EP0030275A1 - Compressor, especially screw compressor with lubrication circuit - Google Patents

Compressor, especially screw compressor with lubrication circuit Download PDF

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Publication number
EP0030275A1
EP0030275A1 EP80106830A EP80106830A EP0030275A1 EP 0030275 A1 EP0030275 A1 EP 0030275A1 EP 80106830 A EP80106830 A EP 80106830A EP 80106830 A EP80106830 A EP 80106830A EP 0030275 A1 EP0030275 A1 EP 0030275A1
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Prior art keywords
compressor
lubricant
circuit
sealant
coolant
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German (de)
French (fr)
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Karl Prof. Dr.-Ing. Bammert
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation

Definitions

  • the invention relates to a compressor, in particular a screw compressor, with two rotors which are in meshing engagement with one another in the working space of a housing by means of suction and pressure-side bearings, and a lubricant circuit for lubricating the bearings, the one reservoir, the lubricant lines leading from this to the bearings Has associated lubricant collection rooms and return lines leading from them to the storage container, and with a coolant and sealant circuit which has a supply pressure container for the coolant and sealant under the compressor discharge pressure, feed lines leading from here to the working space of the compressor and a separator connected to the compressor discharge line for the has coolant and sealant carried by the gas flow.
  • Such compressors with the supply of a cooling, sealing and also lubricating liquid to the work space and to the rotors have the advantage over so-called dry-running compressors that higher pressures can be achieved and that costly toothed gears can be dispensed with in order to achieve contact-free synchronization of the rotors.
  • Two different alternative possibilities are known from GB-PS 846 390 for the lubricant or coolant and sealant circuit for such compressors.
  • a major disadvantage of such a construction with a common lubricant, coolant and sealant circuit becomes apparent when the compressor is to be used to compress gases which tend to dissolve in the medium acting as a lubricant, coolant and sealant -and impair its lubricity.
  • An example of such applications is the compression of refrigerants, such as. B. difluoromonochloromethane, trade name Frigen 22 or Freon 22 or other halogenated hydrocarbons, especially if these are to be compressed in one stage to final pressures of 20 or 25 bar. From solution diagrams it follows that the proportion of refrigerant dissolved in the oil can be up to 30%, and that as a result the viscosity of the oil is so strong, e.g. B. to 3.5 qmm / sec. can be reduced so that the oil can no longer fulfill its function as a lubricant for bearing lubrication.
  • the invention has for its object to improve a compressor of the type mentioned in such a way that no or only very simple, cheap and space-saving seals between the bearings and the work space are required and still avoid impairment of the bearing lubrication caused by gas dissolved in the lubricant becomes.
  • This object is achieved in that the reservoir of the lubricant circuit is closed and its gas space is connected to the intake line of the compressor by a compensating line.
  • the lubricant circuit and the coolant and sealant circuit contain the same medium as lubricant, coolant and sealant and are connected to one another by a controllable connecting valve.
  • This valve can preferably be controlled by a level sensor in the reservoir of the lubricant circuit.
  • a connecting line with a controllable valve is preferably provided between a lubricant line and the suction side of the compressor, which is also provided by the Level sensor in the lubricant reservoir is controllable.
  • the drawing shows a longitudinal section through a screw compressor and the flow diagram of the associated lubricant, coolant and sealant circuit.
  • the compressor has a housing 10, in the working space 12 of which two rotors 14 are mounted next to one another, which engage in one another with helically arranged ribs and grooves. Only one of these rotors 14 is visible in the drawing.
  • the shaft 16 of the rotor is supported at both ends by means of radial sliding bearings 18 and also at the end on the pressure side by means of an axial roller bearing 20.
  • the shaft of one rotor, the main rotor is driven by a drive (not shown), and the main rotor drives the secondary rotor through the meshing engagement.
  • the gas to be compressed in particular a refrigerant such as difluoromonochloromethane, which in this case is under the evaporator pressure, is sucked in via the suction line 22 and the suction nozzle 24, compressed in the working space 12 by the rotors 14 and via the pressure nozzle 26 and the pressure line 28 as
  • the separator and storage container serving pressure container 30 is supplied, from where it passes through the separating filter 32 and the pipeline 34 to the consumer and, in the case of refrigerants, to the condenser.
  • oil or another liquid suitable as a coolant, sealant and lubricant which is fed to the working space 12 by means of the line 36 via a cooler 38, a throttle element 40 and the housing bore 42 in order to close the rotors cool, seal against each other and against the housing and mesh with them to lubricate the flanks.
  • This oil is discharged together with the compressed gas stream via the pressure port 26 and the pressure line 28 and separated from the gas stream in the container 30 and returned to the sump 44.
  • oil is removed from a closed reservoir 46 via a pump 48 and a cooler 50 and fed to the lubricant bores of the bearings 18 via the line 52 and the housing channels 54, 56. From these lubricant bores, the oil enters the bearing gap 1 in both axial directions. A part of the oil passes directly from the bearing gap into the oil collecting spaces 56, 58, which are connected to one another by a longitudinal channel 60 in the housing 10.
  • the portion of the oil which occurs in the direction of the working space passes from the respective bearing 18 into an oil collecting groove 62 which is arranged as an intermediate space between each bearing 18 and a sealing element 64 and is connected to the associated oil collecting space 56 or 58 by a channel 66 in each case .
  • the oil collecting space 56 is connected to the reservoir 46 via an outlet channel 68.
  • the gas space of the storage container 46 is also connected to the suction line 22 via a compensating line 70.
  • the oil collecting groove 62 which is under low pressure, is arranged between each bearing 18 and the working space 12 and effectively causes a leakage of oil from the bearing 18 to the working space 12 or vice versa, a leakage of gas from the working space 12 to the bearing 18 largely prevented.
  • the additional sealing elements 64 are therefore not subject to particularly high requirements; they can be simple and very short elements elements such as B. act short labyrinths or swim rings. These can also be supplied with oil through corresponding housing bores, as shown at 72 for the pressure-side sealing element.
  • the oil therein can only contain relatively small amounts of a soluble gas, e.g. B. refrigerant, dissolved.
  • a soluble gas e.g. B. refrigerant
  • the corresponding proportion in the reservoir 46 at a pressure of z. B. 5 bar and a temperature of 70 ° C significantly less than 5%, which practically does not affect the viscosity of the oil.
  • a level switch 74 with lower and upper limit contact controls on the one hand a solenoid valve 76, which connects the line 36 to the reservoir 46, and also a solenoid valve 78, which connects the line 52 to the suction line 22 of the compressor.
  • the solenoid valve 76 is opened and oil can reach the container 46 from the pressure container 30.
  • valve 78 opens and excess oil from the container 46 enters the suction line and from there with the gas through the compressor into the reservoir pressure container 30.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
  • Rotary-Type Compressors (AREA)

Abstract

Compressor, especially a screw compressor, with two rotors supported in the working space of a housing by means of bearings on the intake and delivery side and in mesh with one another, a lubricant circuit for lubricating the bearings, which has a reservoir (46), lubricant lines (52) leading from the latter to the bearings, lubricant collecting spaces (56, 58) and return lines leading from the latter to the reservoir. The coolant and sealant circuit has a pressurised coolant and sealant reservoir under the delivery pressure of the compressor, feedlines leading from here to the working space of the compressor, and a separator (30), connected to the compressor delivery line, for the coolant and sealant entrained by the gas flow. The reservoir of the lubricant circuit is closed and its gas space is connected to the intake side of the compressor by a compensating line (70). In the compressor, in which the lubricant circuit and the coolant and sealant circuit contain the same medium as lubricant, coolant and sealant, the lubricant circuit and the coolant and sealant circuit are connected by a controllable connecting valve (76), which can be controlled by a level sensor (74) in the reservoir (46) of the lubricant circuit. A connecting line with a valve (78) which can likewise be controlled by the level sensor (74), is provided between a lubricant line (52) and the intake side of the compressor. <IMAGE>

Description

Die Erfindung betrifft einen Verdichter, insbesondere einen Schraubenverdichter, mit zwei im Arbeitsraum eines Gehäuses mittels saug- und druckseitiger Lager gelagerten, miteinander in Kämmeingriff stehenden Rotoren, einem Schmiermittelkreislauf zur Schmierung der Lager, der einen Vorratsbehälter, von diesem zu den Lagern führende Schmiermittelleitungen, den Lagern zugeordnete Schmiermittelauffangräume und von diesen zum Vorratsbehälter führende Rücklaufleitungen aufweist, und mit einem Kühl- und Dichtmittelkreislauf, der einen unter dem Verdichterausblasdruck stehenden Vorratsdruckbehälter für Kühl- und Dichtmittel, von hier zum Arbeitsraum des Verdichters führende Zuführungsleitungen und einen an die Verdichterausblasleitung angeschlossenen Abscheider für das vom Gasstrom mitgeführte Kühl- und Dichtmittel aufweist.The invention relates to a compressor, in particular a screw compressor, with two rotors which are in meshing engagement with one another in the working space of a housing by means of suction and pressure-side bearings, and a lubricant circuit for lubricating the bearings, the one reservoir, the lubricant lines leading from this to the bearings Has associated lubricant collection rooms and return lines leading from them to the storage container, and with a coolant and sealant circuit which has a supply pressure container for the coolant and sealant under the compressor discharge pressure, feed lines leading from here to the working space of the compressor and a separator connected to the compressor discharge line for the has coolant and sealant carried by the gas flow.

Derartige Verdichter mit Zuführung einer kühlenden, abdichtenden und auch schmierenden Flüssigkeit zum Arbeitsraum und zu den Rotoren haben gegenüber sogenannten trockenlaufenden Verdichtern den Vorteil, daß höhere Drücke erzielt werden können und daß auf kostspielige Zahnradgetriebe zur Erzielung eines berührungsfreien Gleichlaufes der Rotoren verzichtet werden kann. Für den Schmiermittel- bzw. Kühl- und Dichtmittelkreislauf für derartige Verdichter sind aus der GB-PS 846 390 zwei verschiedene alternative Möglichkeiten bekannt. Bei der einen Alternative ist nur ein einziger Kreislauf eines gleichzeitig als Schmier-, Kühl- und Dichtmittel wirkenden Mediums vorgesehen, welches zuerst durch die Lager fließt und diese schmiert und anschließend dem Arbeitsraum zugeführt wird, von wo es mit dem Gasstrom ausgetragen und mittels des Abscheiders abgeschieden und in den Vorratsdruckbehälter zurückgeführt wird. Dies hat den Vorteil, daß auf aufwendige und die Baulänge erheblich vergrößernde Abdichtungen zwischen den Lagern und dem Arbeitsraum des Verdichters verzichtet werden kann, da Gasleckagen aus dem Verdichter in die Schmiermittelauffangräume der Lager und/oder Schmiermittelleckagen von den Lagern in den Arbeitsraum des Verdichters unschädlich sind, weil diese Gas- bzw. Schmiermittelanteile letztlich wieder in den Arbeitsraum bzw. den Abscheider gelangen.Such compressors with the supply of a cooling, sealing and also lubricating liquid to the work space and to the rotors have the advantage over so-called dry-running compressors that higher pressures can be achieved and that costly toothed gears can be dispensed with in order to achieve contact-free synchronization of the rotors. Two different alternative possibilities are known from GB-PS 846 390 for the lubricant or coolant and sealant circuit for such compressors. In the one alternative there is only a single circle a medium acting simultaneously as a lubricant, coolant and sealant is provided, which first flows through the bearings and lubricates them and then is fed to the work area, from where it is discharged with the gas stream and separated by means of the separator and returned to the storage pressure vessel. This has the advantage that complex seals between the bearings and the working area of the compressor, which increase the overall length, can be dispensed with, since gas leaks from the compressor into the lubricant collecting areas of the bearings and / or lubricant leakages from the bearings into the working area of the compressor are harmless , because these gas or lubricant parts ultimately get back into the work area or the separator.

Ein wesentlicher Nachteil einer solchen Konstruktion mit gemeinsamen Schmier-, Kühl- und Dichtmittelkreislauf zeigt sich aber, wenn der Verdichter zur Verdichtung von Gasen benutzt werden soll, die die Tendenz haben, sich in dem als Schmier-, Kühl- und Dichtmittel wirkenden Medium zu lösen-und dessen Schmierfähigkeit zu beeinträchtigen. Ein Beispiel für solche Anwendungsfälle ist die Verdichtung von Kältemitteln, wie z. B. Difluormonochlormethan, Handelsbezeichnung Frigen 22 oder Freon 22 oder anderen halogenierten Kohlenwasserstoffen, insbesondere wenn diese einstufig auf Enddrücke von 20 oder 25 bar verdichtet werden sollen. Aus Lösungsdiagrammen ergibt sich, daß der in dem öl gelöste Kältemittelanteil bis zu 30 % betragen kann, und daß hierdurch die Viskosität des öls so stark, z. B. auf 3,5 qmm/sec. verringert werden kann, daß das öl seine Funktion als Schmiermittel zur Lagerschmierung nicht mehr erfüllen kann.A major disadvantage of such a construction with a common lubricant, coolant and sealant circuit, however, becomes apparent when the compressor is to be used to compress gases which tend to dissolve in the medium acting as a lubricant, coolant and sealant -and impair its lubricity. An example of such applications is the compression of refrigerants, such as. B. difluoromonochloromethane, trade name Frigen 22 or Freon 22 or other halogenated hydrocarbons, especially if these are to be compressed in one stage to final pressures of 20 or 25 bar. From solution diagrams it follows that the proportion of refrigerant dissolved in the oil can be up to 30%, and that as a result the viscosity of the oil is so strong, e.g. B. to 3.5 qmm / sec. can be reduced so that the oil can no longer fulfill its function as a lubricant for bearing lubrication.

Dieses Problem tritt nicht auf bei der anderen aus GB-PS 846 390 bekannten Alternative, bei der der Schmiermittelkreislauf und der Kühl- und Dichtmittelkreislauf völlig voneinander getrennt sind, so daß mit dem verdichteten Gasstrom in Berührung kommendes, d. h. mit ihm ausgetragenes und im Abscheider abgeschiedenes öl oder dgl. Medium nicht in den Vorratsbehälter gelangen kann, aus dem das Schmiermittel für die Lager entnommen wird. Hierbei ergibt sich aber der Nachteil, daß zwischen den Lagern und dem Arbeitsraum des Verdichters außerordentlich hochwertige, aufwendige Dichtungen verwendet werden müssen, da sonst die Gasleckage in die Lager des Verdichters bzw. auch die Schmiermittelleckage von den Lagern in den Arbeitsraum des Verdichters unlösbare Probleme schafft. Solche Abdichtungen sind nicht nur teuer, sondern bewirken auch, daß wegen ihrer relativ großen Baulänge der Abstand der Lager der Rotoren so groß gewählt werden muß, daß bereits bei kleinen Belastungen große Durchbiegungen und Biegespannungen der Rotoren auftreten.This problem does not occur in the other alternative known from GB-PS 846 390, in which the lubricant circuit and the coolant and sealant circuit are completely separate from one another, so that anything coming into contact with the compressed gas stream, i. H. Oil or similar medium discharged with it and separated in the separator cannot get into the reservoir from which the lubricant for the bearings is removed. Here, however, there is the disadvantage that extremely high-quality, expensive seals must be used between the bearings and the working space of the compressor, since otherwise the gas leakage into the bearings of the compressor or the lubricant leakage from the bearings into the working space of the compressor creates unsolvable problems . Such seals are not only expensive, but also have the effect that, due to their relatively large overall length, the distance between the bearings of the rotors must be chosen so large that large deflections and bending stresses of the rotors occur even with small loads.

Der Erfindung liegt die Aufgabe zugrunde, einen Verdichter der eingangs genannten Art so zu verbessern, daß keine oder nur sehr einfache, billige und wenig Platz beanspruchende Abdichtungen zwischen den Lagern und dem Arbeitsraum benötigt werden und trotzdem eine Beeinträchtigung der Lagerschmierung durch im Schmiermittel gelöstes Gas vermieden wird.The invention has for its object to improve a compressor of the type mentioned in such a way that no or only very simple, cheap and space-saving seals between the bearings and the work space are required and still avoid impairment of the bearing lubrication caused by gas dissolved in the lubricant becomes.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß der Vorratsbehälter des Schmiermittelkreislaufs geschlossen und sein Gasraum durch eine Ausgleichsleitung mit der Ansaugleitung des Verdichters verbunden ist.This object is achieved in that the reservoir of the lubricant circuit is closed and its gas space is connected to the intake line of the compressor by a compensating line.

Dadurch wird erreicht, daß der gesamte Schmiermittelkreislauf unter dem niedrigen Ansaugdruck des Verdichters steht. Bei diesen niedrigen Drucken können auch nur geringe Mengen des zu verdichtenden Kältemittels oder dergleichen Gases im Schmiermittel in Lösung gehen, die dessen Viskosität und Schmierfähigkeit nicht wesentlich beeinträchtigen. Außerdem können aufgrund von Leckage durch das Schmiermittel mitgeführte Gasanteile in den Gasraum des Vorratsbehälters entweichen und von diesem über die Ausgleichsleitung wieder in den Verdichter zurückgelangen.This ensures that the entire lubricant circuit is under the low suction pressure of the compressor. At these low pressures, only small amounts of the refrigerant or the like gas to be compressed can dissolve in the lubricant, which do not significantly impair its viscosity and lubricity. In addition, gas components entrained by the lubricant can escape into the gas space of the storage container due to leakage and from there return to the compressor via the compensating line.

Gemäß einer bevorzugten weiteren Ausgestaltung der Erfindung enthalten der Schmiermittelkreislauf und der Kühl- und Dichtmittelkreislauf das gleiche Medium als Schmier-, Kühl- und Dichtmittel und sind durch ein steuerbares Verbindungsventil miteinander verbunden. Dieses Ventil ist vorzugsweise durch einen Niveaufühler im Vorratsbehälter des Schmiermittelkreislaufs steuerbar. Hierdurch wird eine selbsttätige Rückführung der durch Leckage von den Lagern in den Arbeitsraum des Verdichters gelangenden und aus dem ausgeblasenen Gasstrom abgeschiedenen Schmiermittelmengen in den Schmiermittelkreislauf und damit eine selbsttätige Konstanthaltung der Umlaufmengen in beiden Kreisläufen erreicht.According to a preferred further embodiment of the invention, the lubricant circuit and the coolant and sealant circuit contain the same medium as lubricant, coolant and sealant and are connected to one another by a controllable connecting valve. This valve can preferably be controlled by a level sensor in the reservoir of the lubricant circuit. In this way, an automatic return of the quantities of lubricant that leaked from the bearings into the working chamber of the compressor and separated from the blown-out gas stream into the lubricant circuit and thus an automatic keeping of the circulating quantities in both circuits is achieved.

Für den Fall, daß Kühl- und Dichtmittel aus dem Verdichterraum über die Wellendichtungen in den Schmiermittelkreislauf gelangt und das Niveau im Schmiermittelvorratsbehälter dadurch zu sehr ansteigt, ist vorzugsweise zwischen einer Schmiermittelleitung und der Saugseite des Verdichters eine Verbindungsleitung mit einem steuerbaren Ventil vorgesehen, welches ebenfalls vom Niveaufühler im Schmiermittelvorratsbehälter steuerbar ist.In the event that coolant and sealant from the compressor chamber enters the lubricant circuit via the shaft seals and the level in the lubricant reservoir rises too much, a connecting line with a controllable valve is preferably provided between a lubricant line and the suction side of the compressor, which is also provided by the Level sensor in the lubricant reservoir is controllable.

Eine Ausführungsform der Erfindung wird anhand der Zeichnung näher erläutert.An embodiment of the invention is explained in more detail with reference to the drawing.

Die Zeichnung zeigt einen Längsschnitt durch einen Schraubenverdichter sowie das Fließschema des zugehörigen Schmier-, Kühl- und Dichtmittelkreislaufs.The drawing shows a longitudinal section through a screw compressor and the flow diagram of the associated lubricant, coolant and sealant circuit.

Der Verdichter hat ein Gehäuse 10, in dessen Arbeitsraum 12 nebeneinander zwei Rotoren 14 gelagert sind, die mit schraubenförmig angeordneten Rippen und Nuten ineinander greifen. In der Zeichnung ist nur der eine dieser Rotoren 14 sichtbar. Die Welle 16 des Rotors ist an beiden Enden mittels Radialgleitlagern 18 und außerdem am druckseitigen Ende mittels eines Axialwälzlagers 20 gelagert. Die Welle des einen Rotors, des Hauptläufers wird durch einen (nicht dargestellten) Antrieb angetrieben, und der Hauptläufer treibt durch den Kämmeingriff den Nebenläufer an. Das zu verdichtende Gas, insbesondere ein Kältemittel wie Difluormonochlormethan, das in diesem Fall unter dem Verdampferdruck steht, wird über die Saugleitung 22 und dem Saugstutzen 24 angesaugt, im Arbeitsraum 12 von den Rotoren 14 verdichtet und über den Druckstutzen 26 und die Druckleitung 28 dem als Abscheider und Vorratsbehälter dienenden Druckbehälter 30 zugeführt, von wo es über das Abscheidefilter 32 und die Rohrleitung 34 zum Verbraucher, bei Kältemitteln zum Kondensator gelangt.The compressor has a housing 10, in the working space 12 of which two rotors 14 are mounted next to one another, which engage in one another with helically arranged ribs and grooves. Only one of these rotors 14 is visible in the drawing. The shaft 16 of the rotor is supported at both ends by means of radial sliding bearings 18 and also at the end on the pressure side by means of an axial roller bearing 20. The shaft of one rotor, the main rotor, is driven by a drive (not shown), and the main rotor drives the secondary rotor through the meshing engagement. The gas to be compressed, in particular a refrigerant such as difluoromonochloromethane, which in this case is under the evaporator pressure, is sucked in via the suction line 22 and the suction nozzle 24, compressed in the working space 12 by the rotors 14 and via the pressure nozzle 26 and the pressure line 28 as The separator and storage container serving pressure container 30 is supplied, from where it passes through the separating filter 32 and the pipeline 34 to the consumer and, in the case of refrigerants, to the condenser.

Im unteren Teil des Druckbehälters 30 befindet sich öl oder eine andere als Kühl-, Dicht- und Schmiermittel geeignete Flüssigkeit, die mittels der Leitung 36 über einen Kühler 38, ein Drosselorgan 40 und die Gehäusebohrung 42 dem Arbeitsraum 12 zugeführt wird, um die Rotoren zu kühlen, gegeneinander und gegenüber dem Gehäuse abzudichten und an ihren in Kämmeingriff stehenden Flanken zu schmieren. Dieses öl wird zusammen mit dem verdichteten Gasstrom über den Druckstutzen 26 und die Druckleitung 28 ausgetragen und im Behälter 30 vom Gasstrom abgeschieden und in den Sumpf 44 zurückgeführt.In the lower part of the pressure vessel 30 there is oil or another liquid suitable as a coolant, sealant and lubricant, which is fed to the working space 12 by means of the line 36 via a cooler 38, a throttle element 40 and the housing bore 42 in order to close the rotors cool, seal against each other and against the housing and mesh with them to lubricate the flanks. This oil is discharged together with the compressed gas stream via the pressure port 26 and the pressure line 28 and separated from the gas stream in the container 30 and returned to the sump 44.

Zur Schmierung der Lager 18 wird öl aus einem geschlossenen Vorratsbehälter 46 über eine Pumpe 48 und einem Kühler 50 entnommen und über die Leitung 52 und die Gehäusekanäle 54, 56 den Schmiermittelbohrungen der Lager 18 zugeführt. Aus diesen Schmiermittelbohrungen tritt das öl nach beiden Axialrichtungen in die Lagerspalte 1. Ein Teil des öls gelangt aus dem Lagerspalt unmittelbar in die ölauffangräume 56, 58, die durch einen Längskanal 60 im Gehäuse 10 miteinander verbunden sind.To lubricate the bearings 18, oil is removed from a closed reservoir 46 via a pump 48 and a cooler 50 and fed to the lubricant bores of the bearings 18 via the line 52 and the housing channels 54, 56. From these lubricant bores, the oil enters the bearing gap 1 in both axial directions. A part of the oil passes directly from the bearing gap into the oil collecting spaces 56, 58, which are connected to one another by a longitudinal channel 60 in the housing 10.

Der in Richtung auf den Arbeitsraum hin auftretende Anteil des öls gelangt aus dem jeweiligen Lager 18 in eine ölsammelnut 62, die als Zwischenraum zwischen jedem Lager 18 und einem Abdichtelement 64 angeordnet und durch jeweils einen Kanal 66 mit dem zugehörigen ölsammelraum 56 bzw. 58 verbunden ist. Der ölauffangraum 56 ist über einen Ablaufkanal 68 mit dem Vorratsbehälter 46 verbunden. Der Gasraum des Vorratsbehälters 46 ist außerdem über eine Ausgleichsleitung 70-mit der Ansaugleitung 22 verbunden. Dadurch stehen der Vorratsbehälter 46, die Räume 56, 58 und die Ölsammelnuten 62 unter dem niedrigen Ansaugdruck des Verdichters. Durch die zwischen jedem Lager 18 und dem Arbeitsraum 12 angeordnete ölsammelnut 62, die unter niedrigem Druck steht, wird in wirksamer Weise eine Leckage von öl aus dem Lager 18 zum Arbeitsraum 12 bzw. umgekehrt eine Leckage von Gas aus dem Arbeitsraum 12 bis zum Lager 18 weitgehend verhindert. An die zusätzlichen Abdichtelemente 64 werden daher keine besonders hohen Anforderungen gestellt, es kann sich um einfache und sehr kurze Elemente wie z. B. kurze Labyrinthe oder Schwimmringe handeln. Diese können durch entsprechende Gehäusebohrungen zusätzlich mit öl versorgt werden, wie dies bei 72 für das druckseitige Abdichtelement gezeigt ist.The portion of the oil which occurs in the direction of the working space passes from the respective bearing 18 into an oil collecting groove 62 which is arranged as an intermediate space between each bearing 18 and a sealing element 64 and is connected to the associated oil collecting space 56 or 58 by a channel 66 in each case . The oil collecting space 56 is connected to the reservoir 46 via an outlet channel 68. The gas space of the storage container 46 is also connected to the suction line 22 via a compensating line 70. As a result, the reservoir 46, the spaces 56, 58 and the oil collecting grooves 62 are under the low suction pressure of the compressor. The oil collecting groove 62, which is under low pressure, is arranged between each bearing 18 and the working space 12 and effectively causes a leakage of oil from the bearing 18 to the working space 12 or vice versa, a leakage of gas from the working space 12 to the bearing 18 largely prevented. The additional sealing elements 64 are therefore not subject to particularly high requirements; they can be simple and very short elements elements such as B. act short labyrinths or swim rings. These can also be supplied with oil through corresponding housing bores, as shown at 72 for the pressure-side sealing element.

Da der Vorratsbehälter 46 unter dem niedrigen Ansaugdruck des Verdichters steht, kann das darin befindliche öl nur relativ geringe Mengen eines löslichen Gases, z. B. Kältemittels, gelöst enthalten. Während z. B. in dem Vorratsdruckbehälter 30 unter dem hohen Auslaßdruck des Verdichters von z. B. 20 bar und einer Temperatur von z. B. 70 °C bis zu 30 % Kältemittel gelöst sein können, beträgt der entsprechende Anteil im Vorratsbehälter 46 bei einem Druck von z. B. 5 bar und einer Temperatur von 70 °C erheblich weniger als 5 %, wodurch praktisch keine Beeinträchtigung der Viskosität des öls eintritt.Since the reservoir 46 is under the low suction pressure of the compressor, the oil therein can only contain relatively small amounts of a soluble gas, e.g. B. refrigerant, dissolved. During e.g. B. in the reservoir pressure tank 30 under the high outlet pressure of the compressor of z. B. 20 bar and a temperature of z. B. 70 ° C up to 30% refrigerant can be solved, the corresponding proportion in the reservoir 46 at a pressure of z. B. 5 bar and a temperature of 70 ° C significantly less than 5%, which practically does not affect the viscosity of the oil.

Da bei dem beschriebenen Verdichter über die Lager und dem Arbeitsraum des Verdichters ölleckagen aus dem Schmiermittelkreislauf in den Kühl- und Dichtmittelkreislauf und umgekehrt auftreten können, ist eine automatische Konstanthaltung der ölmenge im Vorratsbehälter 46 vorgesehen. Ein Niveauschalter 74 mit unterem und oberem Grenzkontakt steuert einerseits ein Magnetventil 76, das die Leitung 36 mit dem Vorratsbehälter 46 verbindet, und außerdem ein Magnetventil 78, das die Leitung 52 mit der Ansaugleitung 22 des Verdichters verbindet. Sobald der ölspiegel im Behälter 46 zu stark abgesunken, d. h. zu viel öl vom Niederdruck- zum Hochdruckkreislauf gelangt ist, wird das Magnetventil 76 geöffnet und es kann öl vom Druckbehälter 30 in den Behälter 46 gelangen.Since oil leaks from the lubricant circuit into the coolant and sealant circuit and vice versa can occur in the described compressor via the bearings and the working space of the compressor, the oil quantity in the reservoir 46 is automatically kept constant. A level switch 74 with lower and upper limit contact controls on the one hand a solenoid valve 76, which connects the line 36 to the reservoir 46, and also a solenoid valve 78, which connects the line 52 to the suction line 22 of the compressor. As soon as the oil level in the container 46 has dropped too much, ie too much oil has come from the low-pressure to the high-pressure circuit, the solenoid valve 76 is opened and oil can reach the container 46 from the pressure container 30.

Steigt der ölspiegel im Behälter 46 übermäßig an, so öffnet das Ventil 78 und es gelangt überschüssiges öl aus dem Behälter 46 in die Ansaugleitung und von dort mit dem Gas durch den Verdichter in den Vorratsdruckbehälter 30.If the oil level in the container 46 rises excessively, the valve 78 opens and excess oil from the container 46 enters the suction line and from there with the gas through the compressor into the reservoir pressure container 30.

Claims (3)

1. Verdichter, insbesondere Schraubenverdichter, mit zwei im Arbeitsraum eines Gehäuses mittels saug-und druckseitiger Lager gelagerten, miteinander in Kämmeingriff stehenden Rotoren, einem Schmiermittelkreislauf zur Schmierung der Lager, der einen Vorratsbehälter, von diesem zu den Lagern führende Schmiermittelleitungen, den Lagern zugeordnete Schmiermittellauffangräume und diesen zum Vorratsbehälter führende Rücklaufleitungen aufweist, und mit einem Kühl- und Dichtmittelkreislauf, der einen unter dem Verdichterausblasdruck stehenden Vorratsdruckbehälter für Kühl- und Dichtmittel, von hier zum Arbeitsraum des Verdichters führende Zuführungsleitungen und einen an die Verdichterausblasleitung angeschlossenen Abscheider für das vom Gasstrom mitgeführte Kühl- und Dichtmittel aufweist, dadurch gekennzeichnet, daß der Vorratsbehälter (46) des Schmiermittelkreislaufs geschlossen und sein Gasraum durch eine Ausgleichsleitung (70) mit der Saugseite (22 bzw. 24) des Verdichters verbunden ist.1. Compressor, in particular screw compressor, with two rotors that are in meshing engagement with one another in the working space of a housing by means of suction and pressure-side bearings, a lubricant circuit for lubricating the bearings, a storage container, lubricant lines leading from this to the bearings, and lubricant collecting spaces assigned to the bearings and this has return lines leading to the storage container, and with a coolant and sealant circuit, which has a supply pressure container for coolant and sealant under the compressor discharge pressure, feed lines leading from here to the working space of the compressor and a separator connected to the compressor discharge line for the cooling carried along by the gas stream - And sealant, characterized in that the reservoir (46) of the lubricant circuit is closed and its gas space is connected by a compensating line (70) to the suction side (22 or 24) of the compressor. 2. Verdichter nach Anspruch 1, bei dem der Schmiermittelkreislauf und der Kühl- und Dichtmittelkreislauf das gleiche Medium als Schmier-, Kühl- und Dichtmittel enthält, dadurch gekennzeichnet , daß der Schmiermittelkreislauf und der Kühl- und Dichtmittelkreislauf durch ein steuerbares Verbindungsventil (76) verbunden sind, das durch einen Niveaufühler (74) im Vorratsbehälter (46) des Schmiermittelkreislaufs steuerbar ist.2. Compressor according to claim 1, wherein the lubricant circuit and the coolant and sealant circuit contains the same medium as lubricant, coolant and sealant, characterized in that the lubricant circuit and the coolant and sealant circuit through a controllable connecting valve (76) is connected, which can be controlled by a level sensor (74) in the reservoir (46) of the lubricant circuit. 3. Verdichter nach Anspruch 2, dadurch gekennzeichnet , daß zwischen einer Schmiermittelleitung (52) und der Saugseite (22 bzw. 24) des Verdichters eine Verbindungsleitung mit einem ebenfalls durch den Niveaufühler (74) steuerbaren Ventil (78) vorgesehen ist.3. Compressor according to claim 2, characterized in that between a lubricant line (52) and the suction side (22 or 24) of the compressor, a connecting line with a valve (78) which is also controllable by the level sensor (74) is provided.
EP80106830A 1979-12-05 1980-11-06 Compressor, especially screw compressor with lubrication circuit Withdrawn EP0030275A1 (en)

Applications Claiming Priority (2)

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DE19792948993 DE2948993A1 (en) 1979-12-05 1979-12-05 COMPRESSORS, ESPECIALLY SCREW COMPRESSORS, WITH LUBRICANT CIRCUIT
DE2948993 1979-12-05

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EP (1) EP0030275A1 (en)
JP (1) JPS5685587A (en)
AU (1) AU6468680A (en)
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DE (1) DE2948993A1 (en)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0134638A1 (en) * 1983-07-12 1985-03-20 Dunham-Bush Inc. Helical screw rotary compressor for air conditioning system
EP0314819A1 (en) * 1987-10-31 1989-05-10 Leybold Aktiengesellschaft Two-shaft vacuum pump with at least one connecting passage between the bearing spaces
EP0758054A1 (en) * 1995-08-09 1997-02-12 SULZER-ESCHER WYSS GmbH Oil circulation system for screw compressors
EP2431613A3 (en) * 2010-09-17 2016-04-06 Pfeiffer Vacuum GmbH Shaft seal for a vacuum pump
BE1023673B1 (en) * 2015-12-11 2017-06-12 Atlas Copco Airpower Naamloze Vennootschap Method for controlling the liquid injection of a compressor device, a liquid-injected compressor device and a liquid-injected compressor element
WO2017096439A1 (en) * 2015-12-11 2017-06-15 Atlas Copco Airpower, Naamloze Vennootschap Method for regulating the liquid injection of a compressor or expander device, a liquid-injected compressor or expander device, and a liquid-injected compressor or expander element
WO2017096438A1 (en) * 2015-12-11 2017-06-15 Atlas Copco Airpower, Naamloze Vennootschap Method for regulating the liquid injection of a compressor, a liquid-injected compressor and a liquid-injected compressor element
BE1023714B1 (en) * 2015-12-11 2017-06-26 Atlas Copco Airpower Naamloze Vennootschap Method for controlling the liquid injection of a compressor or expander device, a liquid-injected compressor or expander device and a liquid-injected compressor or expander element
US20220042592A1 (en) * 2018-09-27 2022-02-10 Zf Friedrichshafen Ag Measuring arrangement for lubricant

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Publication number Priority date Publication date Assignee Title
SE459203B (en) * 1983-12-01 1989-06-12 Atlas Copco Ab AXELTAETNING
CN108757584B (en) * 2018-07-09 2024-03-12 大同北方天力增压技术有限公司 Silencer for turbocharger and air supplementing method thereof
DE102019111774A1 (en) * 2019-03-25 2020-10-01 Liebherr-Components Biberach Gmbh Drive device for a trench wall cutter
CN113864188A (en) * 2021-07-23 2021-12-31 西安交通大学 Two-stage screw air compressor oil return device and method for reducing oil stirring loss

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DE1009347B (en) * 1954-07-03 1957-05-29 Werner Rietschle Rotary piston blower with circulating lubrication

Patent Citations (1)

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DE1009347B (en) * 1954-07-03 1957-05-29 Werner Rietschle Rotary piston blower with circulating lubrication

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0134638A1 (en) * 1983-07-12 1985-03-20 Dunham-Bush Inc. Helical screw rotary compressor for air conditioning system
EP0314819A1 (en) * 1987-10-31 1989-05-10 Leybold Aktiengesellschaft Two-shaft vacuum pump with at least one connecting passage between the bearing spaces
EP0758054A1 (en) * 1995-08-09 1997-02-12 SULZER-ESCHER WYSS GmbH Oil circulation system for screw compressors
US5765392A (en) * 1995-08-09 1998-06-16 Sulzer-Escher Wyss Gmbh Screw compressor apparatus for refrigerants with oils soluble in refrigerants
EP2431613A3 (en) * 2010-09-17 2016-04-06 Pfeiffer Vacuum GmbH Shaft seal for a vacuum pump
CN106870329A (en) * 2015-12-11 2017-06-20 阿特拉斯·科普柯空气动力股份有限公司 Adjust the method for liquid injection, the compressor of liquid injection and the element of compressor
WO2017096439A1 (en) * 2015-12-11 2017-06-15 Atlas Copco Airpower, Naamloze Vennootschap Method for regulating the liquid injection of a compressor or expander device, a liquid-injected compressor or expander device, and a liquid-injected compressor or expander element
WO2017096438A1 (en) * 2015-12-11 2017-06-15 Atlas Copco Airpower, Naamloze Vennootschap Method for regulating the liquid injection of a compressor, a liquid-injected compressor and a liquid-injected compressor element
BE1023673B1 (en) * 2015-12-11 2017-06-12 Atlas Copco Airpower Naamloze Vennootschap Method for controlling the liquid injection of a compressor device, a liquid-injected compressor device and a liquid-injected compressor element
CN106870374A (en) * 2015-12-11 2017-06-20 阿特拉斯·科普柯空气动力股份有限公司 Compressor or expander device, element and the method for controlling the device liquid injection
BE1023714B1 (en) * 2015-12-11 2017-06-26 Atlas Copco Airpower Naamloze Vennootschap Method for controlling the liquid injection of a compressor or expander device, a liquid-injected compressor or expander device and a liquid-injected compressor or expander element
EP3505764A1 (en) * 2015-12-11 2019-07-03 ATLAS COPCO AIRPOWER, naamloze vennootschap Liquid-injected compressor device or expander device and a liquid-injected compressor element or expander element
CN106870329B (en) * 2015-12-11 2020-06-05 阿特拉斯·科普柯空气动力股份有限公司 Method for regulating the liquid injection of a compressor, liquid-injected compressor and element
US10920777B2 (en) 2015-12-11 2021-02-16 Atlas Copco Airpower, Naamloze Vennootschap Method for regulating the liquid injection of a compressor or expander device, a liquid-injected compressor or expander device, and a liquid-injected compressor or expander element
US11614088B2 (en) 2015-12-11 2023-03-28 Atlas Copco Airpower, Naamloze Vennootschap Method of controlling the temperature and mass flow of a liquid injected into the bearings and compressor space of a compressor using two separated liquid supplies
US20220042592A1 (en) * 2018-09-27 2022-02-10 Zf Friedrichshafen Ag Measuring arrangement for lubricant
US11566700B2 (en) * 2018-09-27 2023-01-31 Zf Friedrichshafen Ag Measuring arrangement for lubricant

Also Published As

Publication number Publication date
AU6468680A (en) 1981-06-11
BR8007897A (en) 1981-08-11
DE2948993A1 (en) 1981-06-11
JPS5685587A (en) 1981-07-11

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