WO2005108881A1 - Air-conditioning compressor - Google Patents

Air-conditioning compressor Download PDF

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Publication number
WO2005108881A1
WO2005108881A1 PCT/DE2005/000778 DE2005000778W WO2005108881A1 WO 2005108881 A1 WO2005108881 A1 WO 2005108881A1 DE 2005000778 W DE2005000778 W DE 2005000778W WO 2005108881 A1 WO2005108881 A1 WO 2005108881A1
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WO
WIPO (PCT)
Prior art keywords
flow
air conditioning
conditioning compressor
oil separator
gas
Prior art date
Application number
PCT/DE2005/000778
Other languages
German (de)
French (fr)
Inventor
Tilo SCHÄFER
Thomas Di Vito
Frank Obrist
Original Assignee
Luk Fahrzeug-Hydraulik Gmbh & Co. Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Luk Fahrzeug-Hydraulik Gmbh & Co. Kg filed Critical Luk Fahrzeug-Hydraulik Gmbh & Co. Kg
Priority to DE112005001636T priority Critical patent/DE112005001636A5/en
Publication of WO2005108881A1 publication Critical patent/WO2005108881A1/en

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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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements

Definitions

  • the invention relates to an air conditioning compressor with a refrigerant intake flow and a refrigerant outlet flow and with an oil separator which is arranged in the outlet flow area, a refrigerant flow being branched off from the outlet flow in the area of the oil separator and being supplied to the drive room.
  • Air conditioning compressors of this type are known.
  • the hot outlet gas from the air conditioning compressors contains lubricant that can be separated from the main outlet flow with a separator.
  • the hot, high-pressure lubricant-gas mixture separated there is fed, for example, to a control valve in which it is throttled to the level of the engine compartment.
  • the lubricant-gas mixture cools down, but due to the residual heat that is present, it will still contribute to a considerable warming of the drive room.
  • the invention has for its object to provide an air conditioning compressor that does not have these disadvantages.
  • the object is achieved by an air conditioning compressor with a refrigerant intake flow and a refrigerant outlet flow and with an oil separator which is arranged in the outlet flow area and in which a refrigerant flow is branched off from the outlet flow in the area of the oil separator and is fed to the drive room, the drive room flow using a heat exchanger -Device is cooled by the intake flow.
  • This has the advantage that only a small gas flow, namely the drive room flow, is cooled by the cool intake flow.
  • An air conditioning compressor is characterized in that the heat exchanger device is arranged between the oil separator and a resistor in the supply of the drive room.
  • An air conditioning compressor in which the resistance is adjustable is preferred and is represented, for example, by a valve, in particular a control valve. This has the advantage that a cooler lubricant-gas mixture is fed to the control valve and the valve can thus implement a higher electrical output, since the lower temperatures mean that the electrical resistance of, for example, solenoid coils is lower and therefore lower for the same output Streams are enough.
  • an air conditioning compressor in which the remaining outlet flow is discharged from the compressor in a substantially thermally insulated manner from the intake flow.
  • An air conditioning compressor is characterized in that the heat exchanger device is represented by a separate line, for example by a tube or a groove or a channel, in the housing parts of the air conditioning compressor.
  • This has the advantage that this separate line, which is adjacent to the air conditioning compressor areas through which the cool intake gas flows or is arranged within these areas, enables optimum heat transfer without the two gas areas mixing together.
  • a sufficient section length can be provided for the heat exchanger device and the cooled mixture which is fed to the drive chamber there contributes considerably to lowering the operating temperature of the air conditioning compressor.
  • an air conditioning compressor is preferred in which the drive chamber flow supplied is throttled to the drive chamber pressure by the resistor, for example by the valve. This means that the lubricant-gas mixture cooled in this way continues to cool down due to the isenthalpic expansion of the gas content it contains and thus contributes significantly to lowering the operating temperature.
  • An air conditioning compressor is also preferred, in which the drive room flow supplied has a particularly lubricant-rich phase of the gas (higher density). This has the advantage that the lubricant is decidedly cooler than in known machines and can therefore be effective in the machine's drive area with better lubricating properties.
  • Figure 1 shows schematically an air conditioning compressor with the heat exchanger device according to the invention.
  • Figure 2 shows a component of an air conditioning compressor with the heat exchanger device according to the invention.
  • an air conditioning compressor 1 which sucks in a refrigerant intake flow 3 and, after compression, conducts a refrigerant outlet flow 5 into an oil separator 7, shown schematically.
  • the outlet flow is divided into a main flow 9, which is fed to the air conditioning system, and a decidedly smaller drive chamber flow 11, which absorbs the lubricant separated in the oil separator 7 and leads into the schematically illustrated drive chamber 13 of the compressor 1.
  • a fluid resistance such as.
  • a schematically illustrated control valve 15 is arranged in the conduction area of the engine room flow 11 in the conduction area of the engine room flow 11 in the conduction area of the engine room flow 11 in the conduction area of the engine room flow 11 in the conduction area of the engine room flow 11 a fluid resistance such as. B. a schematically illustrated control valve 15 is arranged.
  • a heat exchanger device 17 shown here by a dashed oval, is arranged, in which a line part 19 of the drive room flow 11 runs together with a line part 21 of the intake flow 3 over a heat exchange path, so that this approximately refrigerant drawn in at a temperature of 30 ° Celsius can cool down the decidedly smaller refrigerant flow that is led into the drive room.
  • the lubricant-gas mixture cooled in this way is throttled in the control valve 15 to the level of the engine room, where it cools down further due to the isenthalpic expansion of the gas component contained. This cooled mixture is fed to the drive room 13 and there contributes considerably to lowering the operating temperature.
  • a lower temperature in the machine's oil sump also minimizes wear and reduces the thermal aging of the lubricant.
  • the heat is only selectively exchanged between the medium that is supplied to the compressor, that is to say the intake flow, and the medium that leaves a device for separating oil as a higher-density phase, that is to say the drive chamber flow.
  • FIG. 2 shows, by way of example, a cross-section of a component of the compressor according to the invention, which can represent, for example, a cylinder head of a compressor.
  • the cylinder head has an outer wall 30, within which there is a pressure area for the intake gas, area 32.
  • the intake gas area 32 is separated radially inwards by a further wall 34.
  • the outlet gas region 36 is separated from the inside by a further intermediate wall 38.
  • a line 42 here in the form of a tube, is now shown within the intake gas pressure area 32, which is derived, for example, from the oil separator 7 from FIG. 1 via a connection 44 and, after a certain length, within the intake gas area 32 through the connection 46 the control valve 15 of Figure 1 is supplied.
  • This tube 42 therefore forms a heat exchanger device with the intake gas region 32, by means of which the cool intake gas in the region 32 can cool the small mass flow of the drive space flow in the tube 42.
  • the outlet pressure region 36 which is located within the partition wall 34, has a considerably higher temperature at approximately> 100 ° Celsius and can advantageously be thermally separated from the suction region 32 by appropriate measures due to the short circumferential length of the wall 34, such as e.g. B.
  • the small oil separator gas stream 11 that is to say the gas stream to the drive chamber 13, does not substantially heat up the intake gas, while the main gas stream 5 to the outlet is as much as possible well insulated from this medium to prevent harmful warming up of the intake gas.
  • the hot engine oil-gas mixture is cooled before throttling and thus also the control valve 15, which in most cases is an electromagnetic valve, with a better efficiency and with a better utilization of the electrical due to the cooler working range Performance can work.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Abstract

The invention relates to an air conditioning compressor comprising a coolant suction flow, a coolant discharge flow, and an oil separator which is arranged in the discharge flow region. According to the invention, a coolant flow is branched off the discharge flow in the oil separator, and supplied to the driving chamber.

Description

Klimakompressor air compressor
Die Erfindung betrifft einen Klimakompressor mit einem Kältemittel-Ansaugstrom und einem Kältemittel-Auslassstrom und mit einem Ölabscheider, welcher im Auslassstrombereich ange- ordnet ist, wobei im Bereich des Olabscheiders ein Kältemittelstrom vom Auslassstrom abgezweigt und dem Triebraum zugeführt wird.The invention relates to an air conditioning compressor with a refrigerant intake flow and a refrigerant outlet flow and with an oil separator which is arranged in the outlet flow area, a refrigerant flow being branched off from the outlet flow in the area of the oil separator and being supplied to the drive room.
Derartige Klimakompressoren sind bekannt. Das heiße Auslassgas der Klimakompressoren enthält Schmierstoff, der mit einem Abscheider vom Hauptauslassstrom getrennt werden kann. Das dort abgeschiedene heiße, unter hohem Druck stehende Schmierstoff-Gas-Gemisch wird beispielsweise einem Regelventil zugeführt, in welchem es auf das Triebraumdruckniveau gedrosselt wird. Dabei kühlt sich das Schmierstoff-Gas-Gemisch zwar ab, wird aber aufgrund der vorhandenen Restwärme immer noch zu einer erheblichen Erwärmung des Triebraumes beitragen.Air conditioning compressors of this type are known. The hot outlet gas from the air conditioning compressors contains lubricant that can be separated from the main outlet flow with a separator. The hot, high-pressure lubricant-gas mixture separated there is fed, for example, to a control valve in which it is throttled to the level of the engine compartment. The lubricant-gas mixture cools down, but due to the residual heat that is present, it will still contribute to a considerable warming of the drive room.
Alternativ gibt es Klimakompressorkonzepte, wo man versucht, größere Teile der Maschine direkt mit dem kalten Sauggas in Verbindung zu bringen. Dies hat den Nachteil, dass sich das Sauggas zu stark erwärmt, was zur Wirkungsgradreduzierung beiträgt und die Temperatur des Auslassgases deutlich steigen lässt. Dadurch wird der erzielte Kühleffekt zum Teil wieder zu- nichte gemacht.Alternatively, there are air conditioning compressor concepts, in which attempts are made to connect larger parts of the machine directly to the cold suction gas. This has the disadvantage that the suction gas heats up too much, which contributes to a reduction in efficiency and the temperature of the outlet gas can rise significantly. As a result, the cooling effect achieved is partially negated.
Der Erfindung liegt die Aufgabe zugrunde, einen Klimakompressor zu schaffen, der diese Nachteile nicht aufweist.The invention has for its object to provide an air conditioning compressor that does not have these disadvantages.
Die Aufgabe wird gelöst durch einen Klimakompressor mit einem Kältemittel-Ansaugstrom und einem Kältemittel-Auslassstrom und mit einem Ölabscheider, welcher im Auslassstrombereich angeordnet ist und wobei im Bereich des Olabscheiders ein Kältemittelstrom vom Auslassstrom abgezweigt und dem Triebraum zugeführt wird, wobei der Triebraumstrom mittels einer Wärmetauscher-Vorrichtung vom Ansaugstrom gekühlt wird. Das hat den Vorteil, dass nur ein kleiner Gasstrom, nämlich der Triebraumstrom, vom kühlen Ansaugstrom gekühlt wird.The object is achieved by an air conditioning compressor with a refrigerant intake flow and a refrigerant outlet flow and with an oil separator which is arranged in the outlet flow area and in which a refrigerant flow is branched off from the outlet flow in the area of the oil separator and is fed to the drive room, the drive room flow using a heat exchanger -Device is cooled by the intake flow. This has the advantage that only a small gas flow, namely the drive room flow, is cooled by the cool intake flow.
Ein erfindungsgemäßer Klimakompressor zeichnet sich dadurch aus, dass die Wärmetauschervorrichtung zwischen dem Ölabscheider und einem Widerstand im zugeführten Triebraumstrom angeordnet ist. Bevorzugt wird ein Klimakompressor, bei welchem der Widerstand verstellbar dargestellt ist und beispielsweise durch ein Ventil, insbesondere ein Regelventil, dargestellt ist. Das hat den Vorteil, dass dem Regelventil ein kühleres Schmierstoff-Gas-Gemisch zugeführt wird und das Ventil dadurch eine höhere elektrische Leistung umsetzen kann, da durch die niedrigeren Temperaturen der elektrische Widerstand beispielsweise von Magnetspulen nie- driger ist und deswegen für die gleiche Leistung niedrigere Ströme genügen. Bevorzugt wird weiterhin ein Klimakompressor, bei welchem der restliche Auslassstrom gegenüber dem Ansaugstrom im Wesentlichen thermisch isoliert aus dem Kompressor abgeführt wird.An air conditioning compressor according to the invention is characterized in that the heat exchanger device is arranged between the oil separator and a resistor in the supply of the drive room. An air conditioning compressor in which the resistance is adjustable is preferred and is represented, for example, by a valve, in particular a control valve. This has the advantage that a cooler lubricant-gas mixture is fed to the control valve and the valve can thus implement a higher electrical output, since the lower temperatures mean that the electrical resistance of, for example, solenoid coils is lower and therefore lower for the same output Streams are enough. Also preferred is an air conditioning compressor in which the remaining outlet flow is discharged from the compressor in a substantially thermally insulated manner from the intake flow.
Das hat den Vorteil, dass ein schädliches Aufwärmen des Ansauggases durch die Wärme- menge des Auslassgases verhindert werden kann.This has the advantage that harmful warm-up of the intake gas can be prevented by the heat quantity of the exhaust gas.
Ein erfindungsgemäßer Klimakompressor zeichnet sich dadurch aus, dass die Wärmetauschervorrichtung durch eine separate Leitung, beispielsweise durch ein Röhrchen oder eine Nut oder einen Kanal, in den Gehäuseteilen des Klimakompressors dargestellt ist. Das hat den Vorteil, dass durch diese separate Leitung, welche an die vom kühlen Ansauggas durchströmten Klimakompressorbereiche angrenzt oder innerhalb dieser Bereiche angeordnet ist, ein optimaler Wärmeübergang ermöglicht wird, ohne dass sich die beiden Gasbereiche miteinander vermischen. Auch ergibt sich der Vorteil, dass eine ausreichende Streckenlänge für die Wärmetauschereinrichtung bereitgestellt werden kann und das gekühlte Gemisch, welches dem Triebraum zu- geführt wird, dort erheblich zur Senkung der Betriebstemperatur des Klimakompressors beiträgt.An air conditioning compressor according to the invention is characterized in that the heat exchanger device is represented by a separate line, for example by a tube or a groove or a channel, in the housing parts of the air conditioning compressor. This has the advantage that this separate line, which is adjacent to the air conditioning compressor areas through which the cool intake gas flows or is arranged within these areas, enables optimum heat transfer without the two gas areas mixing together. There is also the advantage that a sufficient section length can be provided for the heat exchanger device and the cooled mixture which is fed to the drive chamber there contributes considerably to lowering the operating temperature of the air conditioning compressor.
Weiterhin wird ein Klimakompressor bevorzugt, bei welchem der zugeführte Triebraumstrom durch den Widerstand, beispielsweise durch das Ventil, auf den Triebraumdruck gedrosselt wird. Das bedeutet, dass das auf diese Weise gekühlte Schmierstoff-Gas-Gemisch durch isenthalpe Expansion des enthaltenen Gasanteils weiter abkühlt und somit erheblich zur Senkung der Betriebstemperatur beiträgt.Furthermore, an air conditioning compressor is preferred in which the drive chamber flow supplied is throttled to the drive chamber pressure by the resistor, for example by the valve. This means that the lubricant-gas mixture cooled in this way continues to cool down due to the isenthalpic expansion of the gas content it contains and thus contributes significantly to lowering the operating temperature.
Auch wird ein Klimakompressor bevorzugt, bei welchem der zugeführte Triebraumstrom eine besonders schmierstoffreiche Phase des Gases aufweist (höhere Dichte). Das hat den Vorteil, dass der Schmierstoff entschieden kühler als bei bekannten Maschinen ist und deswegen mit besseren Schmiereigenschaften im Triebraum der Maschine wirksam werden kann.An air conditioning compressor is also preferred, in which the drive room flow supplied has a particularly lubricant-rich phase of the gas (higher density). This has the advantage that the lubricant is decidedly cooler than in known machines and can therefore be effective in the machine's drive area with better lubricating properties.
Die Erfindung wird nun anhand der Figuren beschrieben. Figur 1 zeigt schematisch einen Klimakompressor mit der erfindungsgemäßen Wärmetauschereinrichtung.The invention will now be described with reference to the figures. Figure 1 shows schematically an air conditioning compressor with the heat exchanger device according to the invention.
Figur 2 zeigt ein Bauteil eines Klimakompressors mit der erfindungsgemäßen Wärmetauscher- Vorrichtung.Figure 2 shows a component of an air conditioning compressor with the heat exchanger device according to the invention.
In Figur 1 ist ein Klimakompressor 1 schematisch dargestellt, welcher einen Kältemittel-Ansaugstrom 3 ansaugt und nach Verdichtung einen Kältemittel-Auslassstrom 5 in einen schematisch dargestellten Ölabscheider 7 leitet. Im Ölabscheider 7 wird der Auslassstrom in einen Hauptstrom 9 aufgeteilt, welcher der Klimaanlage zugeführt wird, und einen entschieden kleineren Triebraumstrom 11 , welcher das in dem Ölabscheider 7 abgeschiedene Schmiermittel aufnimmt und in den schematisch dargestellten Triebraum 13 des Kompressors 1 leitet. Im Leitungsbereich des Triebraumstromes 11 ist ein Strömungsmittelwiderstand wie z. B. ein schematisch dargestelltes Regelventil 15 angeordnet. Im Triebraumstrombereich 11 zwischen dem Ölabscheider 7 und dem Regelventil 15 ist eine Wärmetauschervorrichtung 17, hier durch ein gestricheltes Oval dargestellt, angeordnet, in welcher ein Leitungsteil 19 des Triebraumstromes 11 gemeinsam mit einem Leitungsteil 21 des Ansaugstromes 3 über eine Wärmeaustauschstrecke verläuft, so dass das etwa mit einer Temperatur von 30° Grad Celsius angesaugte Kältemittel den entschieden kleineren Kältemittelstrom, welcher in den Triebraum geleitet wird, abkühlen kann. Das auf diese Weise gekühlte Schmierstoff-Gas-Gemisch wird im Regelventil 15 auf Triebraumdruckniveau gedrosselt, wobei es sich dort durch die isenthalpe Expansion des enthaltenen Gasanteils weiter abkühlt. Dieses gekühlte Gemisch wird dem Triebraum 13 zugeführt und trägt dort erheblich zur Senkung der Betriebstemperatur bei. Durch eine niedrigere Temperatur im Ölsumpf der Maschine wird auch der Verschleiß minimiert und die thermische Alterung des Schmierstoffes verringert. Somit wird die Wärme nur selektiv zwischen dem Medium, das dem Verdichter zugeführt wird, also dem Ansaugstrom, und dem Medium, das als Phase höherer Dichte eine Einrichtung zum Abscheiden von Öl verlässt, also dem Triebraumstrom, ausgetauscht.In Figure 1, an air conditioning compressor 1 is shown schematically, which sucks in a refrigerant intake flow 3 and, after compression, conducts a refrigerant outlet flow 5 into an oil separator 7, shown schematically. In the oil separator 7, the outlet flow is divided into a main flow 9, which is fed to the air conditioning system, and a decidedly smaller drive chamber flow 11, which absorbs the lubricant separated in the oil separator 7 and leads into the schematically illustrated drive chamber 13 of the compressor 1. In the conduction area of the engine room flow 11 is a fluid resistance such as. B. a schematically illustrated control valve 15 is arranged. In the drive chamber flow area 11 between the oil separator 7 and the control valve 15, a heat exchanger device 17, shown here by a dashed oval, is arranged, in which a line part 19 of the drive room flow 11 runs together with a line part 21 of the intake flow 3 over a heat exchange path, so that this approximately refrigerant drawn in at a temperature of 30 ° Celsius can cool down the decidedly smaller refrigerant flow that is led into the drive room. The lubricant-gas mixture cooled in this way is throttled in the control valve 15 to the level of the engine room, where it cools down further due to the isenthalpic expansion of the gas component contained. This cooled mixture is fed to the drive room 13 and there contributes considerably to lowering the operating temperature. A lower temperature in the machine's oil sump also minimizes wear and reduces the thermal aging of the lubricant. Thus, the heat is only selectively exchanged between the medium that is supplied to the compressor, that is to say the intake flow, and the medium that leaves a device for separating oil as a higher-density phase, that is to say the drive chamber flow.
In Figur 2 ist beispielhaft ein Bauteil des erfindungsgemäßen Kompressors im Querschnitt dargestellt, welches beispielsweise einen Zylinderkopf eines Kompressors darstellen kann. Der Zylinderkopf weist im Schnitt eine Außenwand 30 auf, innerhalb der sich ein Druckbereich für das Ansauggas, der Bereich 32, befindet. Der Ansauggasbereich 32 wird radial nach innen durch eine weitere Wand 34 abgetrennt. Innerhalb der Trennwand 34 befindet sich ein Bereich 36, durch welchen der Auslassstrom des Klimakompressors geleitet wird. Nach innen wird der Aus- lass-Gasbereich 36 durch eine weitere Zwischenwand 38 abgetrennt. Innerhalb der Trennwand 38 befindet sich ein dritter Gasbereich 40, in welchem der Triebraumdruck weitergeleitet wird. Innerhalb des Ansaug-Gasdruckbereiches 32 ist nun erfindungsgemäß eine Leitung 42, hier in Gestalt eines Röhrchens, dargestellt, welche beispielsweise über einen Anschluss 44 vom Ölabscheider 7 aus Figur 1 hergeleitet ist und nach einer gewissen Länge innerhalb des Ansaug- Gasbereiches 32 durch den Anschluss 46 dem Regelventil 15 aus Figur 1 zugeführt wird. Dieses Röhrchen 42 bildet also mit dem Ansaug-Gasbereich 32 eine Wärmetauschervorrichtung, durch welche das kühle Ansauggas im Bereich 32 den geringen Massenstrom des Triebraumstromes im Röhrchen 42 kühlen kann. Der Auslassdruckbereich 36, der sich innerhalb der Trennwand 34 befindet, hat mit etwa > 100° Celsius eine erheblich höhere Temperatur und kann durch die geringe Umfangslänge der Wandung 34 vorteilhaft durch entsprechende Maßnahmen thermisch vom Ansaugbereich 32 abgetrennt werden, wie z. B. durch Isolierbeschichtungen oder Ähnliches, und verhindert damit eine unnötige Aufheizung des Ansauggasstromes 32. Erfindungs- gemäß vorteilhaft wird also der kleine Olabscheider-Gasstrom 11 , also der Gasstrom zum Triebraum 13, das Ansauggas nicht wesentlich aufheizen, während der Hauptgasstrom 5 zum Ausläse möglichst gut von diesem Medium isoliert sein sollte, um ein schädliches Aufwärmen des Ansauggases zu verhindern.FIG. 2 shows, by way of example, a cross-section of a component of the compressor according to the invention, which can represent, for example, a cylinder head of a compressor. On average, the cylinder head has an outer wall 30, within which there is a pressure area for the intake gas, area 32. The intake gas area 32 is separated radially inwards by a further wall 34. There is an area 36 within the partition 34, through which the outlet flow of the air conditioning compressor is passed. The outlet gas region 36 is separated from the inside by a further intermediate wall 38. Within the partition 38 there is a third gas area 40 in which the engine pressure is passed on. A line 42, here in the form of a tube, is now shown within the intake gas pressure area 32, which is derived, for example, from the oil separator 7 from FIG. 1 via a connection 44 and, after a certain length, within the intake gas area 32 through the connection 46 the control valve 15 of Figure 1 is supplied. This tube 42 therefore forms a heat exchanger device with the intake gas region 32, by means of which the cool intake gas in the region 32 can cool the small mass flow of the drive space flow in the tube 42. The outlet pressure region 36, which is located within the partition wall 34, has a considerably higher temperature at approximately> 100 ° Celsius and can advantageously be thermally separated from the suction region 32 by appropriate measures due to the short circumferential length of the wall 34, such as e.g. B. by insulating coatings or the like, and thus prevents unnecessary heating of the intake gas stream 32. According to the invention, the small oil separator gas stream 11, that is to say the gas stream to the drive chamber 13, does not substantially heat up the intake gas, while the main gas stream 5 to the outlet is as much as possible well insulated from this medium to prevent harmful warming up of the intake gas.
Bei Maschinen aus dem Stand der Technik ergibt sich das Problem, dass die Drosseleinrichtungen das abgeschiedene Öl-Gasgemisch direkt dem Triebraum 13 zuführen, wobei das heiße Gemisch nicht vor der Drosselung gekühlt wird. Dabei ergeben sich nach der Drosselung erheblich höhere Temperaturen im Triebraum 13 als bei der Erfindung.In machines from the prior art, the problem arises that the throttle devices feed the separated oil-gas mixture directly to the drive chamber 13, the hot mixture not being cooled before the throttling. After throttling, there are considerably higher temperatures in the drive chamber 13 than in the invention.
Bei der Erfindung ist auch besonders vorteilhaft, dass das heiße Triebraum-Ölgasgemisch vor der Drosselung gekühlt wird und damit auch das Regelventil 15, welches in den meisten Fällen ein Elektromagnetventil ist, durch den kühleren Arbeitsbereich mit einem besseren Wirkungsgrad und mit einer besseren Ausnutzung der elektrischen Leistung arbeiten kann. Bezuqszeichenliste Kältemittel-Ansaugstrom Kältemittel-Auslassstrom Ölabscheider Auslass-Hauptstrom Triebraumstrom Triebraum Regelventil Wärmetauschervorrichtung Leitungsteil Triebraumstrom Leitungsteil Ansaugstrom Außenwand Zylinderkopf Druckbereich Ansauggas Trennwand Druckbereich Auslassgas Trennwand Triebraumdruck-Bereich Leitung Triebraumdruck Anschluss Ölabscheider Anschluss Regelventil In the invention, it is also particularly advantageous that the hot engine oil-gas mixture is cooled before throttling and thus also the control valve 15, which in most cases is an electromagnetic valve, with a better efficiency and with a better utilization of the electrical due to the cooler working range Performance can work. Reference list of refrigerant intake flow Refrigerant outlet flow oil separator Outlet main flow Drive room flow Drive room control valve Heat exchanger device Line part Drive room flow Line part Intake flow Outer wall Cylinder head Pressure area Intake gas partition Wall pressure area Outlet gas partition Wall drive area pressure area Line drive chamber pressure Connection oil separator Connection control valve

Claims

Patentansprüche claims
1. Klimakompressor mit einem Kältemittel-Ansaugstrom (3) und einem Kältemittel- Auslassstrom (5) und mit einem Ölabscheider (7), welcher im Auslassstrombereich angeordnet ist und wobei im Bereich des Olabscheiders (7) ein Kältemittelstrom (11) vom Auslassstrom (5) abgezweigt und dem Triebraum (13) zugeführt wird, dadurch gekennzeichnet, dass der Triebraumstrom (11) mittels einer Wärmetauschervorrichtung (17) vom Ansaugstrom (3) gekühlt wird.1. A / C compressor with a refrigerant intake flow (3) and a refrigerant outlet flow (5) and with an oil separator (7) which is arranged in the outlet flow area and wherein in the area of the oil separator (7) a refrigerant flow (11) from the outlet flow (5 ) is branched off and fed to the drive room (13), characterized in that the drive room flow (11) is cooled by the intake flow (3) by means of a heat exchanger device (17).
2. Klimakompressor nach Anspruch 1 , dadurch gekennzeichnet, dass die Wärmetauschervorrichtung (17) zwischen dem Ölabscheider (7) und einem Widerstand in dem zugeführten Triebraumstrom (11) angeordnet ist.2. Air conditioning compressor according to claim 1, characterized in that the heat exchanger device (17) is arranged between the oil separator (7) and a resistor in the drive room flow (11) supplied.
3. Klimakompressor nach Anspruch 2, dadurch gekennzeichnet, dass der Widerstand verstellbar ausgeführt ist, insbesondere, dass der Widerstand durch ein Ventil, beispielsweise ein Regelventil (15), dargestellt ist.3. Air conditioning compressor according to claim 2, characterized in that the resistance is adjustable, in particular that the resistance is represented by a valve, for example a control valve (15).
4. Klimakompressor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der restliche Auslassstrom (9) gegenüber dem Ansaugstrom (3) im Wesentlichen thermisch isoliert aus dem Kompressor (1) abgeführt wird.4. Air conditioning compressor according to one of the preceding claims, characterized in that the remaining outlet flow (9) is discharged from the compressor (1) substantially thermally insulated from the intake flow (3).
5. Klimakompressor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Wärmetauschervorrichtung (17) durch eine separate Leitung, beispielsweise ein Röhrchen (42) oder eine Nut oder einen eingelassenen Kanal, in den Gehäuseteilen des Klimakompressors dargestellt ist5. Air conditioning compressor according to one of the preceding claims, characterized in that the heat exchanger device (17) by a separate line, for example a tube (42) or a groove or an embedded channel, is shown in the housing parts of the air conditioning compressor
6. Klimakompressor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der zugeführte Triebraumstrom (11) durch den Widerstand, beispielsweise durch das Ventil (15), auf den Triebraumdruck gedrosselt wird.6. Air conditioning compressor according to one of the preceding claims, characterized in that the supplied drive chamber flow (11) is throttled by the resistance, for example by the valve (15), to the drive chamber pressure.
7. Klimakompressor nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der zugeführte Triebraumstrom (11) eine besonders schmierstoffreiche Phase des Gases aufweist (höhere Dichte). 7. Air conditioning compressor according to one of the preceding claims, characterized in that the supplied drive chamber flow (11) has a particularly lubricant-rich phase of the gas (higher density).
PCT/DE2005/000778 2004-05-07 2005-04-28 Air-conditioning compressor WO2005108881A1 (en)

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