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EP0069859B1 - Compressor aggregate - Google Patents

Compressor aggregate Download PDF

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Publication number
EP0069859B1
EP0069859B1 EP82104890A EP82104890A EP0069859B1 EP 0069859 B1 EP0069859 B1 EP 0069859B1 EP 82104890 A EP82104890 A EP 82104890A EP 82104890 A EP82104890 A EP 82104890A EP 0069859 B1 EP0069859 B1 EP 0069859B1
Authority
EP
European Patent Office
Prior art keywords
hollow cylinder
housing
pump
compressor
compressor unit
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP82104890A
Other languages
German (de)
French (fr)
Other versions
EP0069859A2 (en
EP0069859A3 (en
Inventor
Siegfried Schönwald
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
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Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to AT82104890T priority Critical patent/ATE16518T1/en
Publication of EP0069859A2 publication Critical patent/EP0069859A2/en
Publication of EP0069859A3 publication Critical patent/EP0069859A3/en
Application granted granted Critical
Publication of EP0069859B1 publication Critical patent/EP0069859B1/en
Expired legal-status Critical Current

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Classifications

    • 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
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/06—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B27/0606—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary having cylinders in star- or fan-arrangement, the connection of the pistons with an actuating element being at the outer ends of the cylinders
    • 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
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0261—Hermetic compressors with an auxiliary oil pump

Definitions

  • the invention relates to a compressor unit in which the compressor and its drive motor designed as an external rotor motor are arranged on a common fixed axis in a unit housing and in which a lubricant feed pump designed as a friction pump is provided on the end of the fixed axis facing away from the compressor, with its output opens into a bore channel provided in the fixed axis and projects with its inflow opening into the lubricant reservoir at the bottom of the unit housing, which furthermore has a hollow cylinder coupled to the external rotor as an impeller.
  • Such a compressor unit is known from DE-A1-1 503408.
  • the friction pump is formed by the bearing sleeve designed as a hollow cylinder and spiral grooves provided in the area of the bearing sleeve in the fixed axis.
  • Such a friction pump is very simple in construction, but it can only pump a small amount of oil.
  • a friction pump is known per se, in which a shaft rotates in a hollow cylinder as an impeller. There is a gap between the shaft and the hollow cylinder, in which the medium to be conveyed is carried along by the rotating shaft. The gap extends over a partial circumference of the hollow cylinder and is delimited on both sides by an interrupter narrowing the gap. The medium to be conveyed enters and exits at the beginning and end of the gap.
  • To increase the delivery volume several gap spaces are provided in the known friction pump over the circumference of the hollow cylinder. In this way, the delivery volume can be increased, but the delivery pressure drops sharply because the length of the individual gap spaces is shortened.
  • the invention has for its object to provide a compressor unit of the type described in such a way that the oil required for lubricating and sealing the mutually movable parts of the compressor is pumped to a sufficient extent and also with the required pressure.
  • a pump housing having an annular space between an inner and an outer housing part is arranged on the axis and the hollow cylinder protrudes into the annular space, so that a between the housing parts of the pump housing and the hollow cylinder inner and an outer gap is formed that further a connection between the inner and outer gap and on both sides of the hollow cylinder on the pump housing at least one constriction acting as an interrupter is provided.
  • the hollow cylinder is advantageously formed on the bearing cap of the external rotor. This reduces the assembly effort. Characterized in that several through holes are provided in the wall of the hollow cylinder, pressure and volume flows of the inner and outer gap can compensate.
  • a radial piston compressor 2 and an external rotor motor 3 are arranged together on a fixed axis 4.
  • a bore channel 5 which extends from its end 6, which is opposite the radial piston compressor 2, to the radial piston compressor 2.
  • a hollow cylinder 8 is formed, which forms the rotor of a friction pump.
  • the hollow cylinder 8 projects into an annular space 9, which is formed between an inner and an outer housing part 10 or 11 of a pump housing 12.
  • the inner housing part 10 consists of an integrally formed on a housing end plate 13 ring wall which is pushed over the end 6 of the fixed axis 4.
  • the housing end plate 3 is connected to the outer housing part 11 by means of screws 14.
  • a cover plate 16, the diameter of which is at least equal to the diameter of the outer rotor of the outer rotor motor 3, is fastened to the outer housing part 11 above the oil level 15.
  • the ring wall forming the inner housing part 10 has a passage opening 17 which overlaps with a bore 18 opening into the bore channel 5. This passage opening 17 forms the outlet of the pump.
  • annular disks 20 are inserted one above the other. Through these annular disks 20, the total width of the axial gap is divided into several parallel columns of smaller width. The smaller gaps provide a higher resistance to the flow, so that the leakage current through the axial gap is greatly reduced.
  • the total height of the stacked disks 20 is dimensioned such that it corresponds to the minimum width of the axial gap due to tolerances. This means that regardless of the actual width of the axial gap, the same number of washers can always be inserted into the axial gap.
  • FIG. 2 shows that there is an inner gap 21 and an outer gap 22 between the hollow cylinder 8 and the two housing parts 10 and 11.
  • a radial channel 23 formed in the pump housing 12, which extends under the hollow cylinder 8 the oil flows into an axial channel 24, which extends on both sides of the hollow cylinder 8. From here, the oil flows through the rotating hollow cylinder 8 into the two gaps 21 and 22 dragged along.
  • an interrupter 25 is arranged on both sides of the hollow cylinder 8, through which the two columns 21 and 22 are narrowed. The oil carried by the hollow cylinder 8 is dammed up as a result of this narrowing of the gap and is pressed through the passage opening 17 and the bore 18 into the bore channel 5.
  • axially extending outlet channels 27 are provided in the inner and outer housing parts 10 and 11 in front of the breakers 25, which are connected to the outlet opening 17 in Connect.
  • the hollow cylinder of FIG. 8 itself also has through-holes 28, through which the pressure and the volume flows between the inner and outer gap 21 and 22 can be evenly balanced.
  • the inner and outer housing parts 10 and 11 are cylindrical on its side assigned to the hollow cylinder 8, so that these housing parts can be easily manufactured accordingly.
  • the interrupters 25 form separate components which are inserted in corresponding recesses 29 on the two housing parts 10 and 11.
  • the interrupters 25 can be inserted loosely into these recesses 29.
  • a lubricating film is formed between the interrupters 25 and the hollow cylinder 8, which guarantees a short distance, so that no sliding wear occurs during operation.
  • two interrupters 25 are arranged on the circumference of the housing parts 10 and 11. It is also possible to provide only one interrupter or more than two interrupters. The number of interrupters also corresponds to the number of radial inlet channels 23 and through openings 17.
  • the gas in the compressor housing 1 is set in rotation by the external rotor of the external rotor motor 3. This rotation creates a centrifugal pressure field that forces the oil inward at the bottom of the compressor housing 1.
  • a cover plate 16 is provided on the pump housing 12 which repels the oil from the rotating outer rotor.
  • the oil pumped into the bore channel 5 by the friction pump is conducted via this bore channel to the compressor and possibly also to the bearing points of the drive motor.
  • additional channels branch off from the bore channel at the corresponding points, through which the oil then reaches the desired points.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Reduction Or Emphasis Of Bandwidth Of Signals (AREA)
  • Rotary Pumps (AREA)

Abstract

A compressor and its external-rotor drive motor are arranged on a common stationary shaft in a unitary housing. On the end of the stationary shaft which is away from the compressor, a friction pump is mounted for pumping lubricant from a supply in the unit housing into an axial canal drilled in the stationary shaft. The impeller of the friction pump consists of a hollow cylinder which is coupled to the external rotor. The hollow cylinder is received in a pump housing which has an annular space between an inner and an outer housing part into which the hollow cylinder extends, forming an inner and an outer gap. The two gaps are in communication with each other and each contains at least one constriction which forces oil carried by rotation of the hollow cylinder past openings in the inner housing into the axial canal.

Description

Die Erfindung betrifft ein Verdichteraggregat, bei dem der Verdichter und sein als Außenläufermotor ausgebildeter Antriebsmotor auf einer gemeinsamen feststehenden Achse in einem Aggregatgehäuse angeordnet sind und bei dem auf dem dem Verdichter abgewandten Ende der feststehenden Achse eine als Reibungspumpe ausgebildete Schmiermittelförderpumpe vorgesehen ist, die mit ihrem Ausgang in einen in der feststehenden Achse vorgesehenen Bohrungskanal mündet und mit ihrer Zuflußöffnung in den Schmiermittelvorrat am Boden des Aggregatgehäuses ragt, die ferner als Laufrad einen mit dem Außenläufer gekuppelten Hohlzylinder aufweist.The invention relates to a compressor unit in which the compressor and its drive motor designed as an external rotor motor are arranged on a common fixed axis in a unit housing and in which a lubricant feed pump designed as a friction pump is provided on the end of the fixed axis facing away from the compressor, with its output opens into a bore channel provided in the fixed axis and projects with its inflow opening into the lubricant reservoir at the bottom of the unit housing, which furthermore has a hollow cylinder coupled to the external rotor as an impeller.

Ein solches Verdichteraggregat ist durch die DE-A1-1 503408 bekannt. Die Reibungspumpe wird bei diesem Aggregat durch die als Hohlzylinder ausgebildete Lagerhülse und im Bereich der Lagerhülse in der feststehenden Achse vorgesehene Spiralnuten gebildet. Eine solche Reibungspumpe ist zwar sehr einfach in ihrem Aufbau, jedoch vermag sie nur eine geringe Ölmenge zu fördern.Such a compressor unit is known from DE-A1-1 503408. In this unit, the friction pump is formed by the bearing sleeve designed as a hollow cylinder and spiral grooves provided in the area of the bearing sleeve in the fixed axis. Such a friction pump is very simple in construction, but it can only pump a small amount of oil.

Durch die DE-A1-2428932 ist eine Reibungspumpe an sich bekannt, bei der als Laufrad eine Welle in einem Hohlzylinder rotiert. Zwischen der Welle und dem Hohlzylinder besteht ein Spaltraum, in dem das zu fördernde Medium von der rotierenden Welle mitgeschleppt wird. Der Spaltraum erstreckt sich über einen Teilumfang des Hohlzylinders und wird zu beiden Seiten durch einen den Spaltraum verengenden Unterbrecher begrenzt. Am Anfang und Ende des Spaltraumes erfolgt der Ein- und Austritt des zu fördernden Mediums. Zur Erhöhung des Fördervolumens sind bei der bekannten Reibungspumpe über dem Umfand des Hohlzylinders mehrere Spalträume vorgesehen. Auf diese Weise läßt sich zwar das Fördervolumen erhöhen, jedoch sinkt der Förderdruck stark ab, da die Länge der einzelnen Spalträume verkürzt wird.From DE-A1-2428932 a friction pump is known per se, in which a shaft rotates in a hollow cylinder as an impeller. There is a gap between the shaft and the hollow cylinder, in which the medium to be conveyed is carried along by the rotating shaft. The gap extends over a partial circumference of the hollow cylinder and is delimited on both sides by an interrupter narrowing the gap. The medium to be conveyed enters and exits at the beginning and end of the gap. To increase the delivery volume, several gap spaces are provided in the known friction pump over the circumference of the hollow cylinder. In this way, the delivery volume can be increased, but the delivery pressure drops sharply because the length of the individual gap spaces is shortened.

Durch die DE-B2-2 710 734 ist ein Verdichteraggregat mit einem Radialkolbenverdichter bekannt, bei dem sowohl in die zwischen den Kolben und den Wänden der Kolbenräume bestehenden Spalte als auch in den zwischen dem Zylinderblock und der feststehenden Achse bestehenden Spalt Öl eingebracht wird. Hierfür ist eine relativ große Menge Öl bei einem ausreichenden Förderdruck notwendig.From DE-B2-2 710 734 a compressor unit with a radial piston compressor is known in which oil is introduced both into the gaps existing between the pistons and the walls of the piston chambers and into the gap existing between the cylinder block and the fixed axis. This requires a relatively large amount of oil with a sufficient delivery pressure.

Der Erfindung liegt die Aufgabe zugrunde, ein Verdichteraggregat der eingangs beschriebenen Art so auszubilden, daß das zur Schmierung und Abdichtung der gegeneinander beweglichen Teile des Verdichters notwendige Öl in ausreichendem Maße und auch mit dem erforderlichen Druck gefördert wird.The invention has for its object to provide a compressor unit of the type described in such a way that the oil required for lubricating and sealing the mutually movable parts of the compressor is pumped to a sufficient extent and also with the required pressure.

Die Lösung der gestellten Aufgabe gelingt nach der Erfindung dadurch, daß an der Achse ein zwischen einem inneren und einem äußeren Gehäuseteil einen ringförmigen Raum aufweisendes Pumpengehäuse angeordnet ist und der Hohlzylinder in den ringförmigen Raum hineinragt, so daß zwischen den Gehäuseteilen des Pumpengehäuses und dem Hohlzylinder ein innerer und ein äußerer Spalt gebildet ist, daß ferner zwischen dem inneren und äußeren Spalt eine Verbindung und zu beiden Seiten des Hohlzylinders an dem Pumpengehäuse mindestens eine als Unterbrecher wirkende Verengung vorgesehen ist. Dadurch, daß zu beiden Seiten des Hohlzylinders ein Spalt vorgesehen ist, wird der zur Verfügung stehende Spaltraum nahezu verdoppelt, ohne daß die Spaltlänge und damit der Förderdruck vermindert wird. Außerdem wird diese Vergrößerung des Spaltraumes ohne konstruktiven Mehraufwand erreicht.The object is achieved according to the invention in that a pump housing having an annular space between an inner and an outer housing part is arranged on the axis and the hollow cylinder protrudes into the annular space, so that a between the housing parts of the pump housing and the hollow cylinder inner and an outer gap is formed that further a connection between the inner and outer gap and on both sides of the hollow cylinder on the pump housing at least one constriction acting as an interrupter is provided. The fact that a gap is provided on both sides of the hollow cylinder, the available gap space is almost doubled without the gap length and thus the delivery pressure being reduced. In addition, this enlargement of the gap is achieved without additional design effort.

In vorteilhafter Weise ist der Hohlzylinder an der Lagerkappe des Außenläufers angeformt. Hierdurch wird der Montageaufwand reduziert. Dadurch, daß in der Wand des Hohlzylinders mehrere durchgehende Löcher vorgesehen sind, können sich Druck- und Volumenströme des inneren und äußeren Spaltes ausgleichen.The hollow cylinder is advantageously formed on the bearing cap of the external rotor. This reduces the assembly effort. Characterized in that several through holes are provided in the wall of the hollow cylinder, pressure and volume flows of the inner and outer gap can compensate.

Fertigungstechnische Vorteile ergeben sich dadurch, daß die den ringförmigen Raum begrenzenden Wände des Gehäuseteiles zylindrisch ausgebildet und vor jedem Ausgang gesonderte Unterbrecherteile eingesetzt und an den Wänden des Gehäuseteiles befestigt sind.Manufacturing advantages result from the fact that the walls of the housing part delimiting the annular space are cylindrical and separate interrupter parts are inserted before each exit and are fastened to the walls of the housing part.

Um den Verluststrom über den zwischen dem rotierenden Zylinder und den feststehenden Gehäuseteilen bestehenden Axialspalt klein zu halten, wird vorgeschlagen, daß in den Axialspalt zwischen der Stirnseite des Hohlzylinders und dem Pumpengehäuse mehrere ringförmige Scheiben übereinandergestapelt sind, deren Stapelhöhe gleich der durch Toleranzen bedingten Mindestweite des Axialspaltes ist. Da der laminare Strömungswiderstand mehrerer paralleler Spaltquerschnitte größer ist als der eines einzelnen Spaltes gleicher Gesamtspaltweite, wird der Verluststrom stark reduziert. Hier hat es sich außerdem als zweckmäßig erwiesen, daß die Scheiben in geringem Maße gewellt ausgebildet sind. Die Scheiben bilden in diesem Falle ein Federpaket, dessen einzelne Scheibenabstände im Mittel etwa gleich sind.In order to keep the leakage current small across the axial gap between the rotating cylinder and the fixed housing parts, it is proposed that several annular disks are stacked one above the other in the axial gap between the end face of the hollow cylinder and the pump housing, the stack height of which is equal to the minimum width of the axial gap which is caused by tolerances is. Since the laminar flow resistance of several parallel gap cross sections is greater than that of a single gap of the same total gap width, the leakage current is greatly reduced. Here it has also proven to be expedient for the disks to have a slight corrugation. In this case, the disks form a spring assembly, the individual disk spacings of which are approximately the same on average.

Anhand eines in der Zeichnung dargestellten Ausführungsbeispiels wird der Anmeldungsgegenstand nachfolgend näher beschrieben. Es zeigt

  • Fig. 1 ein Verdichteraggregat im Teilschnitt, bei dem auf dem dem Verdichter gegenüberliegenden Ende der feststehenden Achse eine Pumpe angeordnet ist,
  • Fig. 2 eine Pumpe im Schnitt entlang der Linie 11-11 in Fig. 1.
The subject of the application is described in more detail below using an exemplary embodiment shown in the drawing. It shows
  • 1 shows a compressor assembly in partial section, in which a pump is arranged on the end of the fixed axis opposite the compressor,
  • FIG. 2 shows a pump in section along the line 11-11 in FIG. 1.

In einem Aggregatgehäuse 1 sind ein Radialkolbenverdichter 2 und ein Außenläufermotor 3 gemeinsam auf einer feststehenden Achse 4 angeordnet. In der feststehenden Achse 4 ist ein sich von deren dem Radialkolbenverdichter 2 gegenüberliegenden Ende 6 bis zu dem Radialkolbenverdichter 2 erstreckender Bohrungskanal 5 vorgesehen. An der Lagerkappe 7 des Außenläufermotors 3 ist ein Hohlzylinder 8 angeformt, der den Läufer einer Reibungspumpe bildet. Der Hohlzylinder 8 ragt in einen ringförmigen Raum 9, der zwischen einem inneren und einem äußeren Gehäuseteil 10 bzw. 11 eines Pumpengehäuses 12 gebildet ist. Der innere Gehäuseteil 10 besteht aus einer an einer Gehäuseabschlußplatte 13 angeformten Ringwand, die über das Ende 6 der feststehenden Achse 4 geschoben ist. Die Gehäuseabschlu!3platte 13 ist mittels Schrauben 14 mit dem äußeren Gehäuseteil 11 verbunden. Über dem Ölspiegel 15 ist an dem äußeren Gehäuseteil 11 eine Abdeckplatte 16 befestigt, deren Durchmesser mindestens gleich dem Durchmesser des Außenläufers des Au- ßenläufermotors 3 ist.In a unit housing 1, a radial piston compressor 2 and an external rotor motor 3 are arranged together on a fixed axis 4. Provided in the fixed axis 4 is a bore channel 5 which extends from its end 6, which is opposite the radial piston compressor 2, to the radial piston compressor 2. On the bearing cap 7 of the outer surface fermotors 3 is a hollow cylinder 8 is formed, which forms the rotor of a friction pump. The hollow cylinder 8 projects into an annular space 9, which is formed between an inner and an outer housing part 10 or 11 of a pump housing 12. The inner housing part 10 consists of an integrally formed on a housing end plate 13 ring wall which is pushed over the end 6 of the fixed axis 4. The housing end plate 3 is connected to the outer housing part 11 by means of screws 14. A cover plate 16, the diameter of which is at least equal to the diameter of the outer rotor of the outer rotor motor 3, is fastened to the outer housing part 11 above the oil level 15.

Die das innere Gehäuseteil 10 bildende Ringwand weist eine sich mit einer in den Bohrungskanal 5 mündenden Bohrung 18 deckende Durchtrittsöffnung 17 auf. Diese Durchtrittsöffnung 17 bildet den Ausgang der Pumpe.The ring wall forming the inner housing part 10 has a passage opening 17 which overlaps with a bore 18 opening into the bore channel 5. This passage opening 17 forms the outlet of the pump.

In den zwischen der Stirnseite 19 des Hohlzylinders 8 und der Gehäuseabschlußplatte 13 bestehenden Axialspalt sind mehrere ringförmige Scheiben 20 übereinanderliegend eingefügt. Durch diese ringförmigen Scheiben 20 wird die Gesamtweite des Axialspaltes in mehrere parallele Spalte kleinerer Weite unterteilt. Die kleineren Spalte setzen der Strömung einen höheren Widerstand entgegen, so daß der Verluststrom über den Axialspalt stark reduziert wird. Außerdem ist die Gesamthöhe der übereinandergestapelten Scheiben 20 so bemessen, daß sie der durch Toleranzen bedingten Mindestweite des Axialspaltes entspricht. Damit kann, unabhängig von der tatsächlichen Weite des Axialspaltes, immer die gleiche Anzahl von Scheiben in den Axialspalt eingefügt werden.In the existing between the end face 19 of the hollow cylinder 8 and the housing end plate 13, several annular disks 20 are inserted one above the other. Through these annular disks 20, the total width of the axial gap is divided into several parallel columns of smaller width. The smaller gaps provide a higher resistance to the flow, so that the leakage current through the axial gap is greatly reduced. In addition, the total height of the stacked disks 20 is dimensioned such that it corresponds to the minimum width of the axial gap due to tolerances. This means that regardless of the actual width of the axial gap, the same number of washers can always be inserted into the axial gap.

Die Darstellung nach Fig. 2 läßt erkennen, daß zwischen dem Hohlzylinder 8 sowie den beiden Gehäuseteilen 10 und 11 ein innerer Spalt 21 und ein äußerer Spalt 22 besteht. Über einen im Pumpengehäuse 12 ausgebildeten radialen Kanal 23, der sich unter dem Hohlzylinder 8 hindurch erstreckt, strömt das Öl in einen sich zu beiden Seiten des Hohlzylinders 8 erstreckenden axialen Kanal 24. Von hier wird das Öl durch den rotierenden Hohlzylinder 8 in die beiden Spalte 21 und 22 mitgeschleppt. Am Ende der Förderstrecke ist zu beiden Seiten des Hohlzylinders 8 jeweils ein Unterbrecher 25 angeordnet, durch den die beiden Spalten 21 und 22 verengt werden. Das von dem Hohlzylinder 8 mitgeführten Öl wird infolge dieser Spaltverengung aufgestaut und durch die Durchtrittsöffnung 17 und die Bohrung 18 in den Bohrungskanal 5 gedrückt. Von dort gelangt es zu dem Radialkolbenverdichter 2. In der durch einen Pfeil 26 angedeuteten Drechrichtung des Hohlzylinders 8 gesehen, sind vor den Unterbrechern 25 sich axial erstreckende Austrittskanäle 27 in dem inneren und dem äußeren Gehäuseteil 10 und 11 vorgesehen, die mit der Austrittsöffnung 17 in Verbindung stehen. Die Verbindung des in dem äußeren Gehäuseteil 11 vorgesehenen Kanals 27 mit dem im inneren Gehäuseteil 10 vorgesehenen Kanal 27, in den die Austrittsöffnung 17 direkt mündet, erfolgt über eine unterhalb des Hohlzylinders 8 im Pumpengehäuse vorgesehene Rinne. Der Hohlzylin der 8 selbst weist ferner durchgehende Löcher 28 auf, über die sich der Druck und die Volumenströme zwischen dem inneren und äußeren Spalt 21 und 22 zusätzlich ausgleichen können.The illustration according to FIG. 2 shows that there is an inner gap 21 and an outer gap 22 between the hollow cylinder 8 and the two housing parts 10 and 11. Via a radial channel 23 formed in the pump housing 12, which extends under the hollow cylinder 8, the oil flows into an axial channel 24, which extends on both sides of the hollow cylinder 8. From here, the oil flows through the rotating hollow cylinder 8 into the two gaps 21 and 22 dragged along. At the end of the conveying path, an interrupter 25 is arranged on both sides of the hollow cylinder 8, through which the two columns 21 and 22 are narrowed. The oil carried by the hollow cylinder 8 is dammed up as a result of this narrowing of the gap and is pressed through the passage opening 17 and the bore 18 into the bore channel 5. From there it arrives at the radial piston compressor 2. Seen in the direction of rotation of the hollow cylinder 8 indicated by an arrow 26, axially extending outlet channels 27 are provided in the inner and outer housing parts 10 and 11 in front of the breakers 25, which are connected to the outlet opening 17 in Connect. The connection of the channel 27 provided in the outer housing part 11 with the channel 27 provided in the inner housing part 10, into which the outlet opening 17 opens directly, takes place via a channel provided below the hollow cylinder 8 in the pump housing. The hollow cylinder of FIG. 8 itself also has through-holes 28, through which the pressure and the volume flows between the inner and outer gap 21 and 22 can be evenly balanced.

Der innere und äußere Gehäuseteil 10 und 11 ist auf seiner, dem Hohlzylinder 8 zugeordneten Seite zylindrisch ausgebildet, so daß sich diese Gehäuseteile entsprechend einfach fertigen lassen. Die Unterbrecher 25 bilden gesonderte Bauteile, die in entsprechenden Ausnehmungen 29 an den beiden Gehäuseteilen 10 und 11 eingesetzt sind. Die Unterbrecher 25 können in diese Ausnehmungen 29 lose eingelegt werden. Es besteht allerdings auch die Möglichkeit, die Unterbrecher 25 auf andere Art und Weise an den Gehäuseteilen 10 und 11 zu befestigen. Zwischen den Unterbrechern 25 und dem Hohlzylinder 8 bildet sich ein Schmierfilm, der einen geringen Abstand garantiert, so daß im Betrieb kein Gleitverschleiß auftritt.The inner and outer housing parts 10 and 11 are cylindrical on its side assigned to the hollow cylinder 8, so that these housing parts can be easily manufactured accordingly. The interrupters 25 form separate components which are inserted in corresponding recesses 29 on the two housing parts 10 and 11. The interrupters 25 can be inserted loosely into these recesses 29. However, there is also the possibility of attaching the interrupters 25 to the housing parts 10 and 11 in a different way. A lubricating film is formed between the interrupters 25 and the hollow cylinder 8, which guarantees a short distance, so that no sliding wear occurs during operation.

Gemäß der Darstellung in Fig. 2 sind am Umfang der Gehäuseteile 10 und 11 zwei Unterbrecher 25 angeordnet. Es besteht auch die Möglichkeit, nur einen Unterbrecher oder auch mehr als zwei Unterbrecher vorzusehen. Der Anzahl der Unterbrecher entspricht auch die Anzahl der radialen Einlaßkanäle 23 und der Durchtrittsöffnungen 17.2, two interrupters 25 are arranged on the circumference of the housing parts 10 and 11. It is also possible to provide only one interrupter or more than two interrupters. The number of interrupters also corresponds to the number of radial inlet channels 23 and through openings 17.

Durch den Außenläufer des Außenläufermotors 3 wird das Gas in dem Verdichtergehäuse 1 in Rotation versetzt. Durch diese Rotation entsteht ein zentrifugales Druckfeld, das das Öl am Boden des Verdichtergehäuses 1 nach innen drängt. Um zu vermeiden, daß es von dem rotierenden Außenläufer erfaßt und in heftige Bewegung versetzt wird, wodurch das Öl mit Gasblasen versetzt würde, ist an dem Pumpengehäuse 12 eine Abdeckplatte 16 vorgesehen, welche das Öl von dem rotierenden Außenläufer abweist.The gas in the compressor housing 1 is set in rotation by the external rotor of the external rotor motor 3. This rotation creates a centrifugal pressure field that forces the oil inward at the bottom of the compressor housing 1. In order to prevent it from being caught by the rotating outer rotor and set in vigorous motion, as a result of which the oil would be mixed with gas bubbles, a cover plate 16 is provided on the pump housing 12 which repels the oil from the rotating outer rotor.

Es sei noch erwähnt, daß das von der Reibungspumpe in den Bohrungskanal 5 geförderte Öl über diesen Bohrungskanal zu dem Verdichter und gegebenenfalls auch zu den Lagerstellen des Antriebsmotors geführt wird. Hierzu zweigen an den entsprechenden Stellen weitere Kanäle von dem Bohrungskanal ab, durch die das Öl dann an die gewünschten Stellen gelangt.It should also be mentioned that the oil pumped into the bore channel 5 by the friction pump is conducted via this bore channel to the compressor and possibly also to the bearing points of the drive motor. For this purpose, additional channels branch off from the bore channel at the corresponding points, through which the oil then reaches the desired points.

Claims (6)

1. Compressor unit, in which the compressor and its drive motor in the form of an external-rotor motor are arranged on a common fixed shaft in a unit housing, and in which a lubricant supply pump designed as a friction pump is provided on the end of the fixed shaft remote from the compressor, the outlet of which pump opens into a bored channel provided in the fixed shaft and whose inflow aperture projects into the lubricant supply store on the floor of the unit housing, and which pump also comprises as a rotor a hollow cylinder coupled to the external rotor, characterised in that a pump housing (12) having an annular space (9) between an inner and an outer housing part (10 and 11) is arranged on the shaft (4), and the hollow cylinder (8) projects into the annular space (9), so that an inner and an outer gap (21 and 22) are formed between the housing parts (10 and 11) of the pump housing (12) and the hollow cylinder (8), in that also a connection is provided between the inner and outer gaps (21 and 22) and at least one constriction acting as an interrupter (25) is provided on the pump housing (12) on both sides of the hollow cylinder (8).
2. Compressor unit according to claim 1, characterised in that the hollow cylinder (8) is moulded onto the bearing cap (7) of the external rotor.
3. Compressor unit according to claim 1 or 2, characterised in that a plurality of through-apertures (28) are provided in the wall of the hollow cylinder (8).
4. Compressor unit according to claim 1, characterised in that the housing parts (10 and 11) of the pump housing (12) limiting the annular space (9) are of a cylindrical design, and separate interrupter parts (25) are inserted in front of each outlet (17) and are secured to the housing parts (10and 11) of the pump housing (12).
5. Compressor unit according to one of the above claims, characterised in that a plurality of annular discs (20) are stacked up in the axial gap between the frontal face (19) of the hollow cylinder (8) and the pump housing, whose stacked height is equal to the minimum width of the axial gap, which is stipulated by tolerances.
6. Compressor unit according to claim 5, characterised in that the discs (20) are of a slightly corrugated design.
EP82104890A 1981-06-15 1982-06-03 Compressor aggregate Expired EP0069859B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82104890T ATE16518T1 (en) 1981-06-15 1982-06-03 COMPRESSOR UNIT.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19813123631 DE3123631A1 (en) 1981-06-15 1981-06-15 COMPRESSOR UNIT
DE3123631 1981-06-15

Publications (3)

Publication Number Publication Date
EP0069859A2 EP0069859A2 (en) 1983-01-19
EP0069859A3 EP0069859A3 (en) 1984-03-21
EP0069859B1 true EP0069859B1 (en) 1985-11-13

Family

ID=6134717

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82104890A Expired EP0069859B1 (en) 1981-06-15 1982-06-03 Compressor aggregate

Country Status (7)

Country Link
US (1) US4436490A (en)
EP (1) EP0069859B1 (en)
JP (1) JPS57212384A (en)
AT (1) ATE16518T1 (en)
DE (2) DE3123631A1 (en)
DK (1) DK151147C (en)
IE (1) IE52864B1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4681510A (en) * 1986-01-02 1987-07-21 Trd Corporation Pump for saturated liquid
US4899704A (en) * 1989-05-08 1990-02-13 Tecumseh Products Company Self-lubricating bearing
DE102006001174A1 (en) * 2006-01-08 2007-07-12 Obrist Engineering Gmbh reciprocating compressor

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE548405C (en) * 1932-04-19 Sulzer Akt Ges Geb OE catching device for stationary internal combustion engines
US2423719A (en) * 1940-01-05 1947-07-08 Muffly Glenn Motor-compressor unit lubrication
US2294742A (en) 1941-03-28 1942-09-01 Douglas Fraser & Sons Ltd Wharve driven flyer spindle
US2440593A (en) 1946-10-23 1948-04-27 Harry B Miller Radial vane pump mechanism
DE1016074B (en) * 1953-11-04 1957-09-19 Klein Schanzlin & Becker Ag Lubricating oil delivery device with a drum-like slinger
DE959435C (en) * 1954-04-18 1957-03-07 Voith Gmbh J M Friction pump
US3037457A (en) * 1959-08-26 1962-06-05 Gen Electric Pumps
DE1503408A1 (en) * 1966-10-15 1970-02-26 Danfoss As Encapsulated motor compressor, especially for refrigeration machines
DE1909610A1 (en) * 1969-02-26 1970-09-24 Licentia Gmbh Displacement pump
DE2428932C3 (en) * 1974-06-15 1979-11-08 Glyco-Metall-Werke Daelen & Loos Gmbh, 6200 Wiesbaden Liquid pump
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US4131396A (en) * 1977-04-07 1978-12-26 Sundstrand Corporation Hermetic compressor lubrication system with two-stage oil pump
US4239448A (en) 1977-10-25 1980-12-16 Beloit Corporation High pressure pump for fluid jet slitter
DE7736989U1 (en) * 1977-12-03 1979-05-03 Peschke, Rudolf, 6101 Gross-Bieberau FRICTION PUMP
AT354256B (en) * 1978-02-06 1979-12-27 Steyr Daimler Puch Ag PUMP WITH LOW CAPACITY FOR VISCOSE LIQUIDS, IN PARTICULAR LUBRICATING OIL

Also Published As

Publication number Publication date
IE52864B1 (en) 1988-03-30
DE3123631A1 (en) 1982-12-30
ATE16518T1 (en) 1985-11-15
EP0069859A2 (en) 1983-01-19
IE821412L (en) 1982-12-15
DK151147B (en) 1987-11-09
JPS636755B2 (en) 1988-02-12
DE3267390D1 (en) 1985-12-19
DK265182A (en) 1982-12-16
US4436490A (en) 1984-03-13
DK151147C (en) 1988-04-11
EP0069859A3 (en) 1984-03-21
JPS57212384A (en) 1982-12-27

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