WO2004083744A1 - Climatiseur - Google Patents

Climatiseur Download PDF

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Publication number
WO2004083744A1
WO2004083744A1 PCT/JP2004/003436 JP2004003436W WO2004083744A1 WO 2004083744 A1 WO2004083744 A1 WO 2004083744A1 JP 2004003436 W JP2004003436 W JP 2004003436W WO 2004083744 A1 WO2004083744 A1 WO 2004083744A1
Authority
WO
WIPO (PCT)
Prior art keywords
stop
speed
compressor
air conditioner
control
Prior art date
Application number
PCT/JP2004/003436
Other languages
English (en)
Japanese (ja)
Inventor
Yasushi Jinno
Yasushi Watanabe
Original Assignee
Matsushita Electric Industrial Co. Ltd.
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 Matsushita Electric Industrial Co. Ltd. filed Critical Matsushita Electric Industrial Co. Ltd.
Priority to JP2005503680A priority Critical patent/JP4265601B2/ja
Priority to KR1020047018229A priority patent/KR100590352B1/ko
Publication of WO2004083744A1 publication Critical patent/WO2004083744A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/025—Motor control arrangements
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/27—Problems to be solved characterised by the stop of the refrigeration 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/021—Inverters therefor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present invention relates to control of an air conditioner when a compressor is stopped.
  • the one-piston opening tally has a simple structure and can be manufactured at low cost, and has low mechanical loss. Therefore, there is an advantage that it is possible to design a high-performance and inexpensive air conditioner by driving it with a high-performance DC motor.
  • vibration is large due to speed fluctuation of the rotor caused by load fluctuation during one rotation of the rotor.
  • HFC refrigerants mainly R410A refrigerants
  • R410A refrigerants have become mainstream due to the necessity of using alternative refrigerants to protect the global environment.
  • ⁇ Since the pressure is higher than that of the refrigerant (R22 refrigerant), the speed fluctuation becomes remarkable, which is a factor of increasing vibration.
  • Japanese Patent Application Laid-Open No. 2001-37828 discloses that speed fluctuation is controlled by finely controlling an inverter output during one rotation of a compressor motor rotor. Disclosure of torque control type inverter control (hereinafter referred to as torque control inverter). Rotor speed fluctuations are detected during the torque control inver and the output of the rotor during one rotation of the rotor is adjusted to be constant, so the rotor speed is kept almost constant and compressor vibration is suppressed. Is done.
  • the piping design around the compressor must be made flexible and the vibration at stoppage should be absorbed by using a vibration-proof material such as a rubber member. This is a common method.
  • the piping was designed in a complicated shape using long piping, and a large number of vibration isolating materials were required, it was burdensome in terms of material costs and design man-hours. Therefore, as described in Japanese Patent Application Laid-Open No. 2001-37828, taking advantage of the advantage of torque control inverter that the rotor position of the compressor motor can be detected, the compressor at the time of stoppage is used.
  • a method to cut off the inverter power at the rotor position that is effective for suppressing vibration at stop according to the speed and the magnitude of the phase current, and a control to further suppress vibration at stop by applying brake output at stop A method is disclosed.
  • the optimal rotor stop position to suppress vibration at stop is mainly when the load on the compressor is the lightest, that is, when the mouth comes near immediately after the refrigerant gas is discharged. It is detected by a fluctuation in the output of the chamber during torque control.
  • An air conditioner according to the present invention is an air conditioner driven by a torque control member that suppresses speed fluctuation of a rotor of a compressor motor.
  • the compressor speed is controlled by torque control. After the compressor speed is changed to a value at which the control amount exceeds a certain value, the compressor is stopped at the optimum rotor position to suppress vibrations when stopping.
  • FIG. 1 is a diagram for explaining the output state of the torque control chamber when the torque control amount is large.
  • FIG. 2 is a diagram illustrating the output state of the torque control chamber when the torque control amount is small.
  • FIG. 3A is a configuration diagram of an air conditioner according to one embodiment of the present invention.
  • FIG. 3B is a configuration diagram of a control unit according to the embodiment of the present invention.
  • Figure 4 shows the relationship between compressor speed and torque control amount during torque control inversion.
  • FIG. 5 is a diagram showing a stop control tape A according to the embodiment of the present invention.
  • FIG. 6 is a flowchart of the control according to the embodiment of the present invention.
  • FIG. 7 is a diagram showing a time series of a series of operations of a flowchart according to the embodiment of the present invention.
  • FIG. 8 is a diagram showing a stop control table B according to one embodiment of the present invention.
  • FIG. 9A is a diagram showing a stop control table C according to one embodiment of the present invention.
  • FIG. 9B is a diagram showing a stop control table D according to one embodiment of the present invention.
  • FIG. 10 is a flowchart of control in one embodiment of the present invention.
  • FIG. 11 is a diagram showing a time series of a series of operations in a control flowchart according to the embodiment of the present invention.
  • FIG. 12 is a control flowchart according to the embodiment of the present invention.
  • FIG. 13 is a diagram showing a time series of a series of operations of a control flowchart according to the embodiment of the present invention.
  • FIG. 14 is a diagram showing a display example of an indoor unit operation lamp in one embodiment of the present invention.
  • FIG. 3A shows a configuration of an air conditioner according to an embodiment of the present invention.
  • a compressor 1 a pressure reducer 2, an indoor heat exchanger 3, an outdoor heat exchanger 4, and a four-way valve 10 are connected by piping as shown in Fig. 3A.
  • the compressor 1 has a driving motor, and the driving motor has a rotor.
  • the indoor heat exchanger 3 heat is exchanged by blowing air from the indoor blower 5, and the indoor heat exchanger 3 detects the heat exchanger temperature.
  • Indoor piping sensor 7 is installed.
  • the outdoor heat exchanger 4 performs heat exchange by blowing air from the outdoor blower 6, and the outdoor heat exchanger 4 is provided with an outdoor piping sensor 8 for detecting a heat exchanger temperature.
  • the compressor 1 is driven by an inverter 9 and the operation of the inverter 9 is controlled by a control unit 11.
  • the control unit 11 includes, for example, a microcomputer, and includes a speed detecting unit 11 1 and a stop position determining unit 1 12 as shown in FIG. 3B, and further includes a load amount determining unit 1 13 or a speed change ratio.
  • Variable means 1 14 can be provided.
  • FIG. 3B illustrates a case where the control unit 11 includes all of the means 1 1 1 1 1 1 2, 1 1 3 and 1 1 4. Of these, means 1 1 1 and means 1 1 2 are essential, but there are cases where the control unit 11 does not have the means 1 1 3 and the means 1 1 4 or has only one of them. Included in the present invention.
  • FIG. 4 is a diagram showing a relationship between the compressor speed and the torque control amount during the torque control impeller in the first embodiment of the present invention.
  • the torque control amount is constant at Ga% from the compressor speed 0 to fb, and the control amount is gradually decreased from the compressor speed f to fd, and fd
  • the torque control amount is set to G c%.
  • a torque control amount of G b% or more is required, and the compressor speed at that time is fc.
  • the stop speed is classified according to the operating speed when the stop instruction is issued. May be.
  • FIG. 5 is a stop control table A in the present embodiment. If the operator gives an instruction to stop while driving at a speed of fc or higher as shown in Fig. 4, the controller 11 sets the rotor speed to the stop speed fc, which is the upper limit of the speed at which the mouth can be accurately detected. After changing, it is determined that the stop is performed at the optimum rotor position) C for stopping at the speed fc.
  • the stop speed fc refers to a low speed at which the torque control amount at a time exceeds a predetermined value.
  • the control unit 11 changes the low-speed speed to the stop speed fa corresponding to the lowest speed at which stable operation is possible. Decision is made to stop at the optimum rotor position ⁇ a for stopping at speed fa.
  • the positions c c and c a can be set, for example, by experimentally finding the position of the rotor at which the vibration at the time of stop is the smallest when stopping under heavy load.
  • FIG. 6 is a flowchart of the control in the first embodiment.
  • the speed detecting means 111 detects the rotor rotation speed at the time of the stop instruction.
  • the stop position determining means 111 queries the stop control table A for the detected low rotation speed, and determines the stop speed fs of the compressor and the low speed corresponding to fs. One stop position ⁇ s is determined.
  • the control unit 11 starts changing the compressor speed toward the stop speed fs.
  • FIG. 7 shows a time series of a series of operations in this flowchart.
  • FIG. 8 shows a stop control table according to the second embodiment of the present invention.
  • the stop control table ⁇ is based on the stop control table ⁇ ⁇ ⁇ ⁇ in the first embodiment of the present invention.
  • the output of the pipe temperature sensor of the condensing-side heat exchanger when the compressor is stopped is added as a stop-and-stop position setting table.
  • the control unit 11 includes a load amount determination unit 113 in addition to the speed detection unit 111 and the stop position determination unit 112.
  • the load amount determining means 113 determines whether the load amount of the compressor is equal to or greater than a predetermined value.
  • the control unit 11 can set the port-evening stop position for stopping the compressor 1 to the optimum position based on the determination of the load amount determination unit 113.
  • the load determining means 113 determines the output of the pipe temperature sensor provided in the condensing-side heat exchanger when the compressor 1 is stopped.
  • the rotor stop position setting can be determined according to.
  • the pipe temperature sensor output is the output of the indoor pipe temperature sensor 7 during heating, and the output of the outdoor pipe temperature sensor 8 during cooling.
  • the compressor is stopped after changing to the speed of fc. I do.
  • the setting of the stop control table B of the second embodiment further refers to the condensation side pipe temperature Ts at the time of stop. That is, the load amount determining means 113 determines whether Ts is equal to or greater than Tc or less than Tc.
  • the control unit 11 stops the compressor at the optimal low-night stop position co c 1 corresponding to the load, and when T s is less than T c , The compressor can be stopped at the position of the optimum mouth-to-night stop position cc 2 corresponding to the load.
  • the setting of the stop control table B in the second embodiment refers to the condensation-side piping temperature Ts at the time of stop.
  • the load amount determination means 113 determines whether or not the third is greater than or equal to the third and less than Ta. If T s is equal to or greater than Ta, the control unit 11 stops at the position of the optimal mouth overnight stop position ⁇ a 1 corresponding to the load, and if T s is less than Ta, The stop is set so that the stop is performed at the position of the optimum mouth stop position ⁇ a2 corresponding to the load.
  • each rotor stop position ⁇ s can be set based on experimentally obtained data. You.
  • the pipe temperature detected by the sensor 7 or 8 is used as a means for determining the load, but it goes without saying that the present invention is not limited to this.
  • FIG. 9A shows a stop control table C according to the third embodiment of the present invention.
  • the stop control table C is based on the stop control table A described in the first embodiment, and further includes a compressor speed change ratio setting table.
  • the control unit 11 includes a speed change ratio varying unit 114 in addition to the speed detecting unit 111, the stop position determining unit 112, and the load amount determining unit 113.
  • the load amount determining means 1 1 3 detects the compressor load at the time when the stop instruction is issued, and the speed change ratio setting means sets the compressor speed to the stop speed according to the detected compressor load. Compressor speed change ratio can be set.
  • the speed change ratio setting means refers to the pipe temperature sensor output of the condensing-side heat exchanger as the compressor load. If the operator gives a stop instruction during operation at a speed of fc or higher as shown in Fig. 4, the compressor is stopped after changing to the stop speed fc in the setting of the stop control table A described in the first embodiment.
  • the pipe temperature Tk of the condensing-side heat exchanger at the time when the stop instruction is further issued is referred to.
  • the load amount determination means 113 determines whether Tk is equal to or greater than Tc or less than Tc. If it is less than Tc, the speed change ratio variable means 114 changes the speed to the stop speed at the normal compressor change speed ratio Rt. If it is higher than Tc, it is determined that the operation is under heavy load, and the speed change ratio variable means 1 1 4 changes the compressor change speed ratio more slowly than the normal compressor change speed ratio R. Speed change up to the stop speed can be performed with Rc.
  • the setting of the stop control table B of the third embodiment further refers to the condensation-side pipe temperature Tk when the stop instruction is issued.
  • the load amount determining means 1 13 determines whether Tk is equal to or greater than Ta or less than Ta. If Tk is less than Ta, the speed change ratio varying means 1 14 determines whether the normal compressor change speed ratio R t Change the speed up to the stop speed with. If it is equal to or greater than Ta, it is determined that the operation is under heavy load, and the speed change ratio variable means 1 1 4 is set to a compressor change speed that is slower than the normal compressor change speed ratio Rt. Change the speed up to the stop speed at the ratio Ra.
  • control may be performed based on a stop control table D shown in FIG. 9B.
  • the control unit 11 selects a stop position in consideration of the pipe temperature T k of the condensation-side heat exchanger. For example, if the stop speed is: f c and the pipe temperature is equal to or higher than T c, the stop position c c 1 is selected.
  • the compressor speed under a heavy load can be changed gently, and the torque control during that time can be stably performed.
  • the pipe temperature is used as a means for determining the load, but it goes without saying that the present invention is not limited to this.
  • FIG. 10 is a flowchart of control in Embodiment 4 of the present invention.
  • the stop control table according to the present embodiment uses the same stop control table A as that of the first embodiment, and a description thereof will be omitted.
  • the speed detecting means 111 detects the mouth rotation speed at the time of the stop instruction.
  • the stop position determining means 1 1 2 refers to the stop control table A for the detected rotation speed of the mouth and determines the stop speed fs of the compressor and the stop position ⁇ s of the compressor to stop. I do.
  • step 403 the change of the compressor speed is started toward the stop speed fs.
  • step 404 when the compressor speed reaches the stop speed fs set in step 402, At this point, the control unit 11 switches the four-way valve 10 in FIG. 3A. This balances the pressure of the air conditioner. Then, at the mouth stop position ⁇ s set in step 405, the power supply in the evening is cut off and the compressor is stopped.
  • Fig. 11 shows a series of operations of this flow chart in chronological order.
  • FIG. 12 is a flowchart of control in Embodiment 5 of the present invention.
  • the stop control table in the fifth embodiment uses the same stop control table as in the first embodiment, and a description thereof will be omitted.
  • the speed detecting means 111 detects the low speed rotation speed at the time of the stop instruction.
  • the stop position determining means 112 queries the stop control table A for the detected port rotation speed, and determines the compressor stop speed f s and the rotor stop position ⁇ s to stop.
  • step 503 at the same time as changing the compressor speed toward the stop speed, the control unit 11 stops the blower of the evaporating heat exchanger.
  • step 504 the controller 11 stops the blower of the condensing-side heat exchanger at the same time that the compressor speed reaches the stop speed f s set in step 502.
  • step 505 the power supply to the impeller is cut off at the mouth-evening stop position ⁇ s set in step 502, and the compressor is stopped.
  • FIG. 13 shows a time series of a series of operations in this flowchart.
  • the air conditioner does not absorb heat throughout the evaporator, while the condenser keeps radiating heat, reducing the load when the compressor is stopped and reducing the vibration when the compressor is stopped.
  • the change in the optimum rotor position due to the load is suppressed, and the stop control can be performed even with a small number of control parameters.
  • FIG. 14 shows a display example of the indoor unit operation lamp in the sixth embodiment of the present invention.
  • the indoor unit operation lamp is installed in the indoor unit and is set to light up when operating.
  • the control unit 11 controls the blinking operation of the operation lamp during the stop control, that is, from when the operator issues a stop instruction using the remote control until the compressor actually stops. For example, as shown in Fig. 14, the lighting operation for 2 seconds and the turning off for 1 second are taken as one cycle, and the blinking display operation is repeated, and the indoor unit is shown to the operator to indicate that the control operation for stopping is being performed. Control the running ramp.
  • this blinking display operation is performed from step 501 to step 505 in the control flowchart.
  • this blinking display operation is required for another purpose, it goes without saying that another display operation pattern may be set.
  • the person operating the air conditioner sent an operation stop instruction using the remote control, the compressor was running, and the internal and external blowers were operating, and a malfunction was detected. Misunderstandings can be prevented.
  • the rotor position can be reliably detected, and in any case, the compressor can be located at the position of the mouth and the night which is most suitable for suppressing vibration at the time of stop * noise. It is possible to stop. In addition, by reducing the moment of inertia of the mouth, it is possible to more effectively exhibit the effect of stopping vibration and noise. In addition, since the inertia of the mouth and the mouth becomes small, the change of the optimum position of the mouth and the mouth due to the compressor load at the time of stoppage can be suppressed as small as possible, and the control can be simplified. Furthermore, since the compressor speed at which the compressor stops can be limited, the change in the optimal rotor position due to the compressor speed at the time of the stop can be suppressed as small as possible, and the control can be simplified.
  • the present invention determines the rotor stop position of the compressor motor in accordance with the compressor load at the time of stop, so that even when the stop control is performed under various operating conditions, the vibration at the time of stop is more effective. Noise can be suppressed. For example, it is possible to gradually change the compressor speed at the time of heavy load, and to stably perform torque control during the change. Further, according to the present invention, the speed change ratio is changed according to the compressor load at the time of a stop instruction. By doing so, the operation during stop control can be performed stably even when a stop instruction is issued under various operating conditions.
  • the refrigerant pressure at the stop can be balanced, and the vibration and noise at the stop can be further reduced.
  • the blower of the condensing-side heat exchanger continues, and the blower of the evaporator-side heat exchanger is stopped.
  • the evaporator of the air conditioner does not absorb heat, while the condenser continues to radiate heat. The operation during control can be performed stably.
  • the present invention has a display unit for displaying to the indoor unit that the control operation for stopping is being performed.
  • a display portion a liquid crystal display device, an LED, an EL element, a light bulb, or the like can be used.
  • one position of the rotor can be reliably detected, so that it is possible to provide an air conditioner with less vibration and noise suppression at the time of stop.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Control Of Motors That Do Not Use Commutators (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

Dans un climatiseur entraîné par un inverseur de commande de couple destiné à limiter la variation de vitesse du rotor d'un moteur de compresseur, lorsqu'une instruction d'arrêt d'opérations est émise, une vitesse de compresseur est réglée sur une valeur pour laquelle une quantité de commande de couple est égale ou supérieure à une valeur prédéterminée. Le compresseur est ensuite arrêté dans une position de rotor appropriée pour contrôler les vibrations se produisant au moment de l'arrêt. En outre, on détermine une position de l'arrêt de rotor et un taux de changement de la vitesse de compresseur lors de la commande d'arrêt en fonction de la charge du compresseur.
PCT/JP2004/003436 2003-03-17 2004-03-15 Climatiseur WO2004083744A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2005503680A JP4265601B2 (ja) 2003-03-17 2004-03-15 空気調和機
KR1020047018229A KR100590352B1 (ko) 2003-03-17 2004-03-15 공기 조화기

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2003-071407 2003-03-17
JP2003071407 2003-03-17

Publications (1)

Publication Number Publication Date
WO2004083744A1 true WO2004083744A1 (fr) 2004-09-30

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PCT/JP2004/003436 WO2004083744A1 (fr) 2003-03-17 2004-03-15 Climatiseur

Country Status (4)

Country Link
JP (1) JP4265601B2 (fr)
KR (1) KR100590352B1 (fr)
CN (1) CN100412464C (fr)
WO (1) WO2004083744A1 (fr)

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WO2009048577A3 (fr) * 2007-10-08 2009-08-06 Emerson Climate Technologies Système et procédé de calcul de paramètres pour un système de réfrigération équipé d'un compresseur à vitesse variable
WO2009048579A3 (fr) * 2007-10-08 2009-08-06 Emerson Climate Technologies Système et procédé permettant d'étalonner des paramètres pour un système de réfrigération comportant un compresseur à vitesse variable
US7895003B2 (en) 2007-10-05 2011-02-22 Emerson Climate Technologies, Inc. Vibration protection in a variable speed compressor
US8448459B2 (en) 2007-10-08 2013-05-28 Emerson Climate Technologies, Inc. System and method for evaluating parameters for a refrigeration system with a variable speed compressor
US8459053B2 (en) 2007-10-08 2013-06-11 Emerson Climate Technologies, Inc. Variable speed compressor protection system and method
US8539786B2 (en) 2007-10-08 2013-09-24 Emerson Climate Technologies, Inc. System and method for monitoring overheat of a compressor
JP2013240274A (ja) * 2013-07-10 2013-11-28 Mitsubishi Electric Corp 交流直流変換装置、電動機駆動装置、圧縮機駆動装置、空気調和機、ヒートポンプ式給湯機
JP2014507589A (ja) * 2011-01-26 2014-03-27 ワールプール，ソシエダッド アノニマ 冷却用往復圧縮機制御システム及び方法
US8950206B2 (en) 2007-10-05 2015-02-10 Emerson Climate Technologies, Inc. Compressor assembly having electronics cooling system and method
JPWO2013114461A1 (ja) * 2012-02-02 2015-05-11 三菱電機株式会社 空気調和装置及び鉄道車両用空気調和装置
EP2789936A4 (fr) * 2011-12-06 2015-06-03 Panasonic Corp Réfrigérateur
WO2017022626A1 (fr) * 2015-07-31 2017-02-09 株式会社デンソー Dispositif de commande de compresseur électrique et dispositif à cycle frigorifique
WO2018114978A1 (fr) * 2016-12-19 2018-06-28 Nidec Global Appliance Germany Gmbh Dispositif de commande et procédé pour faire fonctionner un compresseur de fluide frigorigène
US20180195508A1 (en) * 2016-03-09 2018-07-12 Gd Midea Air-Conditioning Equipment Co., Ltd. Air conditioner, and method and device for controlling its compressor to stop
US20190072301A1 (en) * 2015-11-06 2019-03-07 Bsh Hausgeraete Gmbh Domestic refrigeration appliance with a coolant circuit and method for operating a domestic refrigeration appliance with a coolant circuit
EP3514458A4 (fr) * 2017-11-27 2020-01-01 Hitachi-Johnson Controls Air Conditioning, Inc. Climatiseur et dispositif de commande de moteur
WO2020070879A1 (fr) * 2018-10-05 2020-04-09 日立ジョンソンコントロールズ空調株式会社 Compresseur et appareil de climatisation de réfrigération utilisant ce dernier
WO2021002002A1 (fr) * 2019-07-04 2021-01-07 三菱電機株式会社 Dispositif d'entraînement de moteur électrique et appareil d'application de cycle de réfrigération
US11206743B2 (en) 2019-07-25 2021-12-21 Emerson Climate Technolgies, Inc. Electronics enclosure with heat-transfer element

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BRPI0702369A2 (pt) * 2007-05-29 2009-01-20 Whirlpool Sa sistema e mÉtodo de diagnàstico atravÉs da captaÇço de ondas mecÂnicas em sistemas de refrigeraÇço e/ou eletrodomÉsticos
JP5043521B2 (ja) * 2007-06-06 2012-10-10 サンデン株式会社 電動圧縮機の制御装置
CN105698453A (zh) * 2016-03-09 2016-06-22 广东美的制冷设备有限公司 变频空调器及其压缩机的停机控制方法和装置
EP3225844B1 (fr) * 2016-03-30 2018-07-04 Nidec Global Appliance Germany GmbH Dispositif de commande électronique pour un compresseur frigorifique
CN106524415B (zh) * 2016-11-18 2018-11-02 珠海格力电器股份有限公司 空调控制方法、装置以及空调
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CN100412464C (zh) 2008-08-20
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JPWO2004083744A1 (ja) 2006-06-22
KR100590352B1 (ko) 2006-06-19
CN1697954A (zh) 2005-11-16

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