WO2014170982A1 - Dispositif de pompe à chaleur et système de climatisation - Google Patents

Dispositif de pompe à chaleur et système de climatisation Download PDF

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Publication number
WO2014170982A1
WO2014170982A1 PCT/JP2013/061467 JP2013061467W WO2014170982A1 WO 2014170982 A1 WO2014170982 A1 WO 2014170982A1 JP 2013061467 W JP2013061467 W JP 2013061467W WO 2014170982 A1 WO2014170982 A1 WO 2014170982A1
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Prior art keywords
temperature
difference
evaporator
average
corrected
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PCT/JP2013/061467
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English (en)
Japanese (ja)
Inventor
守 濱田
畝崎　史武
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三菱電機株式会社
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Priority to GB1519215.6A priority Critical patent/GB2528213B/en
Priority to PCT/JP2013/061467 priority patent/WO2014170982A1/fr
Priority to JP2015512243A priority patent/JP6072901B2/ja
Publication of WO2014170982A1 publication Critical patent/WO2014170982A1/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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • 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
    • F25B2347/00—Details for preventing or removing deposits or corrosion
    • F25B2347/02—Details of defrosting cycles
    • F25B2347/023—Set point defrosting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet 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
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator

Definitions

  • This invention relates to a heat pump device capable of defrosting operation. In particular, it relates to the determination to start the defrosting operation.
  • a heat pump device that can perform a defrosting operation for dissolving frost attached to an evaporator.
  • a heat pump device in which the start timing of the defrost operation is determined so that the one-cycle average COP (performance coefficient, operation efficiency) from the start of the heating operation to the end of the defrost operation is maximized” has been proposed.
  • the heat pump device calculates a current COP and a one-cycle COP based on the refrigerant condensation temperature and the refrigerant evaporation temperature. When it is determined that the current COP is smaller than one cycle COP, the start of the defrosting operation is commanded.
  • the COP is estimated and calculated using the refrigerant condensation temperature and the refrigerant evaporation temperature.
  • the compressor frequency, the air temperature, or the like changes, at least one of the refrigerant condensing temperature and the evaporation temperature changes, and the COP also changes accordingly.
  • the calculated COP decreases even though the evaporator is not frosted, it may be determined that it is the start timing of the defrosting operation.
  • This invention was made in order to solve the said subject, and it aims at providing the heat pump apparatus which can determine the defrost start more correctly.
  • a heat pump device includes a compressor, a condenser, an expansion device, and an evaporator connected to form a refrigerant circuit, and a condenser that detects a saturation temperature of the condenser as a condensation temperature.
  • the temperature detection means for detecting the saturation temperature of the evaporator as the evaporation temperature, and the average from the start of operation to the end of the defrost based on the condensation temperature and the evaporation temperature
  • a heat pump device includes a control device that performs a process of calculating at least the operating efficiency and determining the start of defrosting of the evaporator based on the calculated average operating efficiency.
  • the condensation temperature and the evaporation temperature are corrected, and the operation efficiency and the like are calculated based on the corrected condensation temperature and the corrected evaporation temperature. It is possible to accurately determine the start.
  • FIG. 1 shows schematic structure of the heat pump apparatus 100 concerning Embodiment 1 of this invention. It is a block diagram which shows the outline of the input-output relationship of the signal in the control system of the heat pump apparatus 100 concerning Embodiment 1 of this invention. It is a figure which shows the graph of the relationship between time and COP in Embodiment 1 of this invention. It is a figure which shows the graph of the relationship between the time in 1 cycle in Embodiment 1 of this invention, and COP. It is a figure which shows the flowchart of an example of the flow of the process regarding the defrost start determination control of the heat pump apparatus.
  • FIG. 1 is a diagram showing a schematic configuration of a heat pump apparatus 100 according to Embodiment 1 of the present invention.
  • the refrigerant circuit configuration and operation of the heat pump apparatus 100 will be described with reference to FIG.
  • the heat pump apparatus 100 is an apparatus such as a refrigeration apparatus that performs a cooling operation on a target space or an object by circulating a refrigerant, an air conditioning system that performs a cooling operation or a heating operation that heats an air-conditioning target space. is there.
  • it demonstrates as what is an air conditioning system as a representative.
  • the size relationship of each component may be different from the actual one.
  • FIG. 1 the size relationship of each component may be different from the actual one.
  • FIG. 1 the size relationship of each component may be different from the actual one.
  • the heat pump device 100 is configured by connecting a compressor 1, a condenser 2, an expansion device 3, and an evaporator 4 sequentially in series with a refrigerant pipe to constitute a heat pump circuit. Further, a condenser fan 5 and condensation temperature detection means 11 are provided in the vicinity of the condenser 2. An evaporator fan 6 and an evaporation temperature detecting means 12 are provided in the vicinity of the evaporator 4. The condensing temperature detecting means 11 and the evaporating temperature detecting means 12 detect the temperature, respectively, and send a signal including the detected temperature value (detected value) to the control device 50 for overall control of the heat pump device 100.
  • the compressor 1 sucks the refrigerant flowing through the refrigerant pipe, compresses the refrigerant, and discharges the refrigerant in a high temperature / high pressure state.
  • the condenser 2 performs heat exchange between the refrigerant and the fluid to condense the refrigerant.
  • the fluid is air.
  • the expansion device 3 decompresses and expands the refrigerant passing through the refrigerant pipe.
  • the expansion device 3 may be constituted by a throttle device such as an electronic expansion valve.
  • the evaporator 4 performs heat exchange between the refrigerant and air, and evaporates the refrigerant.
  • the condenser fan 5 supplies air to the condenser 2.
  • the evaporator fan 6 supplies air to the evaporator 4.
  • the condensation temperature detection means 11 is a detection device such as a temperature sensor that detects the saturation temperature (condensation temperature) of the condenser 2.
  • the evaporation temperature detection means 12 is a detection device such as a temperature sensor that detects the saturation temperature (evaporation temperature) of the evaporator 4.
  • the evaporator suction air temperature detection means 13 serving as the evaporator suction temperature detection means is a detection device such as a temperature sensor that detects the temperature of the air flowing into the evaporator 4 (evaporator suction air temperature).
  • the condenser suction air temperature detection means 14 serving as the condenser suction temperature detection means is a detection device such as a temperature sensor that detects the temperature of the fluid (air) flowing into the condenser 2 (condenser suction air temperature).
  • the compressor frequency detection means 15 is a device that detects the rotation frequency of the compressor (hereinafter referred to as the compressor frequency).
  • the control device 50 is composed of, for example, a microcomputer. For example, the rotational frequency of the compressor 1, the condenser fan 5 and the evaporation based on the detection values (condensation temperature detected by the condensation temperature detection means 11, evaporation temperature detected by the evaporation temperature detection means 12, etc.) from each detection means described above. Control is performed by determining the rotational speed of the fan 6 for equipment. For example, the opening degree of the expansion device 3 is controlled. Moreover, when changing the flow path of a refrigerant
  • the operation of the control device 50 according to the present embodiment will be described in detail later with reference to FIG.
  • the operation of the heat pump apparatus 100 will be briefly described based on the flow of the refrigerant.
  • the compressor 1 is first driven.
  • the high-temperature and high-pressure gas refrigerant compressed by the compressor 1 is discharged from the compressor 1 and flows into the condenser 2.
  • the condenser 2 the gas refrigerant that has flowed in is condensed while dissipating heat to the fluid to be heat exchanged, and becomes a low-temperature and high-pressure refrigerant.
  • This refrigerant flows out of the condenser 2, is decompressed by the expansion device 3, and becomes a gas-liquid two-phase refrigerant.
  • This gas-liquid two-phase refrigerant flows into the evaporator 4.
  • the refrigerant that has flowed into the evaporator 4 absorbs heat from the air, thereby evaporating. This refrigerant flows out of the evaporator 4 and is sucked into the compressor 1 again.
  • the condensation temperature detection means 11 and the evaporation temperature detection means 12 each detect the temperature and send a signal related to the detection value to the control device 50.
  • FIG. 2 is a block diagram schematically showing the input / output relationship of signals in the control system of the heat pump apparatus 100 according to Embodiment 1 of the present invention.
  • the control device 50 includes a memory 51 serving as a storage device and a calculation unit 52 that performs calculation processing based on the detection value.
  • the memory 51 stores, for example, detection values detected by the condensation temperature detection means 11, the evaporation temperature detection means 12, the evaporator intake air temperature detection means 13, the condenser intake air temperature detection means 14, and the compressor frequency detection means 15 as data.
  • the calculation unit 52 performs calculation processing based on the detection value stored in the memory 51.
  • the control device 50 sends signals to the compressor 1, the four-way valve (not shown), the expansion device 3, the condenser fan 5, and the evaporator fan 6 based on the calculation result in the calculation unit 52. To control.
  • Formula (1) is a definition formula of Carnot efficiency.
  • the power consumption is calculated by the condensation temperature Tc ⁇ evaporation temperature Te.
  • FIG. 3 is a diagram showing a graph of the relationship between time and COP in Embodiment 1 of the present invention. Based on FIG. 3, the relationship between the time of the heat pump apparatus 100 and the instantaneous COP will be described.
  • the horizontal axis represents time
  • the vertical axis represents COP.
  • the evaporation temperature Te decreases more than the condensation temperature Tc together with frost formation, and the decrease in the instantaneous COP due to frost formation can be accurately captured.
  • the instantaneous COP decreases with frost formation. Become.
  • FIG. 4 is a diagram showing a graph of the relationship between time and COP in one cycle in Embodiment 1 of the present invention.
  • the one-cycle average COP of the heat pump apparatus 100 will be described based on FIG.
  • the operation efficiency in the case of the operation accompanied by the defrosting operation is evaluated by the one-cycle average COP when the cycle from the start of the normal operation to the end of the defrosting operation is defined as one cycle as shown in FIG.
  • the defrosting operation does not contribute to the operation, the instantaneous COP becomes zero. Therefore, if the defrosting operation is started at a timing at which the one-cycle average COP becomes the highest, energy saving can be effectively realized, and therefore the start timing becomes important.
  • FIG. 5 is a flowchart illustrating an example of a flow of processing related to the defrosting start determination control of the heat pump device 100.
  • FIG. 6 is a graph showing a relationship between the instantaneous COP and the average COP in the first embodiment of the present invention.
  • FIG. 7 is a graph showing a relationship between the instantaneous COP and the one-cycle average COP in the first embodiment of the present invention.
  • FIG. 8 is a graph showing a relationship between the instantaneous COP and the average COP in Embodiment 1 of the present invention.
  • FIGS. 5 to 8 the flow of processing related to the defrosting start determination control of the heat pump apparatus 100 will be described.
  • the horizontal axis represents time
  • the vertical axis represents COP.
  • the process regarding the defrost start which the control apparatus 50 performs is demonstrated.
  • the control device 50 stores the condensation temperature Tc, which is a detection value detected by the condensation temperature detection unit 11, and the evaporation temperature Te, which is a detection value detected by the evaporation temperature detection unit 12, in the memory 51.
  • C1 on the right side of the above equation (2) takes into account the decrease in average COP due to the defrosting operation, as shown in FIG.
  • C1 since the optimal value changes with a defrost system, the specification of an apparatus, etc., you may set the value used as an optimal value each time without setting it as a constant.
  • the frequency of the compressor 1 is constant, the temperature of the air flowing into the evaporator 4 (evaporator suction temperature) is constant, and the temperature of the air flowing into the condenser 2 (condenser suction temperature) is It holds for the case where it is constant.
  • the frequency of the compressor 1, the temperature of the intake air of the evaporator 4 and the temperature of the intake air of the condenser 2 often change with time.
  • the condensation temperature Tc and the evaporation temperature Te change.
  • the frequency of the compressor 1 increases, the difference between the condensation temperature Tc and the evaporation temperature Te increases, and the instantaneous COP in the equation (1) decreases.
  • the temperature of the intake air of the condenser 2 rises, the condensation temperature Tc rises and the instantaneous COP of the equation (1) falls.
  • the evaporation temperature Te will fall and the instantaneous COP of Formula (1) will fall.
  • the corrected evaporation temperature and condensation temperature are calculated as follows. First, an evaporation temperature and a condensation temperature when operating at a predetermined reference compressor frequency F0, a reference evaporator suction air temperature Tae0, and a reference condenser suction air temperature Tac0 are set as a reference evaporation temperature Te0 and a reference condensation temperature Tc0. And
  • the compressor frequency detection means 15 detects the actual compressor frequency F. Further, the evaporator intake air temperature detecting means 13 detects the actual evaporator intake air temperature Tae. The condenser intake air temperature detection means 14 detects the actual condenser intake air temperature Tac. The evaporating temperature detecting means 12 detects the actual evaporating temperature Te. The condensation temperature detection means 11 detects the actual condensation temperature Tc.
  • the evaporating temperature when operating (heating operation) at the reference compressor frequency F0, the reference evaporator intake air temperature Tae0, and the reference condenser intake air temperature Tac0 in the current frosting state ( Correction evaporating temperature Te_mod) and condensing temperature (correcting condensing temperature Tc_mod) are corrected.
  • FIG. 9 is a diagram showing the relationship among the compressor frequency F, the evaporation temperature Te, and the condensation temperature Tc in the first embodiment of the present invention. Specifically, the evaporation temperature Te and the condensation temperature Tc are corrected according to the difference ⁇ F between the actual compressor frequency F and the reference compressor frequency F0. As shown in FIG. 9, when ⁇ F is positive, the condensation temperature Tc is decreased according to the absolute value of ⁇ F, and the evaporation temperature Te is corrected to be increased. On the contrary, when ⁇ F is negative, the condensation temperature Tc is increased according to the absolute value of ⁇ F, and the evaporation temperature Te is corrected to decrease.
  • condensation temperature Tc correction condensation temperature Tc_mod
  • evaporation temperature Te correction evaporation temperature Te_mod
  • FIG. 10 is a diagram showing the relationship between the evaporator intake air temperature Tae and the evaporation temperature Te in Embodiment 1 of the present invention. Further, the evaporation temperature Te is corrected according to the difference ⁇ Tae between the actual evaporator intake air temperature Tae and the reference evaporator intake air temperature Tae0. As shown in FIG. 10, when ⁇ Tae is positive, correction is made in a direction to lower the evaporation temperature Te according to the absolute value of ⁇ Tae. On the other hand, when ⁇ Tae is negative, correction is made to increase the evaporation temperature Te according to the absolute value of ⁇ Tae. By doing in this way, correction
  • FIG. 11 is a diagram showing a relationship between the condenser intake air temperature Tac and the condensation temperature Tc in the first embodiment of the present invention. Further, the condensation temperature Tc is corrected according to the difference ⁇ Tac between the actual condenser intake air temperature Tac and the reference condenser intake air temperature Tac0. As shown in FIG. 11, when ⁇ Tac is positive, correction is made in the direction of decreasing the condensation temperature Tc according to the absolute value of ⁇ Tac. On the contrary, when ⁇ Tac is negative, the condensation temperature Tc is corrected in accordance with the absolute value of ⁇ Tac. By doing so, the corrected condensing temperature Tc_mod when the condenser intake air temperature Tac is the reference condenser intake air temperature Tac0 at the present time can be calculated.
  • the actual condensing temperature Tc and the evaporation temperature Te are corrected based on the compressor frequency F, the evaporator intake air temperature Tae, and the condenser intake air temperature Tac.
  • the condensation temperature Tc can be corrected based on the compressor frequency F and corrected based on the condenser intake air temperature Tac.
  • the compressor frequency F and the condenser intake air temperature Tac are used. Make corrections that reflect both.
  • correction based on the condenser intake air temperature Tac may be performed, or correction may be performed in the reverse order.
  • the evaporation temperature Te can be corrected based on the compressor frequency F and corrected based on the evaporator intake air temperature Tae.
  • the compressor frequency F and the evaporator intake air are corrected. Correction that reflects both of the temperatures Tae is performed.
  • correction based on the compressor frequency F correction based on the evaporator intake air temperature Tae may be performed, or correction may be performed in the reverse order.
  • the instantaneous COP when operating at the reference compressor frequency F0, the reference evaporator intake air temperature Tae0, and the reference condenser intake air temperature Tac0 in the current frosting state is calculated based on the equation (4). can do.
  • the instantaneous COP shown in the equation (4) does not change depending on the compressor frequency F, the evaporator intake air temperature Tae, and the condenser intake air temperature Tac, and decreases only by frost formation. Therefore, the equations (2) to (4) Since the defrosting start timing is determined from the value calculated based on the above, the defrosting operation can be started at the optimum timing without erroneous determination. For this reason, 1-cycle average COP becomes high and can be connected to energy saving.
  • control apparatus 50 performs a defrost start determination process based on Formula (1) to Formula (3), it represents with following formula (5) from the compressor frequency F and the condensation temperature Tc.
  • the determination based on the instantaneous heating capability (instant capability) Qh to be performed is also performed.
  • FIG. 13 is a diagram showing a graph of the relationship between the instantaneous heating capacity and the one-cycle average heating capacity in the second embodiment of the present invention. Based on FIG. 13, the relationship between the time and the capability (heating capability) of the heat pump apparatus 100 will be described. In FIG. 13, the horizontal axis represents time, and the vertical axis represents ability. When the frosting phenomenon in the evaporator 4 proceeds, the amount of heat exchange in the evaporator 4 decreases due to an increase in ventilation resistance and an increase in thermal resistance, and the instantaneous heating capacity Qh decreases as shown in FIG.
  • the one-cycle average heating capacity Qh_CYCLE is expressed as in Expression (6) using the average heating capacity Qh_AVE from the start of normal operation to the present time.
  • C2 on the right side of the above equation (6) takes into account the decrease in the average heating capacity Qh_AVE due to the defrosting operation as shown in FIG.
  • FIG. 14 is a diagram showing temporal changes in the instantaneous COP and the heating capacity in the second embodiment of the present invention.
  • the horizontal axis represents time
  • the vertical axis represents COP and capability.
  • FIG. 16 is a diagram showing changes in instantaneous COP and heating capacity when the evaporator intake air temperature Tae in the second embodiment of the present invention changes.
  • the horizontal axis represents time
  • the vertical axis represents COP and capability.
  • the control device 50 determines that both the expression (3) and the following expression (7) When it is determined that it has been established, the defrosting operation is started.
  • FIG. 17 is a view showing a flowchart of an example of a flow of processing relating to defrosting start determination control of the heat pump apparatus 100 according to Embodiment 2 of the present invention.
  • the control device 50 is detected by the compressor frequency F detected by the compressor frequency detection means 15, the condensation temperature Tc detected by the condensation temperature detection means 11, and the evaporation temperature detection means 12.
  • Each value of the evaporation temperature Te is stored in the memory 51 (step S401).
  • the frosting phenomenon is the only factor that establishes the relationship of both equations (3) and (7) at the same time. Therefore, according to the heat pump device 100 of the present embodiment, the compressor frequency F, the evaporator suction air temperature Tae or the condenser suction is obtained by using the above formulas (3) and (7) for the defrosting start determination. Even when the air temperature Tac changes, the defrosting operation can be started at an optimal timing without erroneous determination, and energy saving can be achieved.
  • Embodiment 3 In said Embodiment 1 and Embodiment 2, you may make it perform the correction which changes C1 and C2 according to the last defrost driving
  • the reference defrosting operation time is determined in advance, and when the previous defrosting operation time is longer than the reference defrosting operation time, the correction is performed so that C1 in Expression (2) or C2 in Expression (6) is increased. To do.
  • the last defrosting operation time is shorter than the reference defrosting operation time, C1 in Expression (2) or C2 in Expression (6) is corrected to be reduced.
  • FIG. 19 is a diagram showing temporal changes in the instantaneous COP and the heating capacity in the third embodiment of the present invention.
  • the short defrosting time means that the decrease in COP and capacity due to the defrosting operation is too small and the heating operation time is too short.
  • C2 in Formula (6) is good to make small.

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  • Engineering & Computer Science (AREA)
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  • Mechanical Engineering (AREA)
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  • General Engineering & Computer Science (AREA)
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Abstract

La présente invention concerne un dispositif de pompe à chaleur dans lequel un circuit d'agent frigorigène est construit en reliant par des canalisations un compresseur (1), un condenseur (2), un dispositif (3) de détente et un évaporateur (4), le dispositif de pompe à chaleur comportant: un moyen (11) de détection de température de condensation qui détecte la température de saturation du condenseur (2) en tant que température de condensation; un moyen (12) de détection de température d'évaporation qui détecte la température de saturation de l'évaporateur (4) en tant que température d'évaporation; et un dispositif (50) de commande qui effectue un processus visant à calculer, sur la base de la température de condensation et de la température d'évaporation, au moins un rendement moyen de fonctionnement du début du fonctionnement à la fin du dégivrage en faisant l'hypothèse que le dégivrage est effectué à l'instant présent, et à déterminer le début du dégivrage de l'évaporateur sur la base du rendement moyen de fonctionnement calculé.
PCT/JP2013/061467 2013-04-18 2013-04-18 Dispositif de pompe à chaleur et système de climatisation WO2014170982A1 (fr)

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Application Number Priority Date Filing Date Title
GB1519215.6A GB2528213B (en) 2013-04-18 2013-04-18 Heat pump apparatus and air conditioning system
PCT/JP2013/061467 WO2014170982A1 (fr) 2013-04-18 2013-04-18 Dispositif de pompe à chaleur et système de climatisation
JP2015512243A JP6072901B2 (ja) 2013-04-18 2013-04-18 ヒートポンプ装置及び空気調和システム

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JP2019163869A (ja) * 2018-03-19 2019-09-26 三菱電機冷熱プラント株式会社 冷却装置とその制御方法および制御プログラム
WO2020145281A1 (fr) * 2019-01-08 2020-07-16 三菱電機株式会社 Système de réfrigération
JP2020112343A (ja) * 2019-01-08 2020-07-27 三菱電機株式会社 冷凍システム
US11709004B2 (en) 2020-12-16 2023-07-25 Lennox Industries Inc. Method and a system for preventing a freeze event using refrigerant temperature

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EP3222939B1 (fr) * 2016-03-23 2020-08-19 Honeywell spol s.r.o. Gestion du givre d'un évaporateur
US10458688B2 (en) 2017-03-22 2019-10-29 Honeywell International Inc. Frost management of an evaporator
US11131497B2 (en) * 2019-06-18 2021-09-28 Honeywell International Inc. Method and system for controlling the defrost cycle of a vapor compression system for increased energy efficiency
CN114413534B (zh) * 2022-01-11 2023-05-02 珠海格力电器股份有限公司 除霜控制方法、装置、设备、计算机设备及电子设备

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JP2010060150A (ja) * 2008-09-01 2010-03-18 Mitsubishi Electric Corp ヒートポンプ装置

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JPH05264089A (ja) * 1992-03-17 1993-10-12 Daikin Ind Ltd 冷凍装置の除霜運転制御装置
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JP2010060150A (ja) * 2008-09-01 2010-03-18 Mitsubishi Electric Corp ヒートポンプ装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019163869A (ja) * 2018-03-19 2019-09-26 三菱電機冷熱プラント株式会社 冷却装置とその制御方法および制御プログラム
JP7011766B2 (ja) 2018-03-19 2022-01-27 三菱電機冷熱プラント株式会社 冷却装置とその制御方法および制御プログラム
WO2020145281A1 (fr) * 2019-01-08 2020-07-16 三菱電機株式会社 Système de réfrigération
JP2020112343A (ja) * 2019-01-08 2020-07-27 三菱電機株式会社 冷凍システム
JP7433040B2 (ja) 2019-01-08 2024-02-19 三菱電機株式会社 冷凍システム
US11709004B2 (en) 2020-12-16 2023-07-25 Lennox Industries Inc. Method and a system for preventing a freeze event using refrigerant temperature

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JP6072901B2 (ja) 2017-02-01
GB201519215D0 (en) 2015-12-16
GB2528213A (en) 2016-01-13

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