EP0410330A2 - Procédé et dispositif de fonctionnement d'une installation frigorifique - Google Patents

Procédé et dispositif de fonctionnement d'une installation frigorifique Download PDF

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Publication number
EP0410330A2
EP0410330A2 EP19900113997 EP90113997A EP0410330A2 EP 0410330 A2 EP0410330 A2 EP 0410330A2 EP 19900113997 EP19900113997 EP 19900113997 EP 90113997 A EP90113997 A EP 90113997A EP 0410330 A2 EP0410330 A2 EP 0410330A2
Authority
EP
European Patent Office
Prior art keywords
cooling
compressors
refrigeration system
cooling point
requirement
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP19900113997
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German (de)
English (en)
Other versions
EP0410330A3 (en
EP0410330B1 (fr
Inventor
Wolfgang Höner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
York Deutschland GmbH
Original Assignee
York International GmbH
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
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Application filed by York International GmbH filed Critical York International GmbH
Priority to AT90113997T priority Critical patent/ATE91010T1/de
Publication of EP0410330A2 publication Critical patent/EP0410330A2/fr
Publication of EP0410330A3 publication Critical patent/EP0410330A3/de
Application granted granted Critical
Publication of EP0410330B1 publication Critical patent/EP0410330B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • F25B49/022—Compressor 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/22—Refrigeration systems for supermarkets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation

Definitions

  • the invention relates to a method for operating a refrigeration system, in particular a composite refrigeration system, with at least two compressors connected in parallel, which are operated simultaneously or alternately individually to cover the respective refrigeration requirement of at least one cooling point.
  • the invention further relates to a device for carrying out the method.
  • This device is, in particular, a composite refrigeration system with at least one cooling point provided with sensors, with at least two compressors connected in parallel, which, in cyclically alternating or joint operation, provide the cooling capacity required to cover the cooling requirement.
  • the cooling capacity of a refrigeration system is determined by the cooling requirement of the connected cooling points, which is essentially influenced by the ambient temperature and the atmospheric humidity of the ambient air at the location of the cooling points. As a result, strong fluctuations in the cooling requirement are possible in the course of the season.
  • a refrigeration system must always meet the maximum cooling requirement, i.e. H. If the ambient temperature is high and the ambient air humidity is high, the location of the cooling points should be designed for maximum load of refrigerated goods and temperature as well as for the cooling volume of the cooling points.
  • the previously mentioned fluctuations in the cooling requirement have the consequence that the compressors provided for the cooling supply are operated with different duty cycles, with a known high frequency having a disadvantageous effect on their service life.
  • the switching on of the compressors if there is no common operation due to high cooling demand, the individual compressors are switched on after a predetermined cycle, so that the switching on frequency is as equal as possible for all compressors.
  • the determination of the cooling requirement and the dependent operation of the compressors of the refrigeration system is usually carried out by evaluating the suction pressure in the coolant circuit. For this purpose, the current pressure in the suction line is compared in a control circuit with a lowest value determined by calculation, so that the maximum cooling capacity required to supply the cooling points is provided at maximum cooling requirements.
  • the cooling points are controlled independently of this in a separate control loop that controls the supply of refrigerant to the specified temperature values.
  • the solution to the problem is characterized in that a reference signal for the respective cooling conditions at the cooling point is transmitted to a central unit from each cooling point, that the respective cooling requirement is determined therefrom and that the connected compressors are switched on or off accordingly.
  • the devices originally provided for local temperature control of the cooling points are linked to the capacity control of the compressor network, the reference signal of the cooling point being based on a target specification which includes both the maximum cooling volume and the resulting maximum cooling requirement the location of the cooling point with the prevailing ambient conditions is also taken into account, evaluated in the central unit in order to obtain a measure of the actual cooling requirement and accordingly to put one or more compressors into operation.
  • the refrigerant suction pressure is expediently also evaluated in the central unit as an additional reference variable and is based on the respective switching command to the compressors.
  • the supply of refrigerant to the connected cooling points is opened or closed by the central unit.
  • the cyclical switching or step switching of the compressors is carried out directly by a step switch arranged in the central unit.
  • the deviation of the cooling point temperature from its predetermined target value in conjunction with a stored time factor is a measure of the cooling requirement present, ie. H. a measure of the increase or decrease of the respective evaporation pressure of the refrigerant, taking into account all factors that determine the refrigeration demand.
  • a composite refrigeration system of the type mentioned at the outset for carrying out the method described above is characterized in accordance with the invention in that a central unit is provided which works both with the sensors of each cooling point and with the connected units sealing the refrigeration system is connected that each sensor gives a reference signal to the central unit, which evaluates this to determine the cooling requirement and that the central unit controls the operation of the compressors in accordance with the determined cooling requirement.
  • a sensor is understood to mean a temperature control unit which comprises one or more temperature sensors placed at the cooling point and a thermostat which is operatively connected to them.
  • the thermostat is preferably designed as an electronic temperature controller in order to ensure the most precise possible temperature detection with sufficiently small tolerances.
  • the sensors of each cooling point are connected to a step switch provided for controlling the compressors and apply a reference signal to the latter, and that the step switch controls the operation of the connected compressors in accordance with the reference signals received.
  • the temperature deviation of the cooling points gives a direct connection or return command to the step switch of the compressor control.
  • the signal With a temperature deviation of z. B. 1 to 2 K, the signal is in the neutral zone, ie there is no switching on or off of the compressors. If there is a 1K deviation, the tap changer receives a return signal and if there is a 2K deviation, a step forward signal. Adjustable timers are provided for forward and reverse. With the help of the suction pressure measurement, minimum and maximum values of the suction pressure can be limited.
  • the only figure shows one Circuit diagram of a composite refrigeration system, which works according to the inventive method.
  • the single figure shows a composite refrigeration system 10, with a total of three cooling points 11, which are connected in parallel and which are represented schematically by evaporators 11a.
  • a sensor designed as a temperature control is assigned to each cooling point and is formed from a thermostat 13 and at least one temperature sensor 18.
  • Each thermostat 13 assigned to a cooling point 11 cooperates with the at least one temperature sensor 18 and is connected to a central unit 20 via a signal line 14. Via this signal line 14, the central unit 20 is transmitted a reference signal from each of the thermostats 13 assigned to the cooling points 11 belonging to the refrigeration system, which provides information about the current cooling requirement of the cooling point 11 and thus indirectly about both the temperature of the cooling point 11 and the ambient conditions at the installation site the cooling point 11 there.
  • the signal line 14 is preferably designed as a data bus line, so that signals of different types can be transmitted. In addition, the transmission of control commands with the signal line 14 is also possible.
  • Each cooling point 11 is supplied via an inlet line 19 with the refrigeration unit formed by a compressor 22 with the amount of refrigerant required to cover the respective refrigeration requirement.
  • a remote-controlled shut-off valve 12 is arranged in front of each evaporator 11a in the refrigerant line 19 and interrupts or releases the supply of refrigerant in accordance with the reference signal of the thermostat 13 assigned to this cooling point 11.
  • the shut-off valves are preferably designed such that they assume two end positions, namely “open” and “closed”, without an intermediate position.
  • throttle point 17 in the feed line 19, which is preferably designed as a thermostatic expansion valve in order to ensure the complete evaporation of the refrigerant in the evaporator associated with the cooling point 11, not shown here in any more detail.
  • each cooling point can also be assigned a blower 14, which serves to distribute the cooling power released at the cooling point 11 in the evaporator 11a evenly.
  • the above-mentioned refrigeration unit is formed from three compressors 22, each connected in parallel and driven by an electric motor 23, which has a condenser 25, in which the highly compressed refrigerant is liquefied, giving off heat, and a downstream collector 27, from which the feed line 19 branches. is connected to the evaporators 11a.
  • suction line 24 is designed as a collecting line for the individual lines coming from the individual cooling points and, when the refrigeration unit is reached, is in turn guided in individual lines to the individual compressors 22.
  • this can, as shown in the example, be designed as an air-cooled condenser, and the heat dissipation can be increased by means of a single-stage or multi-stage fan.
  • water cooling can also be provided instead, which serves as a regenerative heat source.
  • the central unit 20 is connected to each thermostat 13 via signal lines 14 and thus receives the current reference values from the connected cooling points 11.
  • control signals can also be transmitted via this signal line 14, which is for the remote actuation of the remotely operated shut-off valves 12 is used.
  • a control line 15 is provided, which establishes the connection between the central unit 20 and the respective drive module of the assigned shut-off valve 12.
  • the additional blower 14, which is used for uniform cooling distribution at the cooling point 11, is also connected via a control line 16 to the associated thermostat 13, the control line 16 being able to be switched through, so that the blower 14 is controlled directly by the central unit 20.
  • each drive motor 23 for the compressors 22 is connected to the central unit 20 via a separate line 28.
  • a pressure sensor 21 is provided, which is used to detect the suction pressure of the refrigerant in the return line 24 and is designed as a measuring transducer and is also connected to the central unit 20.
  • the central unit receives the additional information about the respective refrigerant temperature, which in comparison with the respective cooling point temperature determines the required cooling capacity, i. H. the need for cooling, can be determined.
  • the suction pressure is entered as the setpoint minimum for the maximum cooling capacity.
  • the suction pressure setpoint increase via the thermostats 13 can take place in a preselected range, for example 0-10 K.
  • the deviation from the temperature setpoint of the cooling point can be between 0 and 2 K.
  • a setpoint shift for the suction pressure is 0 K at the maximum deviation of the cooling point temperature. The closer the cooling point temperature approaches its setpoint, the greater the increase in suction pressure setpoint. If there is a 0 K deviation from the cold store temperature setpoint, the largest setpoint increase for the suction pressure of 10 K, for example, comes into play. It is provided that the setpoint shift for the suction pressure takes place step-by-step with the inclusion of a timing element not described here.
  • This increase in the suction pressure setpoint according to the invention increases the operating time of the cooling points 11, which has an advantageous effect on the operation of the throttle valves 17. This prevents short operating times, which lead to inefficient operation of the refrigeration system 10 as a result of insufficient refrigerant filling of the evaporators 11a of the cooling points 11 and which, due to insufficient suction gas overheating, reduce the performance of the compressors 22 and adversely affect their service life.
  • the reference signal of the cooling point 11, which exhibits the greatest deviation of the cooling point temperature from the setpoint value, is decisive for the setpoint shift of the suction pressure of the refrigerant, since compliance with the setpoint for the cooling point must always be given priority.
  • cooling points 11 with a lower setpoint deviation are introduced more quickly to the temperature setpoint due to the higher cold supply compared to the current demand.
  • the method according to the invention is such that when the temperature falls below the cooling point at the cooling point, the supply of refrigerant to this cooling point 11 is interrupted by actuating the remotely operable shut-off valve 12.
  • shut-off valves 12 installed in the feed line 19 have two end positions for "open” and "closed", i. H. without intermediate position.
  • the compressor is switched off with a time delay, but if the suction pressure setpoint is exceeded, a compressor 22 is switched on. If there is a correspondingly high cooling requirement, the entire refrigeration unit, ie. H. all compressors 22 connected in parallel must be switched on.
  • the refrigeration system 10 shown by way of example can also be operated using a second method according to the invention, the temperature deviation at the cooling points 11 being used directly to control the step switch of the compressor control 20.
  • the cooling capacity of the refrigeration system 10 is not adapted to the cooling requirements of the cooling points 11 by shifting the suction pressure setpoint for the refrigerant but by increasing or decreasing the cooling capacity by switching the installed compressors 22 on or off.
  • the detection of the suction pressure of the refrigerant in the return line 24 only serves to limit the suction pressure downwards and upwards, i.e. H. with regard to minimum and maximum pressure.
  • the cooling unit is only switched on again when the temperature of a cooling point has exceeded the specified tolerance range.
  • the compressor is queried and evaluated when the return is requested, and also to initiate the long-term shutdown of the cooling points 11, e.g. B. to defrost iced evaporators.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Air Conditioning Control Device (AREA)
EP90113997A 1989-07-28 1990-07-21 Procédé et dispositif de fonctionnement d'une installation frigorifique Expired - Lifetime EP0410330B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90113997T ATE91010T1 (de) 1989-07-28 1990-07-21 Verfahren und vorrichtung zum betrieb einer kaelteanlage.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3925090 1989-07-28
DE3925090A DE3925090A1 (de) 1989-07-28 1989-07-28 Verfahren zum betrieb einer kaelteanlage

Publications (3)

Publication Number Publication Date
EP0410330A2 true EP0410330A2 (fr) 1991-01-30
EP0410330A3 EP0410330A3 (en) 1991-06-26
EP0410330B1 EP0410330B1 (fr) 1993-06-23

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EP90113997A Expired - Lifetime EP0410330B1 (fr) 1989-07-28 1990-07-21 Procédé et dispositif de fonctionnement d'une installation frigorifique

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EP (1) EP0410330B1 (fr)
AT (1) ATE91010T1 (fr)
DE (2) DE3925090A1 (fr)

Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0543622A2 (fr) * 1991-11-18 1993-05-26 Sanyo Electric Co., Limited. Appareil de conditionnement d'air et dispositif de commande pour celui-ci
EP0552127A1 (fr) * 1992-01-17 1993-07-21 Carrier Corporation Séquence automatique d'arrêt d'un refroidisseur
EP0604359A1 (fr) * 1992-12-21 1994-06-29 Carrier Corporation Système de contrôle de la capacité de chauffage ou de refroidissement dans les installations de chauffage ou de climatisation
EP0660213A2 (fr) * 1993-12-22 1995-06-28 Novar Electronics Corporation Méthode de synchronisation d'enceinte réfrigérée pour l'optimisation de compresseur
WO1997032170A1 (fr) * 1996-02-28 1997-09-04 Danfoss A/S Systeme de refrigeration
FR2783309A1 (fr) * 1998-09-16 2000-03-17 Mc International Procede de regulation du taux de compression d'un fluide frigorigene par augmentation de la pression d'evaporation et installation frigorifique
WO2001035520A1 (fr) * 1999-11-12 2001-05-17 Lg Electronics Inc. Dispositif et procede pour commander l'alimentation en courant et en capacitance statique d'un compresseur
EP1398584A1 (fr) * 2002-09-13 2004-03-17 Whirlpool Corporation Procédé de commande d'un réfrigérateur à plusieurs compartiments froids et réfrigérateur utilisant un tel procédé
WO2010029027A1 (fr) * 2008-09-10 2010-03-18 Ago Ag Energie + Anlagen Pompe à chaleur ou machine frigorifique et procédé permettant de faire fonctionner une pompe à chaleur ou une machine frigorifique
US8065886B2 (en) 2001-05-03 2011-11-29 Emerson Retail Services, Inc. Refrigeration system energy monitoring and diagnostics
US8302415B2 (en) 2005-03-18 2012-11-06 Danfoss A/S Method for controlling a refrigeration system
US8473106B2 (en) 2009-05-29 2013-06-25 Emerson Climate Technologies Retail Solutions, Inc. System and method for monitoring and evaluating equipment operating parameter modifications
US8495886B2 (en) 2001-05-03 2013-07-30 Emerson Climate Technologies Retail Solutions, Inc. Model-based alarming
US8700444B2 (en) 2002-10-31 2014-04-15 Emerson Retail Services Inc. System for monitoring optimal equipment operating parameters
US8964338B2 (en) 2012-01-11 2015-02-24 Emerson Climate Technologies, Inc. System and method for compressor motor protection
US8974573B2 (en) 2004-08-11 2015-03-10 Emerson Climate Technologies, Inc. Method and apparatus for monitoring a refrigeration-cycle system
US9121407B2 (en) 2004-04-27 2015-09-01 Emerson Climate Technologies, Inc. Compressor diagnostic and protection system and method
US9140728B2 (en) 2007-11-02 2015-09-22 Emerson Climate Technologies, Inc. Compressor sensor module
US9285802B2 (en) 2011-02-28 2016-03-15 Emerson Electric Co. Residential solutions HVAC monitoring and diagnosis
US9310439B2 (en) 2012-09-25 2016-04-12 Emerson Climate Technologies, Inc. Compressor having a control and diagnostic module
US9310094B2 (en) 2007-07-30 2016-04-12 Emerson Climate Technologies, Inc. Portable method and apparatus for monitoring refrigerant-cycle systems
US9551504B2 (en) 2013-03-15 2017-01-24 Emerson Electric Co. HVAC system remote monitoring and diagnosis
US9638436B2 (en) 2013-03-15 2017-05-02 Emerson Electric Co. HVAC system remote monitoring and diagnosis
US9765979B2 (en) 2013-04-05 2017-09-19 Emerson Climate Technologies, Inc. Heat-pump system with refrigerant charge diagnostics
US9803902B2 (en) 2013-03-15 2017-10-31 Emerson Climate Technologies, Inc. System for refrigerant charge verification using two condenser coil temperatures
US9823632B2 (en) 2006-09-07 2017-11-21 Emerson Climate Technologies, Inc. Compressor data module
US9885507B2 (en) 2006-07-19 2018-02-06 Emerson Climate Technologies, Inc. Protection and diagnostic module for a refrigeration system
US10041713B1 (en) 1999-08-20 2018-08-07 Hudson Technologies, Inc. Method and apparatus for measuring and improving efficiency in refrigeration systems
WO2018202496A1 (fr) * 2017-05-01 2018-11-08 Danfoss A/S Procédé de commande de pression d'aspiration sur la base d'une entité de refroidissement la plus chargée

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DE10118444A1 (de) * 2001-04-12 2002-10-17 Linde Ag Verdichtersatz und Verfahren zum Regeln eines Verdichtersatzes
DE102005009173A1 (de) * 2005-02-17 2006-08-24 Bitzer Kühlmaschinenbau Gmbh Kälteanlage
EP1851959B1 (fr) 2005-02-21 2012-04-11 Computer Process Controls, Inc. Systeme de surveillance et de commande d'entreprise
US7665315B2 (en) 2005-10-21 2010-02-23 Emerson Retail Services, Inc. Proofing a refrigeration system operating state
US7752853B2 (en) 2005-10-21 2010-07-13 Emerson Retail Services, Inc. Monitoring refrigerant in a refrigeration system
US7752854B2 (en) 2005-10-21 2010-07-13 Emerson Retail Services, Inc. Monitoring a condenser in a refrigeration system

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FR2505466A1 (fr) * 1981-05-08 1982-11-12 Quiri Cie Sa Usines Procede de regulation automatique d'installations frigorifiques ou de climatisation, et automate programmable pour la mise en oeuvre de ce procede
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US4487028A (en) * 1983-09-22 1984-12-11 The Trane Company Control for a variable capacity temperature conditioning system

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DE3220420A1 (de) * 1982-05-29 1983-12-15 Vereinigte Elektrizitätswerke Westfalen AG, 4600 Dortmund Verfahren zur regelung eines elektrisch ansteuerbaren expansionsventils
EP0253928A1 (fr) * 1986-07-22 1988-01-27 Margaux Controls Inc. Système de régulation du compresseur d'une installation frigorifique
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US2274336A (en) * 1936-04-18 1942-02-24 Westinghouse Electric & Mfg Co Control system for refrigerating apparatus
DE842351C (de) * 1948-02-02 1952-06-26 Escher Wyss Maschinenfabrik G Anlage mit mehreren Verdichtern
US4384462A (en) * 1980-11-20 1983-05-24 Friedrich Air Conditioning & Refrigeration Co. Multiple compressor refrigeration system and controller thereof
FR2505466A1 (fr) * 1981-05-08 1982-11-12 Quiri Cie Sa Usines Procede de regulation automatique d'installations frigorifiques ou de climatisation, et automate programmable pour la mise en oeuvre de ce procede
US4487028A (en) * 1983-09-22 1984-12-11 The Trane Company Control for a variable capacity temperature conditioning system

Cited By (63)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0543622A2 (fr) * 1991-11-18 1993-05-26 Sanyo Electric Co., Limited. Appareil de conditionnement d'air et dispositif de commande pour celui-ci
EP0543622A3 (en) * 1991-11-18 1993-11-18 Sanyo Electric Co Air conditioner and control apparatus therefor
EP0552127A1 (fr) * 1992-01-17 1993-07-21 Carrier Corporation Séquence automatique d'arrêt d'un refroidisseur
EP0604359A1 (fr) * 1992-12-21 1994-06-29 Carrier Corporation Système de contrôle de la capacité de chauffage ou de refroidissement dans les installations de chauffage ou de climatisation
EP0660213A2 (fr) * 1993-12-22 1995-06-28 Novar Electronics Corporation Méthode de synchronisation d'enceinte réfrigérée pour l'optimisation de compresseur
EP0660213A3 (fr) * 1993-12-22 1997-06-04 Novar Electronics Corp Méthode de synchronisation d'enceinte réfrigérée pour l'optimisation de compresseur.
WO1997032170A1 (fr) * 1996-02-28 1997-09-04 Danfoss A/S Systeme de refrigeration
DE19607474C1 (de) * 1996-02-28 1997-10-30 Danfoss As Kälteanlage
FR2783309A1 (fr) * 1998-09-16 2000-03-17 Mc International Procede de regulation du taux de compression d'un fluide frigorigene par augmentation de la pression d'evaporation et installation frigorifique
US10041713B1 (en) 1999-08-20 2018-08-07 Hudson Technologies, Inc. Method and apparatus for measuring and improving efficiency in refrigeration systems
WO2001035520A1 (fr) * 1999-11-12 2001-05-17 Lg Electronics Inc. Dispositif et procede pour commander l'alimentation en courant et en capacitance statique d'un compresseur
US6844698B1 (en) 1999-11-12 2005-01-18 Lg Electronics Inc. Device and method for controlling supply of current and static capacitance to compressor
US8316658B2 (en) 2001-05-03 2012-11-27 Emerson Climate Technologies Retail Solutions, Inc. Refrigeration system energy monitoring and diagnostics
US8065886B2 (en) 2001-05-03 2011-11-29 Emerson Retail Services, Inc. Refrigeration system energy monitoring and diagnostics
US8495886B2 (en) 2001-05-03 2013-07-30 Emerson Climate Technologies Retail Solutions, Inc. Model-based alarming
EP1398584A1 (fr) * 2002-09-13 2004-03-17 Whirlpool Corporation Procédé de commande d'un réfrigérateur à plusieurs compartiments froids et réfrigérateur utilisant un tel procédé
US8700444B2 (en) 2002-10-31 2014-04-15 Emerson Retail Services Inc. System for monitoring optimal equipment operating parameters
US9121407B2 (en) 2004-04-27 2015-09-01 Emerson Climate Technologies, Inc. Compressor diagnostic and protection system and method
US9669498B2 (en) 2004-04-27 2017-06-06 Emerson Climate Technologies, Inc. Compressor diagnostic and protection system and method
US10335906B2 (en) 2004-04-27 2019-07-02 Emerson Climate Technologies, Inc. Compressor diagnostic and protection system and method
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Also Published As

Publication number Publication date
ATE91010T1 (de) 1993-07-15
EP0410330A3 (en) 1991-06-26
DE3925090A1 (de) 1991-02-07
DE59001849D1 (de) 1993-07-29
EP0410330B1 (fr) 1993-06-23

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