EP0614012A1 - Scroll type positive displacement machine - Google Patents

Scroll type positive displacement machine Download PDF

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Publication number
EP0614012A1
EP0614012A1 EP94810009A EP94810009A EP0614012A1 EP 0614012 A1 EP0614012 A1 EP 0614012A1 EP 94810009 A EP94810009 A EP 94810009A EP 94810009 A EP94810009 A EP 94810009A EP 0614012 A1 EP0614012 A1 EP 0614012A1
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EP
European Patent Office
Prior art keywords
oil
drive shaft
bearing
housing
rotor
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.)
Granted
Application number
EP94810009A
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German (de)
French (fr)
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EP0614012B1 (en
Inventor
Fritz Spinnler
Roland Kolb
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Aginfor AG
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Aginfor AG fuer industrielle Forschung
Aginfor AG
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Publication of EP0614012A1 publication Critical patent/EP0614012A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/0207—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F01C1/0215—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F01C1/0223—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving with symmetrical double wraps
    • 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
    • F04C29/023—Lubricant distribution through a hollow driving shaft

Definitions

  • the invention relates to a displacement machine for compressible media with a plurality of spiral-shaped conveying spaces arranged in a fixed housing and with a displacer assigned to the conveying spaces, which is held on a rotor which can be driven eccentrically with respect to the housing in such a way that during operation each of its points is one of the peripheral walls of the Displacement chamber performs limited circular movement, for which purpose an eccentric disc is arranged on the drive shaft, on which the rotor is mounted by means of an oil-lubricated bearing.
  • Displacement machines of the spiral type are known for example from DE-C3-2 603 462.
  • a compressor constructed according to this principle is characterized by an almost pulsation-free conveyance of the gaseous working medium, for example consisting of air or an air-fuel mixture, and could therefore also be used advantageously for charging internal combustion engines.
  • the gaseous working medium for example consisting of air or an air-fuel mixture
  • a number of approximately crescent-shaped work spaces are enclosed along the displacement chamber between the spiral-shaped displacement body and the two peripheral walls of the displacement chamber. which move from the inlet through the displacement chamber to the outlet, their volume constantly being reduced and the pressure of the working medium being increased accordingly.
  • EP 0 354 342 A machine of the type mentioned at the outset is known from EP 0 354 342.
  • the drive shaft is supported in an angularly synchronous manner with the drive shaft Bearings. This is particularly evident in the displacement machine according to EP 0 354 342, in which the drive shaft is mounted in the housing in two ball bearings and the eccentric collar arranged on the drive shaft is supported by a needle bearing.
  • the rotor is penetrated by the drive shaft, so there are two sealing points on it.
  • the lubricating oil must be fed in and out from one side to the eccentric disk of the drive shaft.
  • the oil is fed in and out from the drive side or from the air side of the housing.
  • the drive shaft penetrates the housing on the drive side, which would make it two more places to seal with shaft sealing rings if the main eccentric bearing is supplied with the lubricating oil from this side. If the main eccentric bearing is supplied from the conveying or air side of the machine, only an additional shaft sealing point is necessary, since the drive shaft does not penetrate the housing on the conveying side.
  • the absolute minimum of the necessary shaft seals is therefore three.
  • the rotor of the machine is designated as a whole by 1.
  • Two, 180 ° offset, spiral-shaped displacers are arranged on both sides of the disk 2. These are strips 3a, 3b which are held vertically on the pane 2. In the example shown, the spirals themselves are formed from a plurality of circular arcs adjoining one another. 4 with the hub is designated with which the disc 2 is mounted on the bearing 22 on an eccentric 23. This eccentric disk is in turn part of the drive shaft 24.
  • FIG. 1 shows the housing half 7a shown on the left in FIG. 2 of the machine housing, which is composed of two halves 7a, 7b and is connected to one another via fastening eyes 8 for receiving screw connections.
  • 11a and 11b denote the delivery spaces, which are offset from one another by 180 and are worked into the two housing halves in the manner of a spiral slot. They each run from an inlet 12a, 12b arranged on the outer circumference of the spiral in the housing to an outlet 13 provided in the interior of the housing and common to both delivery spaces (FIG. 2). They have essentially parallel cylinder walls 14a, 14b, 15a, 15b which are arranged at a constant distance from one another and which, in the present case, like the displacer bodies of the disk 2, comprise a spiral of approximately 360 °.
  • the displacer 3a, 3b engage, the curvature of which is dimensioned such that the strips almost touch the inner and outer cylinder walls of the housing at several, for example at two points. Seals are inserted in corresponding grooves on the free end faces of the strips 3a, 3b and the webs 45, 46. With them, the working rooms against the side walls of the housing respectively. sealed against the displacement disc.
  • the drive and the guide of the rotor 1 are provided by the two spaced-apart eccentric arrangements 23, 24 and. 26, 27.
  • the drive shaft 24 is mounted on the drive side in a roller bearing 17 and on the air side in a slide bearing 18. At its end protruding from the housing half 7a, it is provided with a V-belt pulley 19 for the drive.
  • Counterweights 20 are arranged on the drive shaft 24 to compensate for the inertial forces arising when the rotor is eccentrically driven.
  • the guide shaft 27 is mounted within the housing half 7a by means of a roller bearing 28. In order to achieve clear guidance of the rotor in the dead center positions, the two eccentric arrangements are synchronized with a precise angle via a toothed belt drive 16.
  • This double eccentric drive ensures that all points of the rotor disc and thus also all points of the two strips 3a and 3b perform a circular displacement movement.
  • crescent-shaped workrooms enclosing the working medium result on both sides of the bars, which are displaced by the delivery chambers during the drive of the rotor disk in the direction of the outlet. The volumes of these working spaces decrease and the pressure of the working fluid is increased accordingly.
  • the bearings 18 and 22 are shown. These require an oil supply.
  • Lubricant preferably oil
  • lubricant is passed through a bore 29 in the housing half 7a to the plain bearing 18.
  • the fresh oil reaches the oil space 54 through a recess 30 in the slide bearing bore 18.
  • the recess 30 is open with respect to the drive shaft 24 and supplies the slide bearing 18 with oil.
  • the depression 30 causes the throttling and the quantity control of the oil fed into the bore 29 under pressure.
  • a longitudinal bore 53 is made in the drive shaft 24, into which the oil guide sleeve 39 is held at points 58, 58 ′, for example by a press fit in the drive shaft 24.
  • the outer diameter of the sleeve itself is tapered in the middle section 62, as a result of which a second oil channel 60 is formed in an extremely simple manner, which is separate from the first oil channel 59.
  • the oil flowing into the oil space 54 through the recess in the slide bearing 18 can pass through the central bore 59 in the sleeve 39 into the oil space 61 formed by the longitudinal bore 53 in the drive shaft 24, from where the oil through the radial bore 31 to the bearing 22 can reach.
  • the back-flowing oil passes through the radial bore 50 into the oil space 55, which is connected to the bore 57 in the housing 7a.
  • the oil space 55 is sealed by the shaft sealing ring 56 against the outlet 13 carrying the working medium.

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

Abstract

A positive displacement machine for compressible media has a displacer which is held in such a way on a disc-shaped rotor (1) which is eccentrically drivable with respect to the casing, that during operation each of its points carries out a circular movement. To this end, there is arranged on a drive shaft (24) an eccentric disc (23) on which the rotor (1) is supported by means of an oil-lubricated bearing arrangement (22). The lubricating oil is supplied and discharged on the side facing away from the drive side of the drive shaft (24), the separation of the oil inflow (29) from the oil return flow (57) being effected in the casing (7a) by a plain bearing (sleeve bearing, journal) (18) which at both ends has one oil chamber (54, 55) each. The separation of the oil streams is effected by a recess (30) which does not extend over the entire length of the plain bearing (18). By means of this recess, the plain bearing (18) is likewise supplied with oil. The recess (30) connects the oil inflow hole (29) in the casing (7a) to the oil chamber (54). <IMAGE>

Description

Gebiet der ErfindungField of the Invention

Die Erfindung betrifft eine Verdrängermaschine für kompressible Medien mit mehreren in einem feststehenden Gehäuse angeordneten spiralförmigen Förderräumen und mit einem den Förderräumen zugeordneten Verdrängerkörper, der auf einem gegenüber dem Gehäuse exzentrisch antreibbaren Läufer derart gehalten ist, dass während des Betriebes jeder seiner Punkte eine von den Umfangswänden der Verdrängerkammer begrenzte Kreisbewegung ausführt, wozu auf der Antriebswelle eine Exzenterscheibe angeordnet ist, auf welcher der Läufer mittels einer ölgeschmierten Lagerung gelagert ist.The invention relates to a displacement machine for compressible media with a plurality of spiral-shaped conveying spaces arranged in a fixed housing and with a displacer assigned to the conveying spaces, which is held on a rotor which can be driven eccentrically with respect to the housing in such a way that during operation each of its points is one of the peripheral walls of the Displacement chamber performs limited circular movement, for which purpose an eccentric disc is arranged on the drive shaft, on which the rotor is mounted by means of an oil-lubricated bearing.

Stand der TechnikState of the art

Verdrängermaschinen der Spiralbauart sind bespielsweise durch die DE-C3-2 603 462 bekannt. Ein nach diesem Prinzip aufgebauter Verdichter zeichnet sich durch eine nahezu pulsationsfreie Förderung des bespielsweise aus Luft oder einem Luft-Kraftstoffgemisch bestehenden gasförmigen Arbeitsmittels aus und könnte daher unter anderem auch für die Aufladung von Brennkraftmaschinen mit Vorteil herangezogen werden. Während des Betriebes eines solchen Kompressors werden entlang der Verdrängerkammer zwischen dem spiralförmig ausgebildeten Verdrängerkörper und den beiden Umfangswänden der Verdrängerkammer mehrere, etwa sichelförmige Arbeitsräume eingeschlossen, die sich von dem Einlass durch die Verdrängerkammer hindurch zum Auslass hin bewegen, wobei ihr Volumen ständig verringert und der Druck des Arbeitsmittels dementsprechend erhöht wird.Displacement machines of the spiral type are known for example from DE-C3-2 603 462. A compressor constructed according to this principle is characterized by an almost pulsation-free conveyance of the gaseous working medium, for example consisting of air or an air-fuel mixture, and could therefore also be used advantageously for charging internal combustion engines. During the operation of such a compressor, a number of approximately crescent-shaped work spaces are enclosed along the displacement chamber between the spiral-shaped displacement body and the two peripheral walls of the displacement chamber. which move from the inlet through the displacement chamber to the outlet, their volume constantly being reduced and the pressure of the working medium being increased accordingly.

Eine Maschine der eingangs genannten Art ist bekannt aus der EP 0 354 342. Bei dieser Maschine sowie im übrigen bei allen bekannten Spiralverdichtern, bei denen der zur translatorischen Führung des Läufers eine mit der Antriebswelle winkelsynchron laufende Führungswelle vorgesehen ist, erfolgt die Lagerung der Antriebswelle mit Wälzlagern. Dies ist besonders gut ersichtlich bei der Verdrängermaschine nach EP 0 354 342, bei welcher die Antriebswelle im Gehäuse in zwei Kugellagern und der auf der Antriebswelle angeordnete Exzenterbund über ein Nadellager gelagert ist.A machine of the type mentioned at the outset is known from EP 0 354 342. In this machine and, moreover, in all known scroll compressors in which the guide shaft is provided for translatory guiding of the rotor, the drive shaft is supported in an angularly synchronous manner with the drive shaft Bearings. This is particularly evident in the displacement machine according to EP 0 354 342, in which the drive shaft is mounted in the housing in two ball bearings and the eccentric collar arranged on the drive shaft is supported by a needle bearing.

Diese Art der Abstützung des Läufers auf der Exzenterscheibe erfordert wegen der hohen Fliehkraftbelastung und der Exzenterbewegung eine Ölschmierung des Exzenterlagers, wobei das Öl dem Lager über ein Bohrungssystem in der Antriebswelle zugeleitet wird. In der DE 33 20 086 A1 ist ein solches Bohrungssystem beschrieben.This type of support of the rotor on the eccentric requires oil lubrication of the eccentric bearing due to the high centrifugal force and the eccentric movement, the oil being supplied to the bearing via a bore system in the drive shaft. Such a drilling system is described in DE 33 20 086 A1.

Darstellung der ErfindungPresentation of the invention

Entsprechend der Anzahl der Lagerstellen und der Anzahl der Gehäuse- resp. Läuferdurchdringungen durch die Antriebswelle, ist die Anzahl der für das Öl notwendigen Wellenabdichtstellen gegeben. Bei einer Ölführung nach der in der DE 33 20 086 A1 dargestellten Art werden fünf Wellendichtringe für die Abdichtung der Antriebswelle benötigt. Wellendichtringe sind als Schwachstellen der Maschine zu betrachten und ihre Anzahl ist auf das absolut notwendige Minimum zu reduzieren. Der Erfindung liegt daher die Aufgabe zugrunde, eine Ölführung zu definieren, die die Anzahl der Wellendichtringe auf das absolut notwendige Minimum reduziert.According to the number of bearings and the number of housing resp. Rotor penetrations through the drive shaft, the number of shaft sealing points necessary for the oil is given. With an oil guide according to the type shown in DE 33 20 086 A1, five shaft sealing rings are required for sealing the drive shaft. Shaft sealing rings are to be regarded as weak points of the machine and their number must be reduced to the absolutely necessary minimum. The invention is therefore based on the object of defining an oil guide which reduces the number of shaft sealing rings to the absolutely necessary minimum.

Erfindungsgemäss wird diese Aufgabe mit den kennzeichnenden Merkmalen des Patentanapruchs 1 gelöst.According to the invention, this object is achieved with the characterizing features of patent claim 1.

Das einzige Lager der Spiralmaschine, welches wie eingangs beschrieben, wegen der hohen Belastung und der Fliehkrafteinwirkung ein Ölschmierung benötigt, ist das Exzenterlager des Läufers, das sogenannte Hauptexzenterlager. Der Läufer wird von der Antriebswelle durchdrungen, es sind somit zwei Abdichtstellen bei diesem gegeben. Das Schmieröl muss, um die Anzahl der abzudichtenden Stellen zu minimieren, von einer Seite zu der Exzenterscheibe der Antriebswelle zu- und abgeführt werden. Hier bestehen grundsätzlich zwei Möglichkeiten: Man führt das Öl von der Antriebsseite zu und ab oder von der Luftseite des Gehäuses. Das Gehäuse wird auf der Antriebsseite von der Antriebswelle durchdrungen, es wären dadurch zwei weitere Stellen durch Wellendichtringe abzudichten, wenn man das Hauptexzenterlager von dieser Seite mit dem Schmieröl versorgt. Bei einer Versorgung des Hauptexzenterlagers von der Förder- oder Luftseite der Maschine aus, ist nur noch eine zusätzliche Wellenabdichtstelle notwendig, da die Antriebswelle das Gehäuse auf der Förderseite nicht durchdringt. Das absolute Minimum der notwendigen Wellendichtringe beträgt somit drei.The only bearing of the spiral machine, which, as described in the beginning, requires oil lubrication due to the high load and centrifugal force, is the eccentric bearing of the rotor, the so-called main eccentric bearing. The rotor is penetrated by the drive shaft, so there are two sealing points on it. In order to minimize the number of points to be sealed, the lubricating oil must be fed in and out from one side to the eccentric disk of the drive shaft. There are basically two options here: The oil is fed in and out from the drive side or from the air side of the housing. The drive shaft penetrates the housing on the drive side, which would make it two more places to seal with shaft sealing rings if the main eccentric bearing is supplied with the lubricating oil from this side. If the main eccentric bearing is supplied from the conveying or air side of the machine, only an additional shaft sealing point is necessary, since the drive shaft does not penetrate the housing on the conveying side. The absolute minimum of the necessary shaft seals is therefore three.

Es ist eine weitere Aufgabe der Erfindung, eine äusserst einfache und kostengünstige Realisierung der Ölführung in der Welle zu definieren. In der DE 33 20 086 A1 ist eine Ölführung bei einseitiger Zu- und Abführung angedeutet. Die Aufgabe, die Ölströme zu trennen ist aber nur im Bereich der Welle dargestellt, nicht aber im Bereich der Schnittstelle Welle/Gehäuse. Zudem ist in der genannten Offenlegungschrift die angedeutete Lösung für die Fälle vorgesehen, wo die Antriebswelle nur auf einer Seite im Gehäuse fliegend gelagert ist. Bei einer solchen Ausführung kann die Anzahl der erforderlichen Wellendichtringe nur bedingt unter vier reduziert werden, da bei der fliegenden Lagerung das Gehäuse bei der Lagerstelle durchdrungen werden muss, weil ausserhalb des Gehäuses die Antriebs-Riemen- scheibe aufgenommen werden muss.It is a further object of the invention to define an extremely simple and inexpensive implementation of the oil guidance in the shaft. In DE 33 20 086 A1 an oil guide with one-sided supply and discharge is indicated. The task of separating the oil flows is only shown in the area of the shaft, but not in the area of the shaft / housing interface. In addition, the solution indicated is provided for the cases in which the drive shaft is overhung in the housing on only one side in the aforementioned publication. With such a design, the number of required shaft sealing rings can be reduced to less than four since the housing must be penetrated at the bearing point during on-the-fly storage because the drive pulley must be accommodated outside the housing.

Es ist somit eine zusätzliche Aufgabe der Erfindung, die Aufteilung der Ölströme (Zu- und Abfluss) an der Schnittstelle Antriebswelle/Gehäuse zu definieren. Dies wird dadurch erreicht, indem das in der luftseitigen Gehäusehälfte sich befindende Lager der Antriebswelle als Gleitlager ausgeführt wird.It is therefore an additional object of the invention to define the distribution of the oil flows (inflow and outflow) at the drive shaft / housing interface. This is achieved in that the bearing of the drive shaft located in the air-side housing half is designed as a plain bearing.

Kurze Beschreibung der ZeichnungBrief description of the drawing

In der Zeichnung ist ein Ausführungsbeispiel der Erfindung schematisch dargestellt.In the drawing, an embodiment of the invention is shown schematically.

Es zeigen:

Fig. 1
einen Querschnitt durch das antriebsseitige Gehäuseteil der Verdrängermaschine nach Linie I-I in Fig. 2;
Fig. 2
einen Längsschnitt durch den Lader nach Linie II-II in Fig. 1 mit schematisch eingetragenen Schmiermittelbohrungen;
Fig. 3
einen Längsschnitt durch die Antriebswelle.
Show it:
Fig. 1
a cross section through the drive-side housing part of the displacement machine according to line II in Fig. 2;
Fig. 2
a longitudinal section through the loader according to line II-II in Figure 1 with schematically registered lubricant holes.
Fig. 3
a longitudinal section through the drive shaft.

Weg zur Ausführung der ErfindungWay of carrying out the invention

Zwecks Erläuterung der Funktionsweise des Verdichters, welche nicht Gegenstand der Erfindung ist, wird auf die bereits genannte DE-C3-2 603 462 verwiesen. Nachstehend wird nur der für das Verständnis notwendige Maschinenaufbau und Prozessablauf kurz beschrieben.In order to explain the operation of the compressor, which is not the subject of the invention, reference is made to the already mentioned DE-C3-2 603 462. In the following, only the machine structure and process flow necessary for understanding are briefly described.

In Fig.1 ist das Gehäuse mit den Förderräumen und dem eingelegten Verdränger gezeigt. Mit 1 ist der Läufer der Maschine insgesamt bezeichnet. An beiden Seiten der Scheibe 2 sind je zwei , um 180°versetzte, spiralförmige verlaufende Verdrängerkörper angeordnet. Es handelt sich um Leisten 3a, 3b, die senkrecht auf der Scheibe 2 gehalten sind. Die Spiralen selbst sind im gezeigten Beispiel aus mehreren, aneinender anschliessenden Kreisbögen gebildet. Mit 4 ist die Nabe bezeichnet, mit welcher die Scheibe 2 über dem Lager 22 auf einer Exzenterscheibe 23 gelagert ist. Diese Exzenterscheibe ist ihrerseits Teil der Antriebswelle 24.1 shows the housing with the delivery spaces and the inserted displacer. The rotor of the machine is designated as a whole by 1. Two, 180 ° offset, spiral-shaped displacers are arranged on both sides of the disk 2. These are strips 3a, 3b which are held vertically on the pane 2. In the example shown, the spirals themselves are formed from a plurality of circular arcs adjoining one another. 4 with the hub is designated with which the disc 2 is mounted on the bearing 22 on an eccentric 23. This eccentric disk is in turn part of the drive shaft 24.

Mit 5 ist ein radial ausserhalb der Leisten 3a, 3b angeordnetes Auge bezeichnet für die Aufnahme eines Führungslagers 25, welches auf einem Exzenterbolzen 26 aufgezogen ist. Dieser ist seinerseits Teil einer Führungswelle 27. Am Spiralende sind in der Scheibe vier Durchtrittsfenster 6, 6' vorgesehen, damit das Medium von einer Scheibenseite zur anderen gelangen kann, beispielsweise um in einen nur einseitig angeordneten zentralen Auslass abgezogen zu werden.5 with a radially outside the strips 3a, 3b arranged eye is designated for receiving a guide bearing 25 which is mounted on an eccentric bolt 26. This in turn is part of a guide shaft 27. At the spiral end, four passage windows 6, 6 'are provided in the disk so that the medium can get from one disk side to the other, for example to be drawn off into a central outlet arranged only on one side.

In Fig. 1 ist die in Fig. 2 links dargestellte Gehäusehälfte 7a des aus zwei Hälften 7a, 7b zusammengesetzten, über Befestigungsaugen 8 zur Aufnahme von Verschraubungen miteinander verbundenen Maschinengehäuses gezeigt. 11a und 11b bezeichnen die jeweils um 180 gegeneinander versetzten Förderräume, die nach Art eines spiralförmigen Schlitzes in die beiden Gehäusehälften eingearbeitet sind. Sie verlaufen von je einem am äusseren Umfang der Spirale im Gehäuse angeordneten Einlass 12a, 12b zu einem im Gehäuseinneren vorgesehenen, beiden Förderräumen gemeinsamen Auslass 13 (Fig. 2). Sie weisen im wesentlichen parallele, in gleichbleibendem Abstand zueinander angeordnete Zylinderwände 14a, 14b, 15a, 15b auf, die im vorliegenden Fall wie die Verdrängerkörper der Scheibe 2 eine Spirale von ca. 360° umfassen.1 shows the housing half 7a shown on the left in FIG. 2 of the machine housing, which is composed of two halves 7a, 7b and is connected to one another via fastening eyes 8 for receiving screw connections. 11a and 11b denote the delivery spaces, which are offset from one another by 180 and are worked into the two housing halves in the manner of a spiral slot. They each run from an inlet 12a, 12b arranged on the outer circumference of the spiral in the housing to an outlet 13 provided in the interior of the housing and common to both delivery spaces (FIG. 2). They have essentially parallel cylinder walls 14a, 14b, 15a, 15b which are arranged at a constant distance from one another and which, in the present case, like the displacer bodies of the disk 2, comprise a spiral of approximately 360 °.

Zwischen diesen Zylinderwänden greifen die Verdrängerkörper 3a,3b ein, deren Krümmung so bemessen ist, dass die Leisten die inneren und die äusseren Zylinderwände des Gehäuses an mehreren, beispielsweise an zwei Stellen nahezu berühren. An den freien Stirnseiten der Leisten 3a,3b und der Stege 45,46 sind Dichtungen in entsprechende Nuten eingelegt. Mit ihnen werden die Arbeitsräume gegen die Seitenwände des Gehäuses resp. gegen die Verdrängerscheibe gedichtet.Between these cylinder walls, the displacer 3a, 3b engage, the curvature of which is dimensioned such that the strips almost touch the inner and outer cylinder walls of the housing at several, for example at two points. Seals are inserted in corresponding grooves on the free end faces of the strips 3a, 3b and the webs 45, 46. With them, the working rooms against the side walls of the housing respectively. sealed against the displacement disc.

Den Antrieb und die Führung des Läufers 1 besorgen die zwei beabstandeten Exzenteranordnungen 23, 24 resp. 26, 27. Die Antriebswelle 24 ist antriebsseitig in einem Wälzlager 17 und luftseitig in einem Gleitlager 18 gelagert. An ihren aus der Gehäusehälfte 7a herausragenden Ende ist sie mit einer Keilriemenscheibe 19 für den Antrieb versehen. Auf der Antriebswelle 24 sind Gegengewichte 20 angeordnet zum Ausgleich der beim exzentrischen Antrieb des Läufers entstehenden Massenkräfte. Die Führungswelle 27 ist innerhalb der Gehäusehälfte 7a mittels eines Wälzlagers 28 gelagert. Um in den Totpunktlagen eine eindeutige Führung des Läufers zu erzielen, sind die beiden Exzenter- anordnungen über einen Zahnriemenantrieb 16 winkelgenau synchronisiert. Dieser Doppelexzenterantrieb sorgt dafür, dass alle Punkte der Läuferscheibe und damit auch alle Punkte der beiden Leisten 3a und 3b eine kreisförmige Verschiebebewegung ausführen. Infolge der mehrfach abwechselnden Annäherungen der Leisten 3a,3b an die inneren und äusseren Zylinderwände der zugeordneten Förderkammern ergeben sich auf beiden Seiten der Leisten sichelförmige, das Arbeitsmedium einschliessende Arbeitsräume, die während des Antriebs der Läuferscheibe durch die Förderkammern in Richtung auf den Auslass verschoben werden. Hierbei verringern sich die Volumina dieser Arbeitsräume und der Druck des Arbeitsmittels wird entsprechend erhöht.The drive and the guide of the rotor 1 are provided by the two spaced-apart eccentric arrangements 23, 24 and. 26, 27. The drive shaft 24 is mounted on the drive side in a roller bearing 17 and on the air side in a slide bearing 18. At its end protruding from the housing half 7a, it is provided with a V-belt pulley 19 for the drive. Counterweights 20 are arranged on the drive shaft 24 to compensate for the inertial forces arising when the rotor is eccentrically driven. The guide shaft 27 is mounted within the housing half 7a by means of a roller bearing 28. In order to achieve clear guidance of the rotor in the dead center positions, the two eccentric arrangements are synchronized with a precise angle via a toothed belt drive 16. This double eccentric drive ensures that all points of the rotor disc and thus also all points of the two strips 3a and 3b perform a circular displacement movement. As a result of the multiple alternating approaches of the bars 3a, 3b to the inner and outer cylinder walls of the associated delivery chambers, crescent-shaped workrooms enclosing the working medium result on both sides of the bars, which are displaced by the delivery chambers during the drive of the rotor disk in the direction of the outlet. The volumes of these working spaces decrease and the pressure of the working fluid is increased accordingly.

In Fig. 3 sind die Lager 18 und 22 dargestellt. Diese bedürfen einer Ölversorgung. Aus einer nicht dargestellten Schmiermittelquelle wird Schmiermittel, vorzugsweise Öl, über eine Bohrung 29 in der Gehäusehälfte 7a zum Gleitlager 18 geleitet. Durch eine Vertiefung 30 in der Gleitlagerbohrung 18 gelangt das frische Öl in den Ölraum 54. Die Vertiefung 30 ist gegenüber der Antriebswelle 24 offen und versorgt das Gleitlager 18 mit Öl. Gleichzeitig bewirkt die Vertiefung 30 die Drosselung und die Mengenregelung des unter Druck in die Bohrung 29 eingespeisten Öles.3, the bearings 18 and 22 are shown. These require an oil supply. From a not shown Lubricant source, lubricant, preferably oil, is passed through a bore 29 in the housing half 7a to the plain bearing 18. The fresh oil reaches the oil space 54 through a recess 30 in the slide bearing bore 18. The recess 30 is open with respect to the drive shaft 24 and supplies the slide bearing 18 with oil. At the same time, the depression 30 causes the throttling and the quantity control of the oil fed into the bore 29 under pressure.

In der Antriebswelle 24 ist eine Längsbohrung 53 angebracht, in welche die Ölführungshülse 39 an den Stellen 58, 58' beispielsweise durch einen Pressitz in der Antriebswelle 24 gehalten ist. Die Hülse selbst ist in der mittleren Partie 62 im Aussendurchmesser verjüngt, wodurch auf äusserst einfache Weise ein zweiter Ölkanal 60 gebildet wird, welcher vom ersten Ölkanal 59 getrennt ist. Das durch die Vertiefung im Gleitlager 18 in den Ölraum 54 einströmende Öl kann durch die in der Hülse 39 sich befindende Zentralbohrung 59 in den durch die Längsbohrung 53 in der Antriebswelle 24 gebildeten Ölraum 61 gelangen, von wo das Öl durch die Radialbohrung 31 zum Lager 22 gelangen kann.A longitudinal bore 53 is made in the drive shaft 24, into which the oil guide sleeve 39 is held at points 58, 58 ′, for example by a press fit in the drive shaft 24. The outer diameter of the sleeve itself is tapered in the middle section 62, as a result of which a second oil channel 60 is formed in an extremely simple manner, which is separate from the first oil channel 59. The oil flowing into the oil space 54 through the recess in the slide bearing 18 can pass through the central bore 59 in the sleeve 39 into the oil space 61 formed by the longitudinal bore 53 in the drive shaft 24, from where the oil through the radial bore 31 to the bearing 22 can reach.

Das Öl tritt in die Ölräume 38 des Läufers 1 aus und wird durch die Wellendichtringe 23 gegen den Auslass 13 abgedichtet. Der Ölrückfluss aus dem Lager 22 erfolgt durch die Radialbohrung 33, welche den einen Ölraum 38 mit dem Ölkanal 60 verbindet. Das rückströmende Öl gelangt durch die Radialbohrung 50 in den Ölraum 55, welcher mit der Bohrung 57 im Gehäuse 7a verbunden ist. Der Ölraum 55 ist durch den Wellendichtring 56 gegen den das Arbeitsmedium führenden Auslass 13 abgedichtet.The oil exits into the oil spaces 38 of the rotor 1 and is sealed against the outlet 13 by the shaft sealing rings 23. The oil return flow from the bearing 22 takes place through the radial bore 33, which connects the one oil space 38 to the oil channel 60. The back-flowing oil passes through the radial bore 50 into the oil space 55, which is connected to the bore 57 in the housing 7a. The oil space 55 is sealed by the shaft sealing ring 56 against the outlet 13 carrying the working medium.

BezugszeichenlisteReference list

11
Läuferrunner
22nd
Scheibedisc
3a, 3b3a, 3b
Leistestrip
44th
Nabehub
55
Augeeye
66
Durchbruchbreakthrough
7a, 7b7a, 7b
GehäusehälfteHalf of the housing
88th
BefestigungsaugeMounting eye
11a, 11b11a, 11b
FörderraumFunding area
12a, 12b12a, 12b
Einlassinlet
1313
AuslassOutlet
14a, 14b14a, 14b
ZylinderwandCylinder wall
15a, 15b15a, 15b
ZylinderwandCylinder wall
1616
ZahnriementriebTiming belt drive
1717th
Wälzlagerroller bearing
1818th
Gleitlagerbearings
1919th
KeilriemenscheibeV-belt pulley
2020th
Gegengewicht an 24Counterweight on 24
2222
Lagerwarehouse
2323
ExzenterscheibeEccentric disc
2424th
Antriebswelledrive shaft
2525th
FührungslagerGuide bearings
2626
ExzenterbolzenEccentric bolt
2727
FührungswelleGuide shaft
2828
Wälzlagerroller bearing
2929
Bohrung in 7aHole in 7a
3030th
Vertiefungdeepening
3131
Radialbohrung in 24Radial bore in 24
3232
Wellendichtring an 23Shaft seal on 23
3333
Radialbohrung in 24Radial bore in 24
3434
RotationsachseAxis of rotation
3838
Ölräume in 1Oil spaces in 1st
3939
Ölführungs-HülseOil guide sleeve
4545
Stegweb
4646
Stegweb
5050
Radialbohrung in 24Radial bore in 24
5353
Längsbohrung in 24Longitudinal bore in 24
5454
ÖlraumOil room
5555
ÖlraumOil room
5656
WellendichtringShaft seal
5757
Ölrücklaufbohrung in 7aOil return hole in 7a
58, 58'58, 58 '
Befestigungsstelle für 39Attachment point for 39
5959
ÖlkanalOil channel
6060
ÖlkanalOil channel
6161
ÖlraumOil room
6262
Verjüngte Mittelpartie von 39Tapered middle section of 39

Claims (3)

Verdrängermaschine für kompressible Medien mit mehreren in einem feststehenden Gehäuse (7a, 7b) angeordneten spiralförmigen Förderräumen (11a, 11b) und mit einem den Förderräumen zugeordneten Verdrängerkörper (1-4), der auf einem gegenüber dem Gehäuse exzentrisch antreibbaren scheibenförmigen Läufer (1) derart gehalten ist, dass während des Betriebes jeder seiner Punkte eine von den Umfangswänden der Förderräume begrenzte Kreisbewegung ausführt, wozu auf der Antriebswelle (24) eine Exzenterscheibe (23) angeordnet ist, auf welcher der Läufer (1) mittels einer ölgeschmierten Lagerung (22) gelagert ist, dadurch gekennzeichnet,
dass das Schmieröl in der der Antriebsseite der Antriebswelle (24) abgewandten Seite zu- und abgeführt wird, wobei die Trennung des Ölzufluss (29) zum Ölrückfluss (57) im Gehäuse (7a) durch ein Gleitlager (18) erfolgt, welches auf beiden Enden je einen Ölraum (54, 55) aufweist.Displacement machine for compressible media with a plurality of spiral-shaped conveying spaces (11a, 11b) arranged in a fixed housing (7a, 7b) and with a displacer (1-4) assigned to the conveying spaces, which is arranged on a disc-shaped rotor (1) which can be driven eccentrically relative to the housing it is held that during operation each of its points executes a circular movement limited by the peripheral walls of the delivery spaces, for which purpose an eccentric disk (23) is arranged on the drive shaft (24) on which the rotor (1) is supported by means of an oil-lubricated bearing (22) is characterized by
that the lubricating oil is fed in and out in the side facing away from the drive side of the drive shaft (24), the separation of the oil inflow (29) from the oil return flow (57) in the housing (7a) being carried out by means of a slide bearing (18) which is on both ends each has an oil space (54, 55). Verdrängermaschine nach Anspruch 1, dadurch gekennzeichnet, dass die Trennung der Ölströme durch eine sich nicht über die ganze Länge des Gleitlagers (18) erstreckende Vertiefung (30) erfolgt und dass durch diese Vertiefung auch das Gleitlager (18) mit Öl versorgt wird, wobei die Vertiefung (30) die Ölzuflussbohrung (29) im Gehäuse (7a) mit dem Ölraum (54) verbindet.Displacement machine according to Claim 1, characterized in that the oil flows are separated by a depression (30) which does not extend over the entire length of the slide bearing (18) and that the slide bearing (18) is also supplied with oil through this depression, the Recess (30) connects the oil inlet bore (29) in the housing (7a) with the oil chamber (54). Verdrängermaschine nach Anspruch 2, dadurch gekennzeichnet, dass die Aufteilung der Ölströme in der Antriebswelle (24) durch eine in die Längsbohrung (53) eingepresste rotationssymmetrische Hülse (39) mit verjüngter Mittelpartie (62) erfolgt, wobei sich die Presspassungen der Hülse (39) an deren Enden (58, 58') befinden und dadurch zwei koaxiale Ölkanäle (59, 60) in der Antriebswelle (24) gebildet werden, die in ihrer Länge so bemessen sind, dass die Radialbohrungen (31,33) für die Versorgung des Lagers (22) in die Kanäle (59) resp. (60) münden.Displacement machine according to Claim 2, characterized in that the oil flows in the drive shaft (24) are divided by a rotationally symmetrical sleeve (39) with a tapered middle section (62) pressed into the longitudinal bore (53), the press fits of the sleeve (39) are located at the ends (58, 58 ') and thereby two coaxial oil channels (59, 60) are formed in the drive shaft (24), the length of which is dimensioned such that the radial bores (31, 33) for supplying the bearing (22) in the channels (59) resp. (60) flow out.
EP94810009A 1993-01-19 1994-01-10 Scroll type positive displacement machine Expired - Lifetime EP0614012B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH165/93 1993-01-19
CH16593 1993-01-19

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Publication Number Publication Date
EP0614012A1 true EP0614012A1 (en) 1994-09-07
EP0614012B1 EP0614012B1 (en) 1996-09-18

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ID=4180741

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EP94810009A Expired - Lifetime EP0614012B1 (en) 1993-01-19 1994-01-10 Scroll type positive displacement machine

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US (1) US5397223A (en)
EP (1) EP0614012B1 (en)
JP (1) JPH06241181A (en)
DE (1) DE59400648D1 (en)

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WO2008124950A1 (en) * 2007-04-17 2008-10-23 Spinnler Engineering Displacement machine according to the spiral principle
DE102007043595A1 (en) 2007-09-13 2009-03-19 Handtmann Systemtechnik Gmbh & Co. Kg Positive-displacement machine for compressible media, has lubrication system which accommodates lubricant reservoir in housing for closed lubrication cycle
DE102007043594A1 (en) 2007-09-13 2009-03-19 Handtmann Systemtechnik Gmbh & Co. Kg Displacement machine for compressible medium, has pressurization unit maintaining constant difference between pressures in conveying and lubricant chambers and acting on respective sides of sealing elements in operation
DE102010052186A1 (en) * 2010-11-24 2012-05-24 Handtmann Systemtechnik Gmbh & Co. Kg Positive-displacement machine for charge air for internal combustion engine, has counter pressure pump provided in transition region of fixed lubricant tank in pump rotor of lubricant supply and/or lubricant return flow line
EP2458216A3 (en) * 2010-11-24 2016-07-13 Handtmann Systemtechnik GmbH & Co. KG Compressor with lubricant pump

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DE102011103165A1 (en) * 2010-07-02 2012-01-05 Handtmann Systemtechnik Gmbh & Co. Kg Charging device for compressing charge air for an internal combustion engine
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US10865793B2 (en) 2016-12-06 2020-12-15 Air Squared, Inc. Scroll type device having liquid cooling through idler shafts
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US20200025199A1 (en) 2018-07-17 2020-01-23 Air Squared, Inc. Dual drive co-rotating spinning scroll compressor or expander
US11530703B2 (en) 2018-07-18 2022-12-20 Air Squared, Inc. Orbiting scroll device lubrication
US11473572B2 (en) 2019-06-25 2022-10-18 Air Squared, Inc. Aftercooler for cooling compressed working fluid
US11898557B2 (en) * 2020-11-30 2024-02-13 Air Squared, Inc. Liquid cooling of a scroll type compressor with liquid supply through the crankshaft
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Publication number Priority date Publication date Assignee Title
WO2008124950A1 (en) * 2007-04-17 2008-10-23 Spinnler Engineering Displacement machine according to the spiral principle
US8051813B2 (en) 2007-04-17 2011-11-08 Spinnler Engineering Scroll compressor with two scrolls
DE102007043595A1 (en) 2007-09-13 2009-03-19 Handtmann Systemtechnik Gmbh & Co. Kg Positive-displacement machine for compressible media, has lubrication system which accommodates lubricant reservoir in housing for closed lubrication cycle
DE102007043594A1 (en) 2007-09-13 2009-03-19 Handtmann Systemtechnik Gmbh & Co. Kg Displacement machine for compressible medium, has pressurization unit maintaining constant difference between pressures in conveying and lubricant chambers and acting on respective sides of sealing elements in operation
DE102007043594B4 (en) * 2007-09-13 2009-11-26 Handtmann Systemtechnik Gmbh & Co. Kg Spiral compressor with double spiral
DE102007043595B4 (en) * 2007-09-13 2009-12-24 Handtmann Systemtechnik Gmbh & Co. Kg Positive displacement machine according to the spiral principle
DE102010052186A1 (en) * 2010-11-24 2012-05-24 Handtmann Systemtechnik Gmbh & Co. Kg Positive-displacement machine for charge air for internal combustion engine, has counter pressure pump provided in transition region of fixed lubricant tank in pump rotor of lubricant supply and/or lubricant return flow line
DE102010052186B4 (en) * 2010-11-24 2012-08-30 Handtmann Systemtechnik Gmbh & Co. Kg Positive displacement machine for compressible media
EP2458216A3 (en) * 2010-11-24 2016-07-13 Handtmann Systemtechnik GmbH & Co. KG Compressor with lubricant pump

Also Published As

Publication number Publication date
JPH06241181A (en) 1994-08-30
US5397223A (en) 1995-03-14
DE59400648D1 (en) 1996-10-24
EP0614012B1 (en) 1996-09-18

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