EP1450041A1 - Refrigerant circuit with a controlled swash-plate type compressor - Google Patents

Refrigerant circuit with a controlled swash-plate type compressor Download PDF

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Publication number
EP1450041A1
EP1450041A1 EP04000690A EP04000690A EP1450041A1 EP 1450041 A1 EP1450041 A1 EP 1450041A1 EP 04000690 A EP04000690 A EP 04000690A EP 04000690 A EP04000690 A EP 04000690A EP 1450041 A1 EP1450041 A1 EP 1450041A1
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EP
European Patent Office
Prior art keywords
refrigerant
swash plate
pressure
compressor
control valve
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.)
Withdrawn
Application number
EP04000690A
Other languages
German (de)
French (fr)
Inventor
Henry Hartung
Heiko Dröse
Klaus Gebauer
Thomas Reske
Harry Nissen
Thomas Küppers
Dikran-Can Magzalci
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Volkswagen AG
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Volkswagen AG
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Filing date
Publication date
Application filed by Volkswagen AG filed Critical Volkswagen AG
Publication of EP1450041A1 publication Critical patent/EP1450041A1/en
Withdrawn legal-status Critical Current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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/184—Valve controlling parameter
    • F04B2027/1854—External parameters
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2600/023—Compressor control controlling swash plate angles
    • 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters

Definitions

  • the invention relates to a refrigerant circuit with a regulated swash plate compressor, in particular for a motor vehicle air conditioning system operated with the refrigerant R744 (CO 2 refrigerant).
  • the air that is supplied to the passenger compartment is at one Heat exchanger (evaporator) cooled, the refrigerant conducted in it evaporates and extracts the required amount of heat from the air flowing past.
  • the refrigerant is conditioned by changes in state, so that a limited amount of refrigerant is sufficient to cool the air.
  • the gas cooler or condenser refrigerant condenser
  • the amount of heat supplied to the evaporator by the outside air withdrawn again for which purpose between the refrigerant and the outside air Temperature difference must prevail.
  • the gaseous refrigerant is in one Compressor compresses and increases in temperature before it enters the gas cooler is directed and liquefied there. Between the evaporator and the gas cooler is the further arranged an expansion device to the compressed in the compressor and thus refrigerants provided with a higher pressure and a higher temperature to relax again and to regulate the refrigerant flow.
  • Compressor and Expansion valves separate the refrigerant circuit into a high pressure and one Low pressure area.
  • Swashplate compressors are usually used in motor vehicle air conditioning systems (Compressors) used.
  • Compressor is a rotary movement which is arranged in a crankcase Swashplate over connecting elements or coupling links in a back and forth Moving movement implemented by pistons movably arranged in cylinders.
  • gaseous refrigerant drawn in from a suction chamber is compressed and discharged through an exhaust chamber.
  • the stroke of the pistons changes to Agreement with changes in the swash plate inclination angle.
  • This Tilt angle is controlled in a known manner by regulating the pressure in the Crank chamber in which the swash plate is arranged, with reference to the intake pressure set in the cylinder, this pressure by a housed in the cylinder block Control valve is regulated.
  • the swash plate inclination changed to the delivery capacity of the compressor to the required cooling capacity adapt.
  • this is through a control spring in the direction of reducing its inclination, i.e. in the direction a reduction in the stroke volume, preloaded.
  • the proposed refrigerant circuit consists of a swash plate compressor (Compressor), at the outlet of which a high pressure section with a gas cooler or Refrigerant condenser and on its suction side (compressor inlet) Low pressure section are connected to an evaporator, and the High pressure section with adjustable connecting the low pressure section Expansion device, which are connected to each other by a refrigerant line, and a control valve on the suction side of the compressor, through which the refrigerant is sucked back into this, being in front of the inlet of the evaporator Temperature sensor or a pressure sensor in the suction line in front of the compressor is arranged, the control electronics with the actuator of the control valve in There is an operative connection, and that the tilt-adjustable swash plate, the control valve and the respective sensor form a suction pressure control circuit.
  • Compressor swash plate compressor
  • the control valve is a 3-way valve with a suction pressure, a high pressure and a Crank chamber connection.
  • the temperature sensor measures the saturation temperature at Evaporator input from which is stored in a control electronics Vapor pressure curve of the respective refrigerant, the evaporator pressure and thus also the Suction pressure is determined. This eliminates the need for complicated and time-consuming regulation several sensors. Instead of a pressure sensor in the suction line, the Compressor a temperature sensor used in front of the evaporator inlet, because of this is cheaper.
  • the control strategy provides that the suction pressure is independent of keep the speed of the compressor constant. This means that the piston stroke at high engine and thus compressor speeds are low and at maximum when idling.
  • the refrigerant circuit controlled in this way enables rapid adjustment of the Compressor output for the respective cooling requirement.
  • the control valve is preferably a 3-way valve with a pulse width modulation electromagnetic actuator that has a short response time.
  • An internal heat exchanger with the suction line of the compressor can be formed in the outlet line of the refrigerant condenser, through which the high-pressure cooled refrigerant is led to the expansion element and the expanded and vaporous refrigerant is led to the compressor, so that the refrigerant to be expanded and evaporated is cooled , with the consequence that the liquid portion of the refrigerant increases after the expansion and thus more liquid refrigerant is available.
  • the internal heat exchanger thus increases the cooling capacity and also the efficiency of the cooling circuit.
  • An internal heat exchanger is also advantageous because of the rapid change in operating conditions. This version with an internal heat exchanger is particularly suitable for CO 2 refrigerants.
  • a thematic expansion valve is advantageously used as the expansion organ used.
  • overheating is on Evaporator outlet increased so that the expansion valve opens wide and the Refrigerant mass flow is increased, making the maximum in the shortest possible time Cooling capacity is achieved.
  • This refrigerant circuit has a swash plate compressor 1, a gas cooler (refrigerant condenser) 2, an inner heat exchanger 3 with a first refrigerant line coil 3.1, a thermostatic expansion valve 4 of known type with a thermostatic sensor 5, an evaporator 6, at the outlet of which the sensor 5 is arranged, a liquid collector 7 and the heat exchanger 3 with a second refrigerant line coil 3.2 in front of the compressor 1.
  • a 3-way control valve 8 is arranged in the valve cover on the suction side of the compressor 1, via which the refrigerant is sucked into the latter.
  • This control valve 8 has a connection 8.1 to the suction chamber of the compressor 1, a connection 8.2 to its high pressure chamber, a connection 8.3 to its crank chamber and an electromagnetic actuator 8.4 (not shown further), which is operatively connected to these connections 8.1 to 8.3.
  • the actuator 8.4 is connected to control electronics 9, in which the CO 2 vapor pressure curve is stored and which receives as an input variable the saturation temperature of the refrigerant at the inlet of the evaporator 6 from a temperature sensor 10 arranged there.
  • the CO 2 refrigerant which has a pressure of approximately 35 to 45 bar and a temperature of approximately 20 ° C. on the suction side of the compressor 1, is compressed in the compressor 1 to a pressure of essentially 110 bar, the temperature of the Refrigerant rises to approx. 100 ° C.
  • the gas cooler 2 the refrigerant is cooled to approx. 55 ° to 60 ° C by the outside air flowing past and liquefied in the process.
  • the heat extracted from the CO 2 refrigerant is dissipated with the outside air.
  • the CO 2 refrigerant flowing through the line coil 3.1 gives heat to the one flowing through the line coil 3.2
  • Refrigerant from which is integrated in the suction line of the compressor, wherein it is cooled to a temperature of substantially 25 ° C.
  • the liquid CO 2 refrigerant which has a pressure of about 110 bar and a temperature of essentially 25 ° C. on the high pressure side, is converted into the wet vapor state, where it is expanded and released to a pressure of 35 to 45 bar a temperature of 0 ° to 10 ° C is cooled.
  • the CO 2 refrigerant enters the evaporator 6, where it evaporates by absorbing heat from the outside or recirculated air to be cooled for the passenger compartment at a constant pressure of 35 to 45 bar, which corresponds to the suction pressure at the compressor 1.
  • the expansion valve 4 as an adjustable mass flow valve is set so that the refrigerant mass flow passing through the expansion valve 4 for cooling the air is set so that the refrigerant in the evaporator 6 is converted as completely as possible into the gaseous state and at the evaporator outlet by about 2 ° to 4 ° C is overheated.
  • the gaseous refrigerant then flows through the liquid collector 7 in order to retain residues of liquid refrigerant.
  • Saturated wet CO 2 is present at the evaporator inlet, the saturation temperature of which depends on the output of the compressor 1. If the compressor 1 generates a high CO 2 mass flow and a greater cooling capacity than the target cooling capacity due to a high speed of the vehicle engine with which it is coupled, the saturation temperature at the evaporator inlet and thus also the saturation pressure drop. In order to reduce the mass flow and thus the cooling capacity of the compressor 1, the piston stroke in this must be reduced. This is done with the help of the central control electronics 9 and the pulse-width-modulated control valve 8, which is coupled to the central control electronics 9, which receives the saturation temperature of the CO refrigerant from the temperature sensor 10.
  • the suction pressure in the compressor 1 is kept essentially constant, regardless of the speed of the compressor, via the control valve 8.
  • the inclination of the swash plate in this must be reduced. This is done by changing the pressure difference between the pressure in the crank chamber and the pressure in the suction chamber of the compressor 1. Consequently, with the pressure in the suction chamber remaining constant, the pressure in the crank chamber must be increased in order to reduce the inclination of the swash plate and the piston stroke.
  • the actuator 8.4 of the control valve 8 is adjusted by the control electronics 9 so that gaseous CO 2 refrigerant is pressed into the crank chamber of the compressor 1 from the high-pressure chamber connection 8.2.

Abstract

A 3-way control valve (8) has suction pressure (8.1), high pressure (8.2) and a crank chamber connection (8.3). A temperature probe (10) fits in front a vaporizer's (6) opening or a pressure sensor fits in a suction pipe in front of a swash-plate compressor (1) and keeps an active link with the control valve's actuator (8.4). An independent claim is also included for a method for operating a motor vehicle's air-conditioning with a refrigerant circuit.

Description

Die Erfindung betrifft einen Kältemittelkreislauf mit einem geregelten Taumelscheibenkompressor, insbesondere für eine mit dem Kältemittel R744 (CO2-Kältemittel) betriebene Kfz-Klimaanlage.The invention relates to a refrigerant circuit with a regulated swash plate compressor, in particular for a motor vehicle air conditioning system operated with the refrigerant R744 (CO 2 refrigerant).

In Kfz-Klimaanlagen wird die Luft, die der Fahrgastzelle zugeführt wird, an einem Wärmetauscher (Verdampfer) gekühlt, wobei das in diesen geleitete Kältemittel verdampft und die dafür erforderliche Wärmemenge der vorbeiströmenden Luft entzieht. In einem Kreisprozeß wird das Kältemittel durch Zustandsänderungen aufbereitet, so daß für das Kühlen der Luft eine begrenzte Kältemittelmenge ausreicht. In einem zweiten Wärmetauscher, dem Gaskühler oder Kondensator (Kältemittelverflüssiger), wird dem Kältemittel die im Verdampfer zugeführte Wärmemenge durch Außenluft wieder entzogen, wozu zwischen dem Kältemittel und der Außenluft eine Temperaturdifferenz herrschen muß. Daher wird das gasförmige Kältemittel in einem Kompressor verdichtet und in seiner Temperatur erhöht, bevor es in den Gaskühler geleitet und dort verflüssigt wird. Zwischen dem Verdampfer und dem Gaskühler ist des weiteren ein Expansionsorgan angeordnet, um das im Kompressor verdichtete und somit mit einem höheren Druck und mit einer höheren Temperatur versehene Kältemittel wieder zu entspannen und um den Kältemittelfluß zu regeln. Kompressor und Expansionsventil trennen den Kältemittelkreislauf in einen Hochdruck- und einen Niederdruckbereich. Üblicherweise befindet sich im Hochdruckbereich, also im Bereich des verdichteten Kältemittels zwischen dem Kompressor und dem Expansionsorgan auch ein Kältemittelsammler, in dem das stark hygroskopische Kältemittel getrocknet wird, um Korrossionsschäden im Verdichter zu vermeiden.In automotive air conditioning systems, the air that is supplied to the passenger compartment is at one Heat exchanger (evaporator) cooled, the refrigerant conducted in it evaporates and extracts the required amount of heat from the air flowing past. In a cyclic process, the refrigerant is conditioned by changes in state, so that a limited amount of refrigerant is sufficient to cool the air. In one second heat exchanger, the gas cooler or condenser (refrigerant condenser), the amount of heat supplied to the evaporator by the outside air withdrawn again, for which purpose between the refrigerant and the outside air Temperature difference must prevail. Therefore, the gaseous refrigerant is in one Compressor compresses and increases in temperature before it enters the gas cooler is directed and liquefied there. Between the evaporator and the gas cooler is the further arranged an expansion device to the compressed in the compressor and thus refrigerants provided with a higher pressure and a higher temperature to relax again and to regulate the refrigerant flow. Compressor and Expansion valves separate the refrigerant circuit into a high pressure and one Low pressure area. Usually located in the high pressure area, i.e. in the area of the compressed refrigerant between the compressor and the expansion device also a refrigerant collector in which the highly hygroscopic refrigerant is dried to avoid corrosion damage in the compressor.

In Kraftfahrzeug-Klimaanlagen werden in der Regel Taumelscheibenkompressoren (Kompressoren) eingesetzt. Bei einem in der DE 41 39186 A1 beschriebenen Kompressor wird eine Drehbewegung der in einem Kurbelgehäuse angeordneten Taumelscheibe über Verbindungselemente oder Kupplungsglieder in eine hin- und hergehende Bewegung von in Zylindern bewegbar angeordneten Kolben umgesetzt. In diesen wird aus einer Ansaugkammer angesaugtes gasförmiges Kältemittel komprimiert und durch eine Ausstoßkammer ausgefördert. Der Hub der Kolben ändert sich in Übereinstimmung mit Änderungen im Neigungswinkel der Taumelscheibe. Dieser Neigungswinkel wird in bekannter Weise durch eine Regelung des Druckes in der Kurbelkammer, in der die Taumelscheibe angeordnet ist, mit Bezug zum Ansaugdruck im Zylinder eingestellt, wobei dieser Druck durch ein im Zylinderblock untergebrachtes Regelventil geregelt wird. Als Ergebnis dessen wird die Neigung der Taumelscheibe geändert, um die Förderleistung des Kompressors an die geforderte Kälteleistung anzupassen. Zur Stabilisierung der Neigungsstellung der Taumelscheibe ist diese durch eine Regelfeder in Richtung der Reduzierung ihrer Schrägstellung, also in Richtung einer Verkleinerung des Hubvolumens, vorgespannt.Swashplate compressors are usually used in motor vehicle air conditioning systems (Compressors) used. In one described in DE 41 39186 A1 Compressor is a rotary movement which is arranged in a crankcase Swashplate over connecting elements or coupling links in a back and forth Moving movement implemented by pistons movably arranged in cylinders. In gaseous refrigerant drawn in from a suction chamber is compressed and discharged through an exhaust chamber. The stroke of the pistons changes to Agreement with changes in the swash plate inclination angle. This Tilt angle is controlled in a known manner by regulating the pressure in the Crank chamber in which the swash plate is arranged, with reference to the intake pressure set in the cylinder, this pressure by a housed in the cylinder block Control valve is regulated. As a result, the swash plate inclination changed to the delivery capacity of the compressor to the required cooling capacity adapt. To stabilize the inclination of the swash plate, this is through a control spring in the direction of reducing its inclination, i.e. in the direction a reduction in the stroke volume, preloaded.

Wegen der schnellen Änderung der Betriebsbedingungen infolge der Fahrzeugbewegung mit wechselnden Fahrgeschwindigkeiten und unterschiedlichem Wärmeeinfall unterliegt der Kältebedarf großen Schwankungen, an den sich die Kälteleistung des Kompressors anpassen muß. In der CH 690 189 A5 ist ein Regelverfahren beschrieben, bei dem der Kältemittelkreislauf in Strömungsrichtung hinter dem Expansionsventil und dem sich hinter diesem anschließenden Wärmeaustauscher mit dem Triebraum (Kurbelkammer) des Kompressors verbunden ist, so daß in diesem mindestens angenähert derselbe Druck wie an dieser Verbindungsstelle vorhanden ist. Die Leistungsregelung erfolgt dabei durch ein Regelventil, daß in Strömungsrichtung hinter dieser Verbindungsstelle und an der Saugseite des Kompressors angeordnet ist, so daß die Verstellung der Neigung der Taumelscheibe durch die geregelte Differenz zwischen dem Druck in der Kurbelkammer und demjenigen an der Saugseite erfolgt.Because of the rapid change in operating conditions as a result of Vehicle movement with changing driving speeds and different Incidence of heat is subject to large fluctuations in the cooling demand, to which the The cooling capacity of the compressor must be adjusted. In CH 690 189 A5 there is a Control method described in which the refrigerant circuit in the flow direction behind the expansion valve and the one behind it Heat exchanger connected to the drive chamber (crank chamber) of the compressor is, so that in this at least approximately the same pressure as on this Connection point is present. The power is regulated by a Control valve that in the flow direction behind this connection point and at the Suction side of the compressor is arranged so that the adjustment of the inclination of the Swashplate by the regulated difference between the pressure in the crank chamber and the one on the suction side.

Es ist Aufgabe der Erfindung, einen Kältemittelkreislauf mit einem geregelten Taumelscheibenkompressor nach dem Oberbegriff des Anspruchs 1 alternativ und auf einfache Weise zu regeln.It is an object of the invention to provide a refrigerant circuit with a regulated Swash plate compressor according to the preamble of claim 1 alternatively and easy way to regulate.

Diese Aufgabe wird bei einem Kältemittelkreislauf nach dem Oberbegriff des Anspruchs 1 durch dessen kennzeichnende Merkmale und ein Verfahren mit den Merkmalen des Anspruchs 7 gelöst.This task is carried out in a refrigerant circuit according to the generic term of Claim 1 by its characterizing features and a method with the Features of claim 7 solved.

Der vorgeschlagene Kältemittelkreislauf besteht aus einem Taumelscheibenkompressor (Kompressor), an dessen Ausgang ein Hochdruckabschnitt mit einem Gaskühler oder Kältemittelverflüssiger und an dessen Saugseite (Kompressoreingang) ein Niederdruckabschnitt mit einem Verdampfer angeschlossen sind, und einem den Hochdruckabschnitt mit dem Niederdruckabschnitt verbindenden regelbaren Expansionsorgan, die jeweils durch eine Kältemittelleitung miteinander verbunden sind, sowie einem Regelventil an der Saugseite des Kompressors, über das das Kältemittel wieder in diesen gesaugt wird, wobei vor dem Eingang des Verdampfers ein Temperatursensor oder in der Saugleitung vor dem Kompressor ein Drucksensor angeordnet ist, der über eine Regelelektronik mit dem Stellantrieb des Regelventils in Wirkverbindung steht, und daß die neigungsverstellbare Taumelscheibe, das Regelventil und der jeweilige Sensor einen Saugdruckregelkreis ausbilden. Das Regelventil ist ein 3-Wege-Ventil mit einem Saugdruck-, einem Hochdruck- und einem Kurbelkammeranschluß. Der Temperatursensor mißt dabei die Sättigungstemperatur am Verdampfereingang, aus der über die in einer Regelelektronik abgelegte Dampfdruckkurve des jeweiligen Kältemittels der Verdampferdruck und damit auch der Saugdruck bestimmt wird. Damit entfällt eine komplizierte und aufwändige Regelung mit mehreren Sensoren. Bevorzugt wird anstelle eines Drucksensors in der Saugleitung des Kompressors ein Temperatursensor vor dem Verdampfereingang eingesetzt, da dieser kostengünstiger ist. Die Regelstrategie sieht dabei vor, den Saugdruck unabhängig von der Drehzahl des Kompressors konstant zu halten. Das heißt, daß der Kolbenhub bei hohen Motor- und damit Kompressordrehzahlen klein und bei Leerlauf maximal ist. Der auf diese Weise geregelte Kältemittelkreilauf ermöglicht eine schnelle Anpassung der Kompressorleistung an die jeweilige Kälteanforderung.The proposed refrigerant circuit consists of a swash plate compressor (Compressor), at the outlet of which a high pressure section with a gas cooler or Refrigerant condenser and on its suction side (compressor inlet) Low pressure section are connected to an evaporator, and the High pressure section with adjustable connecting the low pressure section Expansion device, which are connected to each other by a refrigerant line, and a control valve on the suction side of the compressor, through which the refrigerant is sucked back into this, being in front of the inlet of the evaporator Temperature sensor or a pressure sensor in the suction line in front of the compressor is arranged, the control electronics with the actuator of the control valve in There is an operative connection, and that the tilt-adjustable swash plate, the control valve and the respective sensor form a suction pressure control circuit. The control valve is a 3-way valve with a suction pressure, a high pressure and a Crank chamber connection. The temperature sensor measures the saturation temperature at Evaporator input from which is stored in a control electronics Vapor pressure curve of the respective refrigerant, the evaporator pressure and thus also the Suction pressure is determined. This eliminates the need for complicated and time-consuming regulation several sensors. Instead of a pressure sensor in the suction line, the Compressor a temperature sensor used in front of the evaporator inlet, because of this is cheaper. The control strategy provides that the suction pressure is independent of keep the speed of the compressor constant. This means that the piston stroke at high engine and thus compressor speeds are low and at maximum when idling. The refrigerant circuit controlled in this way enables rapid adjustment of the Compressor output for the respective cooling requirement.

Das Regelventil ist bevorzugt ein pulsbreitenmoduliertes 3-Wege-Ventil mit einem elektromagnetischen Stellantrieb, der eine kurze Reaktionszeit hat.The control valve is preferably a 3-way valve with a pulse width modulation electromagnetic actuator that has a short response time.

In der Ausgangsleitung des Kältemittelverflüssigers kann ein innerer Wärmetauscher mit der Saugleitung des Kompressors gebildet sein, durch den das unter Hochdruck stehende gekühlte Kältemittel zum Expansionsorgan und das entspannte und dampfförmige Kältemittel zum Kompressor geleitet werden, so daß eine Abkühlung des zu entspannenden und zu verdampfenden Kältemittels erfolgt, mit der Konsequenz, daß der Flüssigkeitsanteil des Kältemittels nach der Expansion steigt und somit mehr flüssiges Kältemittel zur Verfügung steht. Der innere Wärmetauscher erhöht damit die Kälteleistung und auch die Effizienz des Kältekreislaufs. Aber auch wegen der schnellen Änderung der Betriebsbedingungen ist ein innerer Wärmetauscher vorteilhaft. Diese Ausführung mit einem inneren Wärmetauscher eignet sich insbesondere für CO2-Kältemittel.An internal heat exchanger with the suction line of the compressor can be formed in the outlet line of the refrigerant condenser, through which the high-pressure cooled refrigerant is led to the expansion element and the expanded and vaporous refrigerant is led to the compressor, so that the refrigerant to be expanded and evaporated is cooled , with the consequence that the liquid portion of the refrigerant increases after the expansion and thus more liquid refrigerant is available. The internal heat exchanger thus increases the cooling capacity and also the efficiency of the cooling circuit. An internal heat exchanger is also advantageous because of the rapid change in operating conditions. This version with an internal heat exchanger is particularly suitable for CO 2 refrigerants.

Als Expansionsorgan wird vorteilhafterweise ein themostatisches Expansionsventil eingesetzt. Im Anfahrzustand der Klimaanlage ist die Überhitzung am Verdampferausgang erhöht, so daß das Expansionsventil weit öffnet und der Kältemittelmassenstrom erhöht wird, wodurch in kürzester Zeit die maximale Kälteleistung erreicht wird.A thematic expansion valve is advantageously used as the expansion organ used. When the air conditioner starts up, overheating is on Evaporator outlet increased so that the expansion valve opens wide and the Refrigerant mass flow is increased, making the maximum in the shortest possible time Cooling capacity is achieved.

Die Erfindung wird nachstehend anhand eines Ausführungsbeispiels für eine insbesondere mit CO2-Kältemittel betriebene Kraftfahrzeug-Klimaanlage erläutert. Die zugehörigen Zeichnungen zeigen:

Fig.1:
den Kältemittelkreislauf der Klimaanlage und
Fig. 2:
die CO2-Dampfdruckkurve.
The invention is explained below using an exemplary embodiment of a motor vehicle air conditioning system operated in particular with CO 2 refrigerant. The associated drawings show:
Fig.1:
the refrigerant circuit of the air conditioning system and
Fig. 2:
the CO 2 vapor pressure curve.

Dieser Kältemittelkreislauf weist in Kreislaufrichtung nacheinander einen Taumelscheibenkompressor 1, einen Gaskühler (Kältemittelverflüssiger) 2, einen inneren Wärmetauscher 3 mit einer ersten Kältemittel-Leitungsschlange 3.1, ein thermostatisches Expansionsventil 4 bekannter Bauart mit einem thermostatischen Sensor 5, einen Verdampfer 6, an dessen Ausgang der Sensor 5 angeordnet ist, einen Flüssigkeitssammler 7 und den Wärmetauscher 3 mit einer zweiten Kältemittel-Leitungsschlange 3.2 vor dem Kompressor 1 auf. Im Ventildeckel an der Saugseite des Kompressors 1 ist ein 3-Wege-Regelventil 8 angeordnet, über das das Kältemittel in diesen gesaugt wird. Dieses Regelventil 8 weist einen Anschluß 8.1 an die Saugkammer des Kompressors 1, einen Anschluß 8.2 an dessen Hochdruckkammer, einen Anschluß 8.3 an dessen Kurbelkammer und ein nicht weiter dargestelltes elektromagnetisches Stellglied 8.4 auf, das mit diesen Anschlüssen 8.1 bis 8.3 in Wirkverbindung steht. Das Stellglied 8.4 ist an eine Regelelektronik 9 angeschlossen, in der die CO2-Dampfdruckkurve abgelegt ist und die als Eingangsgröße die am Eingang des Verdampfers 6 gegebene Sättigungstemperatur des Kältemittels von einem dort angeordneten Temperatursensor 10 empfängt.This refrigerant circuit has a swash plate compressor 1, a gas cooler (refrigerant condenser) 2, an inner heat exchanger 3 with a first refrigerant line coil 3.1, a thermostatic expansion valve 4 of known type with a thermostatic sensor 5, an evaporator 6, at the outlet of which the sensor 5 is arranged, a liquid collector 7 and the heat exchanger 3 with a second refrigerant line coil 3.2 in front of the compressor 1. A 3-way control valve 8 is arranged in the valve cover on the suction side of the compressor 1, via which the refrigerant is sucked into the latter. This control valve 8 has a connection 8.1 to the suction chamber of the compressor 1, a connection 8.2 to its high pressure chamber, a connection 8.3 to its crank chamber and an electromagnetic actuator 8.4 (not shown further), which is operatively connected to these connections 8.1 to 8.3. The actuator 8.4 is connected to control electronics 9, in which the CO 2 vapor pressure curve is stored and which receives as an input variable the saturation temperature of the refrigerant at the inlet of the evaporator 6 from a temperature sensor 10 arranged there.

Das CO2-Kältemittel, das auf der Saugseite des Kompressors 1 einen Druck von etwa 35 bis 45 bar und eine Temperatur von ca. 20° C aufweist, wird im Kompressor 1 auf einen Druck von im wesentlichen 110 bar verdichtet, wobei die Temperatur des Kältemittels auf ca. 100°C steigt. Im Gaskühler 2 wird das Kältemittel durch vorbeiströmende Außenluft auf ca. 55° bis 60°C abgekühlt und dabei verflüssigt. Die dem CO2-Kältemittel entnommene Wärme wird mit der Außenluft abgeführt. Im inneren Wärmetauscher 3 gibt das durch die Leitungsschlange 3.1 strömende CO2-Kältemittel Wärme an das durch die Leitungsschlange 3.2 strömende The CO 2 refrigerant, which has a pressure of approximately 35 to 45 bar and a temperature of approximately 20 ° C. on the suction side of the compressor 1, is compressed in the compressor 1 to a pressure of essentially 110 bar, the temperature of the Refrigerant rises to approx. 100 ° C. In the gas cooler 2, the refrigerant is cooled to approx. 55 ° to 60 ° C by the outside air flowing past and liquefied in the process. The heat extracted from the CO 2 refrigerant is dissipated with the outside air. In the inner heat exchanger 3, the CO 2 refrigerant flowing through the line coil 3.1 gives heat to the one flowing through the line coil 3.2

Kältemittel ab, die in die Saugleitung des Kompressors integriert ist, wobei es auf eine Temperatur von im wesentlichen 25°C abgekühlt wird. Im Expansionsventil 4 wird das flüssige CO2-Kältemittel, das auf der Hochdruckseite einen Druck von etwa 110 bar und eine Temperatur von im wesentlichen 25°C aufweist, in den Naßdampfzustand überführt, wobei es auf einen Druck von 35 bis 45 bar entspannt und auf eine Temperatur von 0° bis 10°C abgekühlt wird. Mit diesem Zustand gelangt das CO2-Kältemittel in den Verdampfer 6, in dem es durch Wärmeaufnahme von der zu kühlenden Außen- oder Umluft für den Fahrgastraum bei einem gleichbleibendem Druck von 35 bis 45 bar, der dem Saugdruck am Kompressor 1 entspricht, verdampft. Das Expansionsventil 4 als verstellbares Massenstromventil wird dabei so eingestellt, daß der zum Kühlen der Luft das Expansionsventil 4 passierende Kältemittel-Massenstrom so eingestellt ist, daß das Kältemittel im Verdampfer 6 möglichst vollständig in den gasförmigen Zustand überführt wird und am Verdampferausgang um etwa 2° bis 4°C überhitzt ist. Anschließend durchströmt das gasförmige Kältemittel den Flüssigkeitssammler 7, um Reste flüssigen Kältemittels zurückzuhalten.Refrigerant from, which is integrated in the suction line of the compressor, wherein it is cooled to a temperature of substantially 25 ° C. In the expansion valve 4, the liquid CO 2 refrigerant, which has a pressure of about 110 bar and a temperature of essentially 25 ° C. on the high pressure side, is converted into the wet vapor state, where it is expanded and released to a pressure of 35 to 45 bar a temperature of 0 ° to 10 ° C is cooled. With this state, the CO 2 refrigerant enters the evaporator 6, where it evaporates by absorbing heat from the outside or recirculated air to be cooled for the passenger compartment at a constant pressure of 35 to 45 bar, which corresponds to the suction pressure at the compressor 1. The expansion valve 4 as an adjustable mass flow valve is set so that the refrigerant mass flow passing through the expansion valve 4 for cooling the air is set so that the refrigerant in the evaporator 6 is converted as completely as possible into the gaseous state and at the evaporator outlet by about 2 ° to 4 ° C is overheated. The gaseous refrigerant then flows through the liquid collector 7 in order to retain residues of liquid refrigerant.

Am Verdampfereingang liegt gesättigter CO2-Naßdampf vor, dessen Sättigungstemperatur von der Leistung des Kompressors 1 abhängig ist. Wenn der Kompressor 1 infolge einer hohen Drehzahl des Fahrzeugmotors, mit dem er gekoppelt ist, einen hohen CO2-Massenstrom und eine größere Kälteleistung als die Soll-Kälteleistung erzeugt, fällt die Sättigungstemperatur am Verdampfereingang und damit auch der Sättigungsdruck. Um den Massenstrom und damit die Kälteleistung des Kompressors 1 zu reduzieren, muß der Kolbenhub in diesem verringert werden. Das geschieht mit Hilfe der zentralen Regelelektronik 9 und des pulsbreitenmodulierten Regelventils 8, das mit der zentralen Regelelektronik 9 gekoppelt ist, die die Sättigungstemperatur des CO-Kältemittels vom Temperatursensor 10 empfängt.Saturated wet CO 2 is present at the evaporator inlet, the saturation temperature of which depends on the output of the compressor 1. If the compressor 1 generates a high CO 2 mass flow and a greater cooling capacity than the target cooling capacity due to a high speed of the vehicle engine with which it is coupled, the saturation temperature at the evaporator inlet and thus also the saturation pressure drop. In order to reduce the mass flow and thus the cooling capacity of the compressor 1, the piston stroke in this must be reduced. This is done with the help of the central control electronics 9 and the pulse-width-modulated control valve 8, which is coupled to the central control electronics 9, which receives the saturation temperature of the CO refrigerant from the temperature sensor 10.

Über das Regelventil 8 wird nach der diesem Regelverfahren zugrundeliegenden Regelphilosophie der Saugdruck im Kompressor 1 im wesentlichen konstant gehalten, unabhängig von der Drehzahl des Kompressors. Um den Kolbenhub im Kompressor 1 zu reduzieren, muß die Neigung der Taumelscheibe in diesem verringert werden. Das geschieht durch eine Änderung der Druckdifferenz zwischen dem Druck in der Kurbelkammer und dem Druck in der Ansaugkammer des Kompressors 1. Bei gleichbleibendem Druck in der Ansaugkammer muß demzufolge der Druck in der Kurbelkammer erhöht werden, um die Neigung der Taumelscheibe und den Kolbenhub zu verringern. Dazu wird das Stellglied 8.4 des Regelventils 8 durch die Regelelektronik 9 so verstellt, das aus dem Hochdruckkammer-Anschluß 8.2 gasförmiges CO2-Kältemittel in den Kurbelraum des Kompressors 1 gedrückt wird. According to the control philosophy on which this control method is based, the suction pressure in the compressor 1 is kept essentially constant, regardless of the speed of the compressor, via the control valve 8. In order to reduce the piston stroke in the compressor 1, the inclination of the swash plate in this must be reduced. This is done by changing the pressure difference between the pressure in the crank chamber and the pressure in the suction chamber of the compressor 1. Consequently, with the pressure in the suction chamber remaining constant, the pressure in the crank chamber must be increased in order to reduce the inclination of the swash plate and the piston stroke. For this purpose, the actuator 8.4 of the control valve 8 is adjusted by the control electronics 9 so that gaseous CO 2 refrigerant is pressed into the crank chamber of the compressor 1 from the high-pressure chamber connection 8.2.

BEZUGSZEICHENLISTELIST OF REFERENCE NUMBERS

11
Kompressorcompressor
22
Gaskühlergas cooler
33
Wärmetauscherheat exchangers
3.13.1
Kältemittel-LeitungsschlangeRefrigerant piping snake
3.23.2
Kältemittel-LeitungsschlangeRefrigerant piping snake
44
Expansionsventilexpansion valve
55
Sensorsensor
66
VerdampferEvaporator
77
Flüssigkeitssammlerliquid receiver
88th
3-Wege-Regelventil3-way control valve
8.18.1
Saugkammer-AnschlußSuction port
8.28.2
Hochdruckkammer-AnschlußHigh-pressure chamber connection
8.38.3
Kurbelkammer-AnschlußCrank chamber connection
8.48.4
Stellgliedactuator
99
Regelelektronikcontrol electronics
1010
Temperatursensortemperature sensor

Claims (9)

Kältemittelkreislauf mit einem geregelten Taumelscheibenkompressor, bei dem das Kältemittel nacheinander einen regelbaren Taumelscheibenkompressor, einen Kältemittelkühler als Kältemittelverflüssiger, ein den Kältemittelfluß regelndes Expansionsorgan und einen Verdampfer, die jeweils durch eine Kältemittelleitung miteinander verbunden sind, durchströmt, und über ein Regelventil wieder in den Kompressor gesaugt wird, dadurch gekennzeichnet, daß das Regelventil (8) ein 3-Wege-Regelventil mit einem Saugdruck- (8.1), einem Hochdruck- (8.2) und einem Kurbelkammeranschluß (8.3) ist, daß vor dem Eingang des Verdampfers (6) ein Temperaturfühler (10) oder in der Saugleitung vor dem Taumelscheibenkompressor (1) ein Drucksensor angeordnet ist, der über eine Regelelektronik (9) mit dem Stellantrieb (8.4) des Regelventils (8) in Wirkverbindung steht, und daß die neigungsverstellbare Taumelscheibe des Taumelscheibenkompressors (1), das Regelventil (8) und der Temperaturfühler (10) oder der Drucksensor einen Saugdruckregelkreis ausbilden.Refrigerant circuit with a regulated swash plate compressor, in which the refrigerant successively a controllable swash plate compressor, a refrigerant cooler as a refrigerant condenser, an expansion element regulating the refrigerant flow and an evaporator, which are each connected to one another by a refrigerant line, are again flowed through, into the compressor, and via a control valve , characterized in that the control valve (8) is a 3-way control valve with a suction pressure (8.1), a high pressure (8.2) and a crank chamber connection (8.3), that a temperature sensor (6) in front of the inlet of the evaporator (6) 10) or in the suction line in front of the swash plate compressor (1), a pressure sensor is arranged, which is connected to the actuator (8.4) of the control valve (8) via control electronics (9), and that the inclinable swash plate of the swash plate compressor (1), the control valve (8) and the temperature sensor (10) or the pressure sensor form a suction pressure control circuit. Kältemittelkreislauf nach Anspruch 1, dadurch gekennzeichnet, daß das Regelventil (8) ein pulsbreitenmoduliertes 3-Wege-Ventil ist.Refrigerant circuit according to claim 1, characterized in that the control valve (8) is a pulse width modulated 3-way valve. Kältemittelkreislauf nach Anspruch 1, dadurch gekennzeichnet, daß das Regelventil (8) einen elektromagnetischen Stellantrieb (8.4) aufweist.Refrigerant circuit according to claim 1, characterized in that the control valve (8) has an electromagnetic actuator (8.4). Kältemittelkreislauf nach Anspruch 1, dadurch gekennzeichnet, daß in der Ausgangsleitung des Kältemittelverflüssigers (2) ein innerer Wärmetauscher (3) mit der Saugleitung des Kompressors (1) gebildet ist.Refrigerant circuit according to claim 1, characterized in that an internal heat exchanger (3) with the suction line of the compressor (1) is formed in the outlet line of the refrigerant condenser (2). Kältemittelkreislauf nach Anspruch 1, dadurch gekennzeichnet, daß das Expansionsorgan ein thermostatisches Expansionsventil (4) ist.Refrigerant circuit according to claim 1, characterized in that the expansion element is a thermostatic expansion valve (4). Kältemittelkreislauf nach Anspruch 1, dadurch gekennzeichnet, daß zwischen dem Ausgang des Verdampfers (6) und dem inneren Wärmetauscher (3) ein Flüssigkeitssammler (7) angeordnet ist. Refrigerant circuit according to claim 1, characterized in that a liquid collector (7) is arranged between the outlet of the evaporator (6) and the inner heat exchanger (3). Verfahren zum Betreiben einer Kfz-Klimaanlage mit einem Kältemittelkreislauf, bei dem gasförmiges Kältemittel in einem geregelten Taumelscheibenkompressor (1) verdichtet und erwärmt wird, durch einen Wärmetauscher (3) gefördert, in diesem abgekühlt und verflüssigt wird, danach in einem Expansionsorgan (4) entspannt und in einem als Wärmetauscher genutzten Verdampfer (6) wieder in den gasförmigen Zustand versetzt und vom Taumelscheibenkompressor (1) angesaugt wird, wobei die Leistungsregelung des Taumelscheibenkompressors (1) über ein Regelventil (8) erfolgt, das die Differenz zwischen dem Druck in der Kurbelkammer und dem Druck in der Ansaugkammer des Taumelscheibenkompressors regelt und dadurch die Neigung der Taumelscheibe verändert wird, dadurch gekennzeichnet, daß der Saugdruck über die Sättungstemperatur am Eingang des Verdampfers (6) ermittelt wird, wobei ein Temperaturfühler (10) die Sättigungstemperatur erfaßt und der Verdampferdruck über eine in einer Regelelektronik (9) abgelegte Dampfdruckkurve bestimmt wird.Method for operating a motor vehicle air conditioning system with a refrigerant circuit, in which gaseous refrigerant is compressed and heated in a regulated swash plate compressor (1), conveyed through a heat exchanger (3), cooled and liquefied in it, and then expanded in an expansion device (4) and in an evaporator (6) used as a heat exchanger is brought back into the gaseous state and is sucked in by the swash plate compressor (1), the output regulation of the swash plate compressor (1) taking place via a control valve (8) which measures the difference between the pressure in the crank chamber and regulates the pressure in the suction chamber of the swash plate compressor and thereby changes the inclination of the swash plate, characterized in that the suction pressure is determined via the saturation temperature at the inlet of the evaporator (6), a temperature sensor (10) detecting the saturation temperature and the evaporator pressure above one in a rule electronics (9) stored vapor pressure curve is determined. Verfahren nach Anspruch 5 oder 6, dadurch gekennzeichnet, daß zwischen dem vom Taumelscheibenkompressor (1) angesaugten gasförmigen Kältemittel und dem durch das im Kältemittelverflüssiger (2) gekühlten Kältemittel ein Wärmeaustausch stattfindet.Method according to Claim 5 or 6, characterized in that a heat exchange takes place between the gaseous refrigerant sucked in by the swash plate compressor (1) and the refrigerant cooled by the refrigerant in the condenser (2). Verfahren nach Anspruch 8, dadurch gekennzeichnet, daß das Kältemittel R744 (CO2-Kältemittel) ist.A method according to claim 8, characterized in that the refrigerant is R744 (CO 2 refrigerant).
EP04000690A 2003-02-15 2004-01-15 Refrigerant circuit with a controlled swash-plate type compressor Withdrawn EP1450041A1 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102261773A (en) * 2010-05-24 2011-11-30 上海日立电器有限公司 Heat pump water heater system

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5694784A (en) * 1995-05-10 1997-12-09 Tes Wankel Technische Forschungs-Und Entwicklungsstelle Lindau Gmbh Vehicle air conditioning system
US5964578A (en) * 1996-04-01 1999-10-12 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Control valve in variable displacement compressor
EP0952412A2 (en) * 1998-04-16 1999-10-27 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Refrigerating system and method of operating the same
EP1114932A2 (en) * 2000-01-07 2001-07-11 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Control device of variable displacement compressor

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0717151B2 (en) * 1987-07-04 1995-03-01 株式会社豊田自動織機製作所 Variable capacity compressor operation control method
JPH01175517A (en) * 1987-12-28 1989-07-12 Diesel Kiki Co Ltd Air conditioner for vehicle
NO890076D0 (en) * 1989-01-09 1989-01-09 Sinvent As AIR CONDITIONING.
KR950003458Y1 (en) * 1990-11-29 1995-05-02 가부시끼가이샤 도요다지도쇽끼 세이사꾸쇼 Swash plate compressor
CH690189A5 (en) * 1995-03-10 2000-05-31 Daimler Benz Ag A method for controlling the power of a system for cooling the passenger compartment of a motor vehicle.
DE10135727B4 (en) * 2001-07-21 2019-07-04 Volkswagen Ag Control valve fed with AC voltage and swash plate compressor with this control valve

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5694784A (en) * 1995-05-10 1997-12-09 Tes Wankel Technische Forschungs-Und Entwicklungsstelle Lindau Gmbh Vehicle air conditioning system
US5964578A (en) * 1996-04-01 1999-10-12 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Control valve in variable displacement compressor
EP0952412A2 (en) * 1998-04-16 1999-10-27 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Refrigerating system and method of operating the same
EP1114932A2 (en) * 2000-01-07 2001-07-11 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Control device of variable displacement compressor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102261773A (en) * 2010-05-24 2011-11-30 上海日立电器有限公司 Heat pump water heater system

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