • control part 15 demonstrated in the case of acquiring evaporation temperature from the evaporation temperature sensor 24 provided in the refrigerant
  • FIG. 3 is a flowchart showing a control procedure executed by the air-conditioning apparatus according to Embodiment 1 of the present invention.
  • FIG. 4 is a table showing the correspondence relationship with the lower limit value of the air flow rate of the fan on the evaporator side corresponding to the capacity of the compressor in the control procedure shown in FIG.
  • the air volume lower limit value% shown in FIG. 4 means the ratio of the lower limit value of the rotational speed to the maximum value of the rotational speed of the fan 23.
  • the operating frequency range of the compressor 11 is associated with the lower limit value of the fan 23 so that the lower limit value of the fan 23 becomes smaller as the operating frequency of the compressor 11 becomes smaller.
  • the minimum and maximum values of the operating frequency range at each stage serve as a threshold for whether or not to change the stage.
  • step S2 when the operation frequency of the compressor 11 is 75% or less of the maximum value as a result of the determination in step S2, the control unit 15 acquires the value of the dry bulb temperature of the air-conditioning target space from the dry bulb temperature sensor 25 ( In step S4), the set temperature is read (step S5), and the magnitudes of these temperatures are compared (step S6). As a result of the determination, when the condition of set temperature + 1 ° C. ⁇ dry bulb temperature is satisfied, the control unit 15 determines that the cooling capacity is insufficient. In this case, the control unit 15 sets the air volume of the fan 23 on the evaporator 22 side to 100% (step S3).
  • step S6 when the relationship of the set temperature + 1 ° C.> the dry bulb temperature is satisfied, the control unit 15 determines that the cooling capacity has a surplus capacity.
  • the control unit 15 reads the target relative humidity (step S7), and calculates a virtual dew point temperature from the dry bulb temperature and the target relative humidity (step S8).
  • step S6 when the relationship of set temperature + 1 ° C.> dry bulb temperature is satisfied, it is considered that the relative humidity of the air-conditioning target space approximates the target relative humidity.
  • the control unit 15 can calculate the dew point temperature from the target relative humidity and the dry bulb temperature based on the air diagram data stored in advance in the memory 151.
  • control unit 15 acquires the value of the evaporation temperature from the evaporation temperature sensor 24 (step S9). And the control part 15 compares the magnitude
  • step S10 when the relationship of evaporation temperature + 2 ° C.> dew point temperature is satisfied, the control unit 15 determines whether or not the operating frequency of the compressor 11 exceeds 50% of the maximum value. (Step S11). When the operating frequency exceeds 50% of the maximum value, the control unit 15 performs control to lower the rotational speed of the fan 23 by setting the lower limit value of the air volume of the fan 23 to 69% of the maximum value. Specifically, the control unit 15 determines whether or not the air volume of the fan 23 is larger than 69% of the maximum value (step S12). When the air flow rate of the fan 23 is larger than 69% of the maximum value, the control unit 15 refers to the table shown in FIG.
  • step S13 If is less than 69% of the maximum value, the air flow stage is maintained.
  • the operating frequency during operation is 75% or less of the maximum value, if the air volume of the fan 23 is 69% or more of the maximum value, it is the air volume that can perform high sensible heat cooling.
  • the controller 15 may reduce the rotational speed of the fan 23 according to a predetermined table when decreasing the air volume of the fan 23, or may decrease the rotational speed at a minimum controllable interval such as 1 Hz and 1 rpm.
  • step S11 If it is determined in step S11 that the operating frequency of the compressor 11 is 50% or less of the maximum value, the control unit 15 sets the lower limit value of the air volume of the fan 23 to 43% of the maximum value and decreases the rotational speed of the fan 23. Take control. Specifically, the control unit 15 determines whether or not the air volume of the fan 23 is larger than 43% of the maximum value (step S14). When the air volume is larger than 43% of the maximum value, the control unit 15 reduces the air volume level of the fan 23 by one level (step S15). When the operation frequency is 43% or less of the maximum value, the air volume level of the fan 23 is decreased. To maintain.
  • step S10 determines whether the condition of evaporation temperature + 2 ° C.> dew point temperature is not satisfied. If it is determined in step S10 that the condition of evaporation temperature + 2 ° C.> dew point temperature is not satisfied, the control unit 15 performs control to increase the rotational speed of the fan 23. In the control shown in FIG. 3, the control unit 15 performs control to increase the air volume of the fan 23 by one level (step S16).
  • the control unit 15 determines whether or not the end of the fan airflow suppression control is input from the user (step S17). If the end instruction is not input, the control unit 15 again performs step S1. Return to.
  • the control unit 15 monitors the operating frequency of the compressor 11 during operation, and repeats the determination of whether to increase or decrease the air volume of the fan 23 or to maintain the current state. This repetition is desirably performed in the same cycle as the operation frequency control cycle of the compressor 11. This repetition is preferably performed at intervals of 30 seconds, for example.
  • step S17 when the end of the fan air volume suppression control is input from the user, the control unit 15 sets the air volume of the fan 23 to 100% (step S18).
  • + 1 ° C. in the determination condition (set temperature + 1 ° C. ⁇ dry bulb temperature) in step S6 shown in FIG. 3 is a correction value.
  • the determination condition in step S6 is not limited to this condition, and it is desirable to use a determination value that changes from thermo-off to thermo-on in the refrigeration cycle control in the air conditioner 1.
  • the set temperature correction value is preferably set to + 1 ° C., for example.
  • the condition that changes from thermo-off to thermo-on is a condition that requires cooling capacity.
  • + 2 ° C. in the determination condition (evaporation temperature + 2 ° C.> dew point temperature) in step S10 shown in FIG. 3 is a correction value.
  • the correction value in the determination condition of step S10 serves as a threshold value for determining whether or not drainage is generated by a large-sized evaporator, and the value is preferably + 2 ° C.
  • a correction value may not be provided for the determination condition in step S10.
  • the control method described with reference to FIG. 3 is summarized.
  • the control unit 15 controls the operating frequency of the compressor 11 so that the dry bulb temperature of the air-conditioning target space becomes the set temperature. In this control, all heat treatment including sensible heat treatment and latent heat treatment is performed.
  • the control unit 15 sets the operating frequency of the compressor 11 to a large value such as a maximum value.
  • the control unit 15 performs control to lower the operating frequency of the compressor 11 in order to prevent overshooting.
  • the control unit 15 When the operating frequency is a value smaller than the maximum value and lower than a set value (for example, 75%), the dry bulb temperature becomes substantially the same as the set temperature, and the latent heat treatment is considered sufficient. Under this situation, the control unit 15 performs high sensible heat cooling that suppresses latent heat treatment and prioritizes sensible heat treatment. However, the control unit 15 controls the air volume of the fan 23 in accordance with the operation frequency of the compressor 11 so that the sensible heat treatment does not become excessive. If the temperature obtained by adding the correction value (+ 2 ° C.) to the evaporation temperature is higher than the dew point temperature in the determination in step S ⁇ b> 10, the control unit 15 controls the air volume of the fan 23 according to the operating frequency of the compressor 11. The fan air volume is determined according to the operating frequency. In accordance with the table shown in FIG. 4, the control unit 15 decreases the air volume of the fan 23 as the operating frequency of the compressor 11 decreases.
  • the control unit 15 increases the air volume of the fan 23 and decreases the evaporation temperature.
  • the dew point temperature that the control unit 15 compares with the temperature obtained by adding the correction value to the evaporation temperature is a virtually calculated value.
  • the control unit 15 adds the operation frequency described with reference to FIG. 3 to the average value of the total operation frequency obtained by summing the operation frequencies of the plurality of compressors 11. It is sufficient to control by replacing with. For example, consider a case where the air conditioner has three heat source side units 10 and the operating frequencies of the three compressors 11 are 95%, 90%, and 85% of the maximum value in step S2.
  • step S2 the control unit 15 may compare the average value 90% of the total operating frequencies of these operating frequencies with the set value 75%.
  • the control method described in the first embodiment is also applied to an air conditioner in which a plurality of heat source side units 10 are connected to a load side unit 20 provided with a large size evaporator, such as a data center. Can do.
  • the control method described in the first embodiment it is difficult to apply the control method described in the first embodiment to an air conditioner having a plurality of load-side units 20.
  • the load side unit 20 is multi (multiple units)
  • the total capacity of the compressor 11 in operation and the cooling capacity required by one load side unit 20 out of the plurality of load side units 20 are: This is because they do not necessarily match. For example, even if the total capacity during operation is 50%, if one unit on the load side 20 requires 100% cooling capacity, the fan speed should be reduced to maintain high sensible cooling. is not.
  • the air conditioner 1 includes a refrigerant circuit 30 in which a compressor 11, a condenser 12, an expansion device 21, and an evaporator 22 are connected in order through a refrigerant pipe, and an air sucked from an air-conditioning target space.
  • the fan 23 supplied to the air, the dry bulb temperature sensor 25 for measuring the dry bulb temperature of the air in the air-conditioning target space, the evaporation temperature sensor 24 for measuring the evaporation temperature in the evaporator 22, and the dry bulb temperature to be the set temperature.
  • the control unit 15 controls the operation frequency of the compressor 11 and the air volume of the fan 23, and the control unit 15 has a case where the operation frequency of the compressor 11 is equal to or lower than a set value and the evaporation temperature is higher than the dew point temperature.
  • the air volume of the fan 23 is controlled according to the operating frequency of the compressor 11.
  • the control unit 15 determines whether or not the cooling capacity can be lowered based on the operation frequency of the compressor 11 that operates corresponding to the dry bulb temperature of the air-conditioning target space, and the evaporation temperature is
  • the air volume of the fan 23 is controlled according to the operating frequency of the compressor 11 while maintaining a state higher than the dew point temperature. In this case, it can be suppressed that the cooling capacity is insufficient and the output of the compressor is increased or the fan air volume is increased again. Therefore, it is possible to prevent the occurrence of dew condensation in the evaporator 22 and suppress the energy consumption of the fan 23 to save energy.
  • the control unit 15 is based on the operating frequency of the compressor 11 and the dry bulb temperature in the air-conditioning target space as a premise for performing the air volume suppression control of the fan 23. In addition, it is determined whether or not the cooling capacity is sufficient and whether or not the air volume suppression control of the fan 23 may be performed. As a result, when it is determined that the cooling capacity is insufficient, the control unit 15 maintains the operation frequency of the compressor 11 and does not shift to the air volume suppression control of the fan 23. Therefore, even in an air-conditioning target space where the temperature management is strict such as a data center, the air-conditioning apparatus 1 according to the first embodiment can quickly exhibit the cooling capability when the cooling capability is required.
  • the control unit 15 determines the range of the operating frequency and the lower limit value of the air volume of the fan 23 so that the lower limit value of the air volume of the fan 23 decreases as the operating frequency of the compressor 11 decreases. It holds tables that are associated and set in multiple stages. And the control part 15 controls the air volume of the fan 23 using the lower limit value of the air volume of the fan 23 set to the stage of the range to which the operating frequency of the compressor under operation belongs among a plurality of stages. In this case, when the operating frequency of the compressor 11 decreases, the air volume of the fan 23 is controlled to decrease. For this reason, it is possible to suppress the cooling capacity from becoming excessive and to reduce the energy consumption of the fan 23.
  • the control unit 15 determines whether or not the range to which the operating frequency belongs before and after the change, and before and after the change. If the range to which the operating frequency belongs does not change, the stage used for controlling the air volume of the fan 23 does not change. If the change in the operating frequency of the compressor 11 is within the range set in the table shown in FIG. 4, the control unit 15 does not change the lower limit value of the air volume of the fan 23. As a result, the air volume range of the fan 23 is prevented from being frequently changed, and a hunting phenomenon in which the temperature swings up and down can be prevented.
  • the heat source side unit 10 containing the compressor 11 and the condenser 12 is provided with two or more, and the control part 15 sets the average value of the sum total of the operating frequency of the several compressor 11 to one unit
  • the air volume of the fan 23 may be controlled.
  • the temperature of the air-conditioning target space can be reduced. Hunting phenomenon can be suppressed.
  • Embodiment 2 FIG. In the first embodiment, a case has been described in which the plurality of stages in which the capacity of the compressor 11 and the air volume lower limit value of the fan 23 are associated with each other are three stages. In the second embodiment, the stage is increased by one stage compared to the first embodiment.
  • the control unit 15 holds the table shown in FIG. 4 in the memory 151 as an initial stage.
  • the control unit 15 changes the interval between the steps according to the instruction. For example, when an instruction to increase the number of steps is input, the control unit 15 changes the number of steps from the three steps described in the first embodiment to four steps, and updates the table stored in the memory 151.
  • step S2 the determination reference value in step S2 is different. Further, in FIG. 5, there are four stages of air volume control of the fan 23, and steps S101 to S103 are added. In the second embodiment, processing different from the processing described with reference to FIG. 3 will be described in detail, and detailed description of processing similar to the processing described with reference to FIG. 3 will be omitted.
  • step S2 shown in FIG. 5 the control unit 15 determines whether or not the operating frequency of the compressor 11 during operation exceeds a set value (step S2).
  • the set value is 88% of the maximum value.
  • the control unit 15 proceeds to the process in step S4.
  • step S10 the control unit 15 determines whether or not the relationship of evaporation temperature + 2 ° C.> dew point temperature exists. If it is determined in step S10 that evaporation temperature + 2 ° C.> dew point temperature, the control unit 15 determines whether the operating frequency of the compressor 11 exceeds 75% of the maximum value (step S101). When the operating frequency is 75% or less of the maximum value, the control unit 15 proceeds to the process of step S11.
  • step S102 determines whether or not the air volume of the fan 23 is larger than 85% of the maximum value.
  • step S102 determines whether or not the air volume of the fan 23 is larger than 85% of the maximum value.
  • the control unit 15 lowers the air volume level by one level (step S103), and when the air volume of the fan 23 is 85% or less of the maximum value, the air volume level is decreased. maintain.
  • the operating frequency during operation is 88% or less of the maximum value, if the air volume of the fan 23 is 69% or more of the maximum value, the air volume can be high sensible heat cooling.
  • the air conditioner 1 maintains a table in which the operation frequency of the compressor 11 and the lower limit value of the air volume of the fan 23 are associated with each other, and changes the number of stages. When an instruction is input, the number of steps is changed in accordance with the instruction, and the held table is updated.
  • the interval between the steps of associating the operation frequency of the compressor 11 and the air volume lower limit value of the fan 23 can be set finely.
  • the control method described in the second embodiment may be applied to an air conditioner having a plurality of heat source side units 10.

Abstract

Ce dispositif de climatisation comprend: un circuit de fluide frigorigène, dans lequel un compresseur, un condenseur, un dispositif d'expansion et un évaporateur sont connectés dans cet ordre à l'aide d'un tuyau de fluide frigorigène; un ventilateur qui alimente l'évaporateur avec un air aspiré à partir d'un espace à climatiser; un capteur de température de thermomètre sec qui mesure la température de thermomètre sec de l'air dans l'espace à climatiser; un capteur de température d'évaporation qui mesure la température d'évaporation de l'évaporateur; et une unité de commande qui commande la fréquence de fonctionnement du compresseur et le volume d'air du ventilateur de sorte que la température de thermomètre sec soit une température définie. Dans les cas où la fréquence de fonctionnement du compresseur est égale à une valeur définie ou inférieure, et la température d'évaporation est supérieure à une température du point de rosée, l'unité de commande commande le volume d'air du ventilateur en fonction de l'amplitude de la fréquence de fonctionnement du compresseur.
PCT/JP2017/018463 2017-05-17 2017-05-17 Dispositif de climatisation WO2018211612A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2017/018463 WO2018211612A1 (fr) 2017-05-17 2017-05-17 Dispositif de climatisation

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2017/018463 WO2018211612A1 (fr) 2017-05-17 2017-05-17 Dispositif de climatisation

Publications (1)

Publication Number Publication Date
WO2018211612A1 true WO2018211612A1 (fr) 2018-11-22

Family

ID=64274063

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2017/018463 WO2018211612A1 (fr) 2017-05-17 2017-05-17 Dispositif de climatisation

Country Status (1)

Country Link
WO (1) WO2018211612A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113932365A (zh) * 2021-10-21 2022-01-14 合肥天鹅制冷科技有限公司 一种具有双换热器的八区分步式环控系统及其控制方法

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06307705A (ja) * 1993-04-20 1994-11-01 Toshiba Corp 空気調和機の湿度制御方法
JPH08285353A (ja) * 1995-04-07 1996-11-01 Toshiba Corp 空気調和装置
JPH1096545A (ja) * 1996-09-24 1998-04-14 N T T Facilities:Kk 空気調和機およびその制御方法
JP2002333186A (ja) * 1993-06-01 2002-11-22 Hitachi Ltd 空気調和機
JP2007040583A (ja) * 2005-08-02 2007-02-15 Ntt Facilities Inc 空気調和システムの除湿制御方法
JP2015001359A (ja) * 2013-06-18 2015-01-05 株式会社Ｎｔｔファシリティーズ 空調システムの無除湿制御方法
JP2015031419A (ja) * 2013-07-31 2015-02-16 三菱電機株式会社 空気調和機

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06307705A (ja) * 1993-04-20 1994-11-01 Toshiba Corp 空気調和機の湿度制御方法
JP2002333186A (ja) * 1993-06-01 2002-11-22 Hitachi Ltd 空気調和機
JPH08285353A (ja) * 1995-04-07 1996-11-01 Toshiba Corp 空気調和装置
JPH1096545A (ja) * 1996-09-24 1998-04-14 N T T Facilities:Kk 空気調和機およびその制御方法
JP2007040583A (ja) * 2005-08-02 2007-02-15 Ntt Facilities Inc 空気調和システムの除湿制御方法
JP2015001359A (ja) * 2013-06-18 2015-01-05 株式会社Ｎｔｔファシリティーズ 空調システムの無除湿制御方法
JP2015031419A (ja) * 2013-07-31 2015-02-16 三菱電機株式会社 空気調和機

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113932365A (zh) * 2021-10-21 2022-01-14 合肥天鹅制冷科技有限公司 一种具有双换热器的八区分步式环控系统及其控制方法
CN113932365B (zh) * 2021-10-21 2023-01-06 合肥天鹅制冷科技有限公司 一种具有双换热器的八区分步式环控系统及其控制方法

Similar Documents

Publication Publication Date Title
US11262092B2 (en) Air conditioning system including a ventilator that supplies humidified outdoor air
US8538587B2 (en) HVAC system with automated blower capacity dehumidification, a HVAC controller therefor and a method of operation thereof
WO2019153887A1 (fr) Procédé et dispositif de commande de système de climatisation, et système de climatisation associé
KR101171583B1 (ko) 공조 제어 방법 및 장치
JP5996107B2 (ja) 空気調和システム
US11879658B2 (en) Air-conditioning ventilation system
WO2015037434A1 (fr) Appareil de climatisation
US11306928B2 (en) Method and apparatus for re-heat circuit operation
JP2019168194A (ja) 外気処理ユニット
WO2023138059A1 (fr) Procédé de commande anti-condensation et système de commande pour climatiseur, dispositif électronique et support de stockage
WO2018164253A1 (fr) Dispositif de climatisation
JPH10259944A (ja) 空気調和システム
WO2018211612A1 (fr) Dispositif de climatisation
CN114930092A (zh) 空调系统控制装置、空调系统、空调系统控制方法以及程序
WO2020003490A1 (fr) Dispositif de climatisation
US11788739B2 (en) Method and apparatus for hybrid dehumidification
KR102558826B1 (ko) 공기 조화 시스템 및 제어 방법
JP2019011950A (ja) 空気調和機
JP6239100B2 (ja) 空気調和システム
JP2023019957A (ja) 空気調和機
JPH0694285A (ja) 空気調和装置
JP2015218986A (ja) 空気調和機
CN116294094A (zh) 一种末端空调器干湿分离运行的方法及一拖多空调系统
CN115419937A (zh) 一种地暖控制方法、控制装置和地暖
JP2021004702A (ja) 外気処理装置及び空調システム

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 17909951

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 17909951

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: JP