EP1040304B1 - Appareil de reglage de la longueur de cycle d'un compresseur - Google Patents

Appareil de reglage de la longueur de cycle d'un compresseur Download PDF

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Publication number
EP1040304B1
EP1040304B1 EP98904711A EP98904711A EP1040304B1 EP 1040304 B1 EP1040304 B1 EP 1040304B1 EP 98904711 A EP98904711 A EP 98904711A EP 98904711 A EP98904711 A EP 98904711A EP 1040304 B1 EP1040304 B1 EP 1040304B1
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EP
European Patent Office
Prior art keywords
compressor
time
call
interval
energy value
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.)
Expired - Lifetime
Application number
EP98904711A
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German (de)
English (en)
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EP1040304A1 (fr
EP1040304A4 (fr
Inventor
Jack Hammer
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.)
INTELLIDYNE HOLDINGS, LLC
Original Assignee
Intellidyne Holdings LLC
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
Priority claimed from US08/996,750 external-priority patent/US5960639A/en
Application filed by Intellidyne Holdings LLC filed Critical Intellidyne Holdings LLC
Publication of EP1040304A1 publication Critical patent/EP1040304A1/fr
Publication of EP1040304A4 publication Critical patent/EP1040304A4/fr
Application granted granted Critical
Publication of EP1040304B1 publication Critical patent/EP1040304B1/fr
Anticipated expiration legal-status Critical
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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
    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/85—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using variable-flow pumps
    • 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
    • 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
    • F25B2600/23—Time delays

Definitions

  • the invention relates in general to devices that consume electrical energy in the process of generating a cooling medium used for the purposes of reducing the temperatures within an area requiring reduced temperatures.
  • This invention is particularly suited to reducing power consumption in refrigeration and air conditioning units.
  • Air Conditioning/Cooling/Refrigeration systems which utilize compressors, are least efficient when starting up. Prior to reaching optimum running conditions, the average net BTU output of the refrigeration system is below its rated capacity. The optimum run conditions of a refrigeration system are not obtained until all of the component parts of the system have obtained their design operational temperatures. This can take considerable time after the compressor starts because the thermal inertia of each device, which was just off and is relatively hotter than when running, must be overcome.
  • Shah refers to a delay in making a setpoint change, which may or may not coincide with a compressor call at the new setpoint.
  • Shah does not teach directly delaying a compressor call as in the present invention. In Shah, the compressor call may come on, un-delayed, in spite of the delay in setpoint change.
  • Shah does not teach using a delay to more efficiently regulate a steady-state temperature.
  • the invention increases the net BTU output of the refrigeration system by cycle control of the compressor. By intelligently increasing the delay between compressor run cycles, (the amount of which has been experimentally proven and to be within reasonable limits) longer more efficient (higher net BTU) output cycles are generated.
  • the cooling system is over-sized. This "over-sizing" condition exists, within a typical properly designed system, about 85% of the time and causes the cooling system to cycle the compressor in an inefficient and energy consuming fashion.
  • the present invention seeks to:
  • the invention through the use of computer technology, is able to determine the thermodynamic loading imposed upon the compressor, without the need of any additional sensors, and to alter the compressor cycling pattern in such a fashion as to cause the cooling capacity of the system to more closely match the demand of the system.
  • This more efficient ratio of capacity vs. demand causes a more efficient use of each compressor cycle and thereby a reduction of electric consumption.
  • Short-cycling causes undo stress on the compressor as well as much greater than normal electrical demands due to locked-rotor conditions which can occur as a result of non-pressure-equalization within the compressor. This condition is caused by an insufficient time-lapse between when the compressor is stopped and then restarted.
  • Another factor of short-cycling is the excess heat buildup in the motor windings which can be caused by repeated rapid starting of the compressor.
  • the invention incorporates an anti-short-cycling algorithm as part of its program.
  • the invention is therefore desirable for the invention to be an energy saving device capable of being used in cooling energy value sensor (such as a thermostat or pressuretrol) demand type control systems. It is not limited to such applications, but would also be suited for use with energy management systems. This invention would be suitable for new, retrofit and original equipment manufacturer (OEM) installations. It is also the invention's intent to be simple to install and not require any programming or adjustments.
  • cooling energy value sensor such as a thermostat or pressuretrol
  • OEM original equipment manufacturer
  • FIG. 1A shows a refrigeration system, generally designated 2, which includes the present invention.
  • the system comprises a compressor 4, which pumps high pressure gas through high pressure pipe 6 to condenser 8.
  • Fan 10 is propelled by motor 12, and drives air 14 across condenser 8 to cool the condenser coils 9, and the gas therein, causing the gas to condense to liquid and give up its heat of condensation.
  • cooling air 14 Through the length of the condenser 8, large amounts of heat are lost to cooling air 14, which brings down the temperature and heat content of the media leaving the condenser, bringing said media to a liquid state.
  • the liquid media is driven by pressure and it flows from condenser 8 through liquid pipe 16.
  • Liquid media flows along the liquid pipe 16, to evaporator 18, where fan 20, driven by motor 22, drives hot air 24 to be cooled by the evaporator 18.
  • the liquid media from liquid pipe 16, in evaporator 18 absorbs heat from the air 24, and the media evaporates, absorbing the heat of evaporation, and exits along low pressure gas pipe 26, returning to compressor 4, which again drives it through its cycle via high pressure gas pipe 6.
  • thermostat 28 controls fan motor 22, by closing a relay 29 between current source 30 and fan motor 22. Absent the invention, thermostat 28 would simultaneously close relay 31 between current 32 and compressor 4, so that current could flow across relay 31 and would actuate power compressor 4.
  • control apparatus 34 of the present invention interrupts the connection 36, which provides voltage to relay 31, and thereby prevents the compressor 4 from turning on. This results in a delay, which is controlled according to the program outlined further below.
  • control apparatus 34 is interposed in the wire 39 between the compressor 4 and energy value sensor, which is pressuretrol 40.
  • Pressuretrol 40 is typically found as the temperature equivalent sensor on a refrigeration unit.
  • a program also provides an appropriate delay to increase efficiency.
  • FIG. 2 is a typical installation wiring diagram which shows a control unit 34 of the present invention, wired into the cooling circuit.
  • Figure 2 shows control circuit power 42, which may be 230, 115 or 24 volts AC in the embodiment shown depending on which contact 44 a, b, or c it is attached to.
  • Wires 44-46 supply control circuit power to control unit 34.
  • Control wire 36 or 39 would provide control voltage to compressor contactor relay 31, but is broken so that yellow wire 48 and blue wire 49 insert control unit 34 into the circuit to prevent the compressor from operating until an appropriate delay has intervened.
  • FIG. 3 is a more detailed circuit diagram of the control unit 34.
  • AC power is supplied by wires white 44 and brown 46 to transformer 47, then to rectifier 50, comprising four ring diodes, which rectifies the AC to DC.
  • Approximately 14 volt DC is output across smoothing capacitor 56 to voltage regulator 57 across bypass capacitor 58 to pin 1 of BS-1.
  • BS-1 distributes 12 volts DC to control circuit 60 and its micro-controller chips 61 and memory 62 via voltage regulating chip 63 and power-on reset chip 64.
  • Light Emitting Diode 101 (LED) indicates mode status.
  • LED 102 indicates if an energy value sensor is calling for compressor.
  • Optoisolator 104 provides a sensor call to the controller over a wide range of possible call voltages, making this unit well suited for a variety of cooling systems.
  • Controller 34 operates according to the computer program at the end of this specification, entitled "COOLING ROUTINE”.
  • the program incorporates a 180 second anti-short-cycling delay to always avoid starting the compressor within 180 seconds of compressor shut down. This is sufficient time to reduce undue stress on the compressor, as well as much greater than normal electrical demands, due to locked-rotor conditions, by allowing pressure-equalization within the compressor. A 180 second rest reduces excess heat buildup in the motor windings which heat can be caused by repeated rapid starting of the compressor.
  • An anti-short-cycling algorithm tests off-time against the program constant MINOFFTIME, before allowing the compressor to start.
  • the compressor off-time has been greater than 1 hour, the compressor is started immediately upon a call for cooling, the counter is reset, and a new count begins.
  • the delay is calculated as 10% of the last off time, and a countdown for that interval from the sensor call continues. Once the countdown ends, the compressor relay actuates the compressor, and a new timecount starts.
  • T1, T6 and T11 represent points on the temperature or pressure graphs that correspond to points when the compressor is started.
  • T3, T8 and T13 correspond to the temperature or pressure levels when the compressor is stopped.
  • T2 correspond to the new temperature or pressure compressor start points.
  • T4, T9 and T14 correspond to the respective longer intervals before the compressor stop points.
  • T0-T1, T5-T6 and T10-T11 are the time intervals from the last compressor shut-down to a point when there is a need for cooling, hereinafter the off-call-time.
  • T0-T2, T5-T7, and T10-T12 are the new off-intervals required due to the invention, including the invention's extended off-intervals of T1-T2, T6-T7 and T11-T12.
  • Figure 5 graphs the effect of a load, over seven cycles of a conventional cooling system, without the present invention (top). As can be seen on the bottom of figure 5, the same load is handled in only five on-cycles, with reduced on-time, with the present invention. Temperature excursions beyond the high point are insignificant and brief. The graph also illustrates the compressor response either to temperature or cooling media pressure, depending on whether the energy value sensor is a thermostat or a pressuretrol.
  • T1 represents the compressor turn-on point along the temperature or pressure curves without the invention
  • T2 represents the new turn-on point and includes the extended off-time T1-T2 with the invention
  • T3 corresponds to the turn-off point of the temperature or pressure curves without the invention
  • T4 with the invention.
  • Figure 6 graphs a saturation load. Without the invention, the compressor runs continuously. The invention gives the compressor a 6 minute rest (T3-T4; T5-T6; etc.) every 54 minutes (T2-T3, T5-T6, etc.), to cool down, to save energy in the brief off-time. Temperature (not graphed) is largely unaffected by this rest period.
  • FIG. 7 graphs a short cycle restart without the invention.
  • the T1-T2 interval is too short to equalize compressor pressure or to cool the motor coils.
  • a severe and power consuming electrical load results, that might even burn out the motor.
  • the short compressor off-time (T1-T2) is extended by T2-T3 to an adequate 3 minutes (T1-T3), resulting in an easier starting load on the motor.

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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 Positive-Displacement Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Control Of Motors That Do Not Use Commutators (AREA)

Claims (19)

  1. Procédé de régulation du fonctionnement d'un système de refroidissement (2), comprenant les étapes consistant à :
    - mesurer une période d'arrêt (figure 5 T0 à T1) d'un circuit de commande (34) d'un compresseur (4) dans le but de retarder l'application de courant au compresseur (4) ;
    - détecter un appel (figure 5 T1) de compresseur (4) à partir d'un capteur de valeur d'énergie (28) ; et
    - toujours empêcher le fonctionnement du compresseur (4) pendant un intervalle (figure 5 T1 à T2) qui est une valeur dérivée de la période d'arrêt mesurée (figure 5 T0 à T1) et non inférieure à un temps d'arrêt minimum (figure 7 T1 à T3).
  2. Procédé selon la revendication 1, dans lequel le fonctionnement du compresseur (4) est empêché à moins et jusqu'à ce que la période d'arrêt (figure 7 T1 à T2) ne dépasse une valeur prédéterminée (figure 7 T1 à T3), laquelle valeur permet une égalisation de pression de compresseur (4) significative.
  3. Procédé selon la revendication 1, comprenant en outre les étapes consistant à :
    - stocker la période d'arrêt (figure 5 T0 à T1) mesurée en dernier dans une mémoire ;
    - calculer un pourcentage de la période d'arrêt ;
    - empêcher le fonctionnement du compresseur (4) pour un délai (figure 5 T1 à T2) égal au pourcentage ; et
    - faire fonctionner le compresseur (4) à la suite (figure 5 T2 à T4) du délai (figure 5 T1 à T2).
  4. Procédé selon la revendication 1, comprenant en outre les étapes consistant à :
    - mesurer un cycle actif (figure 6 T1 à T15) du temps de fonctionnement du compresseur (4) ;
    - arrêter l'opération du compresseur (4) une fois que le cycle actif s'est étendu pendant un intervalle de temps actif significatif (figure 6 T2 à T3) ; et
    - l'étape d'interruption de fonctionnement du compresseur (4) est pour un temps inactif mesuré d'un intervalle de repos (figure 6 T3 à T4), lequel intervalle de repos est court mais suffisant pour permettre :
    - l'égalisation du compresseur (4) ;
    - le refroidissement du moteur du compresseur (4) ; et
    - l'efficacité résultant de l'intervalle de repos (figure 6 T3 à T4), qui est bref, pendant lequel une température de l'espace est sensiblement maintenue par une inertie thermique d'objets et de fluides refroidis quelconques dans l'espace.
  5. Procédé de régulation d'un système de refroidissement (2) selon la revendication 1, ledit procédé comprenant les étapes consistant à :
    - surveiller une valeur provenant d'un capteur de valeur d'énergie (28) ;
    - déterminer à partir de ladite valeur si la valeur nécessite un appel pour le fonctionnement du compresseur (4) ;
    - générer un appel lorsque cela est nécessaire (figure 7 T2) ;
    - mesurer une période d'arrêt avant ledit appel à partir d'une extinction (figure 7 T1-T2) précédente du compresseur (4) ;
    - stocker la période d'arrêt (figure 7 T1 à T2) mesurée en dernier dans une mémoire ;
    dans lequel le temps inactif minimum (figure 7 T1 à T3) permettrait une égalisation de pression du compresseur (4) significative ;
    - calculer un pourcentage de la période d'arrêt ;
    - la valeur dérivée de la période d'arrêt mesurée (figure 5 T0 à T1) est égale au pourcentage ;
    - faire fonctionner le compresseur (4) à la suite de l'intervalle ;
    - mesurer un cycle actif (figure 6 T1 à T15) du temps de fonctionnement du compresseur (4) ;
    - interrompre le fonctionnement du compresseur (4) une fois que le cycle actif s'est étendu pendant un intervalle significatif (figure 6 T2 à T3) suffisant pour amener un espace à une température d'équilibre ; et
    - empêcher le fonctionnement du compresseur (4) pendant un intervalle de repos prédéterminé (figure 6 T3 à T4), lequel intervalle de repos est court mais suffisant pour permettre :
    - une égalisation du compresseur (4),
    - un refroidissement du moteur du compresseur (4), et
    - une amélioration de l'efficacité en sauvegardant de l'énergie pendant l'intervalle de repos (figure 6 T3 à T4), pendant lequel intervalle de repos une inertie thermique d'objets et de fluides refroidis quelconques dans l'espace maintient sensiblement une température dans l'espace.
  6. Procédé selon la revendication 5, dans lequel un ensemble suivant de valeurs optimales est sensiblement utilisé :
    - le temps inactif minimum (figure 7 T1 à T3) est trois minutes ;
    - le pourcentage est dix pourcents ;
    - l'intervalle significatif (figure 6 T2 à T3) est 54 minutes ; et
    - l'intervalle de repos prédéterminé (figure 6 T3 à T4) est 6 minutes.
  7. Système de refroidissement (2) comprenant un compresseur (4), un milieu de refroidissement et un échangeur de chaleur, comprenant en outre ;
    - un capteur de valeur d'énergie (28) ; et
    - des moyens :
    - pour surveiller le capteur de valeur d'énergie (28),
    - pour contrôler le compresseur (4),
    - pour déterminer la charge thermique sur le système de refroidissement (2),
    - pour mesurer une période d'arrêt (figure 5 T0 à T1) d'un circuit de commande (34) de compresseur (4),
    - pour recevoir un appel de compresseur (4) provenant du capteur de valeur d'énergie (28), et
    - pour toujours empêcher le capteur de valeur d'énergie (28) de faire fonctionner le compresseur (4) du système pour un intervalle (figure 5 T1 à T2) qui est une valeur dérivée de la période d'arrêt mesurée.
  8. Appareil selon la revendication 7, dans lequel le moyen de contrôle comprend :
    - une coupure dans un fil de fourniture de courant (36 ou 39) entre :
    - le capteur de valeur d'énergie (28), et
    - le compresseur (4) ; et
    - des moyens (34) pour former un pont de manière commutable sur ladite coupure.
  9. Appareil selon la revendication 8 dans lequel le moyen destiné à surveiller le capteur de valeur d'énergie (28) comprend :
    - un fil chaud (36 ou 39) activé par le capteur de valeur d'énergie (28) en réponse à une valeur d'énergie au niveau de laquelle l'espace nécessite plus de refroidissement ; et
    - un moyen de commutation (104) destiné à être actionné par une tension sur le fil chaud (36 ou 39).
  10. Appareil selon la revendication 9 dans lequel le moyen de commutation (104) destiné à être actionné par une tension sur le fil chaud (36 ou 39) est un circuit électronique (104) destiné à détecter une large plage d'entrées de tension.
  11. Appareil selon la revendication 10 dans lequel la large plage d'entrées de tension est entre 24 VAC et 240 VAC.
  12. Appareil selon la revendication 10 dans lequel le circuit électronique comprend un photocoupleur (104).
  13. Appareil selon la revendication 10 dans lequel le circuit électronique comprend un microcontrôleur (60).
  14. Appareil selon la revendication 13 avec des moyens destinés à augmenter un temps de fonctionnement par cycle du compresseur (4) et ainsi à améliorer une utilisation électrique et à diminuer un temps de fonctionnement total du compresseur (4).
  15. Appareil selon la revendication 7 dans lequel le capteur de valeur d'énergie est un thermostat (28).
  16. Appareil selon la revendication 7 dans lequel le capteur de valeur d'énergie est un pressostat (40).
  17. Appareil selon la revendication 8 dans lequel le moyen de commutation (31) se trouve dans une position normalement fermée de telle sorte que, si la fourniture de courant (42) ou le contrôleur (34) ne fonctionne pas, le système de refroidissement (2) fonctionne toujours.
  18. Procédé selon la revendication 1, dans lequel si la période d'arrêt (figure 5 T0 à T1) du compresseur (4) a été supérieure à une valeur maximale, l'intervalle est sensiblement zéro.
  19. Procédé selon la revendication 18, dans lequel la valeur maximale est sensiblement une heure.
EP98904711A 1997-12-23 1998-01-26 Appareil de reglage de la longueur de cycle d'un compresseur Expired - Lifetime EP1040304B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US08/996,750 US5960639A (en) 1997-01-23 1997-12-23 Apparatus for regulating compressor cycles to improve air conditioning/refrigeration unit efficiency
US996750 1997-12-23
PCT/US1998/001550 WO1999032838A1 (fr) 1997-12-23 1998-01-26 Appareil de reglage de la longueur de cycle d'un compresseur

Publications (3)

Publication Number Publication Date
EP1040304A1 EP1040304A1 (fr) 2000-10-04
EP1040304A4 EP1040304A4 (fr) 2002-08-21
EP1040304B1 true EP1040304B1 (fr) 2007-03-14

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Application Number Title Priority Date Filing Date
EP98904711A Expired - Lifetime EP1040304B1 (fr) 1997-12-23 1998-01-26 Appareil de reglage de la longueur de cycle d'un compresseur

Country Status (9)

Country Link
EP (1) EP1040304B1 (fr)
CN (1) CN1125297C (fr)
AT (1) ATE356963T1 (fr)
AU (1) AU747039B2 (fr)
DE (1) DE69837347T2 (fr)
ES (1) ES2285761T3 (fr)
HK (1) HK1033598A1 (fr)
NZ (1) NZ505835A (fr)
WO (1) WO1999032838A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013075113A1 (fr) * 2011-11-18 2013-05-23 Cooper Technologies, Inc. Rendement amélioré de chauffage, de ventilation et de climatisation par extension indirecte de temps de fonctionnement de compresseur

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US6755032B1 (en) 2000-01-13 2004-06-29 Ford Global Technologies, Inc. Control method for a vehicle having an engine and an accessory device
DE60119181D1 (de) * 2000-01-12 2006-06-08 Ford Global Tech Inc Steuerungsverfahren für ein Fahrzeug mit einer Brennkraftmaschine und eine Hilfseinrichtung
US6298675B1 (en) * 2000-01-12 2001-10-09 Ford Global Technologies, Inc. Estimation method for a vehicle having an engine and a cycling accessory device
BRPI0505060B1 (pt) * 2005-11-09 2020-11-10 Embraco Indústria De Compressores E Soluções Em Refrigeração Ltda sistema de controle de compressor linear, método de controle de compressor linear e compressor linear
DE102015212543A1 (de) * 2015-07-03 2017-01-05 Robert Bosch Gmbh Verfahren, Klimatisierungseinrichtung und System
JP7099425B2 (ja) * 2019-10-03 2022-07-12 トヨタ自動車株式会社 車載温調装置

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WO1984000603A1 (fr) * 1982-07-22 1984-02-16 Donald L Bendikson Controleur d'energie pour systeme de refrigeration
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Publication number Priority date Publication date Assignee Title
WO2013075113A1 (fr) * 2011-11-18 2013-05-23 Cooper Technologies, Inc. Rendement amélioré de chauffage, de ventilation et de climatisation par extension indirecte de temps de fonctionnement de compresseur

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ATE356963T1 (de) 2007-04-15
NZ505835A (en) 2003-05-30
ES2285761T3 (es) 2007-11-16
DE69837347T2 (de) 2007-11-29
HK1033598A1 (en) 2001-09-07
AU6251498A (en) 1999-07-12
EP1040304A1 (fr) 2000-10-04
WO1999032838A1 (fr) 1999-07-01
AU747039B2 (en) 2002-05-09
CN1286747A (zh) 2001-03-07
DE69837347D1 (de) 2007-04-26
EP1040304A4 (fr) 2002-08-21
CN1125297C (zh) 2003-10-22

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