EP0321781A1 - Fluid displacement apparatus with a spiral element - Google Patents

Fluid displacement apparatus with a spiral element Download PDF

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Publication number
EP0321781A1
EP0321781A1 EP88120414A EP88120414A EP0321781A1 EP 0321781 A1 EP0321781 A1 EP 0321781A1 EP 88120414 A EP88120414 A EP 88120414A EP 88120414 A EP88120414 A EP 88120414A EP 0321781 A1 EP0321781 A1 EP 0321781A1
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EP
European Patent Office
Prior art keywords
housing
rotor
guide
spiral
disk
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Granted
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EP88120414A
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German (de)
French (fr)
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EP0321781B1 (en
Inventor
Fritz Spinnler
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BBC Brown Boveri AG Switzerland
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BBC Brown Boveri AG Switzerland
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Priority to AT88120414T priority Critical patent/ATE72878T1/en
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    • 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

Definitions

  • the invention relates to a positive displacement machine for compressible media with at least four conveying spaces arranged in a fixed housing, with four conveying spaces, each housing half having two conveying spaces which are offset from one another by approximately 180.degree is assigned to this engaging displacement body, which is held as a spiral bar vertically on a disc-shaped rotor which can be driven eccentrically with respect to the housing, for guiding it in the housing a second guide eccentric arrangement arranged at a distance from a first drive eccentric arrangement is provided, with the flexible absorption of any length differences between the delivery space and displacement body a compensating means is provided on the rotor.
  • Displacement machines based on the spiral principle are known for example from DE-C3-2 603 462. These machines are characterized by an almost pulsation-free conveyance of, for example gaseous working medium consisting of air or an air-fuel mixture and can therefore also be used with advantage for supercharging purposes of internal combustion engines.
  • gaseous working medium consisting of air or an air-fuel mixture
  • several approximately crescent-shaped working spaces are trapped along the conveying chamber between the spiral-shaped displacer body and the two cylinder walls of the conveying chamber due to different curvature of the spiral shapes, which move from a working medium inlet through the conveying chamber to a working medium outlet , their volume is constantly reduced and the pressure of the working fluid is increased accordingly.
  • the displacement bodies are formed by spiral strips, which are held essentially vertically on the disk-shaped rotor and have a relatively large axial length in relation to their thickness. Similar conditions exist on the side of the fixed housing, where spiral, strip-like webs also remain between the conveying chambers with a relatively large length in the axial and circumferential directions in relation to the wall thickness.
  • a precise rolling of a displacement body according to the spiral principle by a translatory circular movement is achieved by a double crank drive, as is known for example from DE-A-3 230 979 and in which one crank drives and the second crank guides.
  • this known solution provides a transfer member which can be shifted in length, namely in the direction of the connecting line of the points of attack.
  • This transmission member consists of a support member which is adjustable in the guide arrangement of the rotor and which can be a sliding block which can be displaced in a parallel guide.
  • the parallel guide comprises one of the two bearings of the guide arrangement, via which a possible compensation of expansion differences can take place.
  • a bearing arrangement provided with an elastic bedding is provided on at least one of the points of attack, preferably at the point of application of the guide device .
  • This elastic bedding can be formed, for example, by a rubber-elastic ring which sits between the outer bearing ring and the bearing eye.
  • the object on which the invention is based is to provide, in a displacement machine of the type mentioned at the outset, a further possibility for accommodating changes in length occurring between two points of attack, which is as simple as possible and brings about an automatic compensation.
  • this is achieved in that the guide eye of the guide eccentric arrangement is connected to the disk-shaped rotor via a rib, which is designed as a tangential extension of one of the spiral strips at its end on the inlet side.
  • FIGS. 1 and 2 For the sake of clarity, the machine is shown in the disassembled state in FIGS. 1 and 2.
  • the rotor of the machine is designated as a whole by 1.
  • Arranged on both sides of the disk 2 are two, displaced by 180 ° to each other, spirally extending displacement body. It is strips 3.3 ', which are held vertically on the disc 2.
  • the spirals themselves are formed from a plurality of circular arcs adjoining one another.
  • the entry-side end of the strips 3.3 ' is each reinforced. 4 with the hub is designated with which the disc 2 is mounted on a roller bearing 22.
  • the bearing itself sits on an eccentric disk 23, which in turn is part of the drive shaft 24.
  • Fig. 1 the housing half 7 shown in Fig. 3 on the left of two halves (7,7 ') composed, via fastening eyes 8 for receiving screw connections interconnected machine housing is shown.
  • 9 symbolizes the holder for the drive shaft, 10 the holder for the guide shaft.
  • 11 and 11 ' denote the two delivery spaces, each offset by 180 °, which are incorporated in the manner of a spiral slot in the two housing halves. They each run from an inlet 12, 12 '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.
  • the drive and the guide of the rotor 1 are provided by the two spaced-apart eccentric arrangements (23, 24 and 26, 27, respectively).
  • the two eccentric arrangements are synchronized by a toothed belt drive 16 with precise angles. This double eccentric drive ensures that all points of the rotor disc and thus all points of the two strips 3 and 3 'perform a circular displacement movement.
  • crescent-shaped work spaces enclosing the working medium result on both sides of the strips, 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 are reduced and the pressure of the working fluid is increased accordingly.
  • Fig. 1 shows that the disc 2 - apart from the radially projecting eye 5 - closes radially with the strips 3.3 '.
  • the disk has to penetrate at least one half of the housing in the radial direction in the area of the inlets 12, 12 '. In the present case, this is done on the housing half 7 shown in FIG. 3 on the left lying webs 17, 17 'lowered by the amount of the pane thickness.
  • This measure has the advantage that in this housing half only on the inner webs 18, 18 'sealing strips are to be arranged, which seal the delivery spaces 11, 11' against the disk 2 against each other up to the outlet.
  • this transition is now formed as a circular shoulder 19,19 'with the radius R1.
  • the counter surface on the disc 2 is provided with a corresponding circular arc-shaped recess 20, 20 ', the radius R2 of this recess corresponding to the eccentricity e + radius R1.
  • the guide eye 5 is connected to the rotor 1 via a rib 29.
  • the rib 29 extends tangentially to the spiral. It is connected to the inlet end of the spiral strip 3.
  • Fig. 4 it is shown as a one-piece rib made with the rotor. Its width preferably corresponds to the width of the guide eye 5; its thickness is chosen so that the guide eye is elastic in the radial direction.
  • the rib 29 in which the rib 29 is made of the same material as the rotor, the rib can also be manufactured separately with or without a guide eye, for example from a material that is particularly suitable for the loads that occur.
  • the rib can be connected to the runner in any suitable manner, and in particular a joint arrangement can be provided.

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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)
  • Screw Conveyors (AREA)
  • Crushing And Pulverization Processes (AREA)
  • Catching Or Destruction (AREA)
  • Spinning Or Twisting Of Yarns (AREA)

Abstract

In a displacement machine for compressible media, having four delivery spaces arranged in a fixed housing, each housing half (7) has two delivery spaces (11, 11') which are offset by about 180 DEG with respect to one another and extend in a spiral shape from an inlet (12,12') to an outlet (13). Each delivery space is allocated a displacement body which fits into the latter and is held, as a spiral-shaped strip (3,3') perpendicularly on a disk-shaped rotor (1) which can be driven eccentrically with respect to the housing. For the guidance of said rotor a second eccentric guiding arrangement (10) arranged at an interval from a first eccentric drive arrangement (9) is provided in the housing. For the flexible accommodation of any length differences between delivery space and displacement body, the guide eye (5) of the eccentric guiding arrangement is connected to the disk-shaped rotor (1) via a stem (29) which is formed as a tangential extension on the inlet-side end of one of the spiral-shaped strips (3).

Description

Gebiet der ErfindungField of the Invention

Die Erfindung betrifft eine Verdrängermaschine für kompressi­ble Medien mit mindestens vier in einem feststehenden Gehäuse angeordneten Förderräumen, wobei bei vier Förderräumen jede Gehäusehälfte zwei um ca. 180° gegeneinander versetzte und spiralförmig von einem Einlass zu einem Auslass verlaufende Förderräume aufweist, und wobei jedem Förderraum ein in diesen eingreifenden Verdrängerkörper zugeordnet ist, der als spiral­förmige Leiste senkrecht auf einem gegenüber dem Gehäuse ex­zentrisch antreibbaren scheibenförmigen Läufer gehalten ist, zu dessen Führung im Gehäuse eine zu einer ersten Antriebsex­zenteranordnung mit Abstand angeordnete zweite Führungsexzen­teranordnung vorgesehen ist, wobei zur nachgiebigen Aufnahme von allfälligen Längendifferenzen zwischen Förderraum und Ver­drängerkörper ein Ausgleichsmittel am Läufer vorgesehen ist.The invention relates to a positive displacement machine for compressible media with at least four conveying spaces arranged in a fixed housing, with four conveying spaces, each housing half having two conveying spaces which are offset from one another by approximately 180.degree is assigned to this engaging displacement body, which is held as a spiral bar vertically on a disc-shaped rotor which can be driven eccentrically with respect to the housing, for guiding it in the housing a second guide eccentric arrangement arranged at a distance from a first drive eccentric arrangement is provided, with the flexible absorption of any length differences between the delivery space and displacement body a compensating means is provided on the rotor.

Stand der TechnikState of the art

Verdrängermaschinen nach dem Spiralprinzip sind beispielsweise aus der DE-C3-2 603 462 bekannt. Diese Maschinen zeichnen sich durch eine nahezu pulsationsfreie Förderung des beispielsweise aus Luft oder einem Luft-Kraftstoff-Gemisch bestehenden gas­förmigen Arbeitsmittel aus und können daher auch für Aufla­dezwecke von Brennkraftmaschinen mit Vorteil herangezogen wer­den. Während des Betriebes einer solchen als Verdichter arbei­tenden Verdrängermaschine werden entlang der Förderkammer zwischen dem spiralförmig ausgebildeten Verdrängerkörper und den beiden Zylinderwänden der Förderkammer infolge unter­schiedlicher Krümmung der Spiralformen mehrere, etwa sichel­förmige Arbeitsräume eingeschlossen, die sich von einem Ar­beitsmitteleinlass durch die Förderkammer hindurch zu einem Arbeitsmittelauslass hin bewegen, wobei ihr Volumen ständig verringert und der Druck des Arbeitsmittels entsprechend er­höht wird. Die Verdrängerkörper werden durch auf dem scheiben­förmigen Läufer im wesentlichen senkrecht stehend gehaltene, spiralförmige Leisten gebildet, die eine relativ grosse axiale Länge im Verhältnis zu ihrer Stärke aufweisen. Aehnliche Ver­hältnisse liegen auf der Seite des feststehenden Gehäuses vor, wo zwischen den Förderkammern ebenfalls spiralförmige, lei­stenartige Stege stehenbleiben mit im Verhältnis zur Wand­stärke relativ grosser Länge in axialer und in Umfangsrich­tung.Displacement machines based on the spiral principle are known for example from DE-C3-2 603 462. These machines are characterized by an almost pulsation-free conveyance of, for example gaseous working medium consisting of air or an air-fuel mixture and can therefore also be used with advantage for supercharging purposes of internal combustion engines. During the operation of such a displacement machine working as a compressor, several approximately crescent-shaped working spaces are trapped along the conveying chamber between the spiral-shaped displacer body and the two cylinder walls of the conveying chamber due to different curvature of the spiral shapes, which move from a working medium inlet through the conveying chamber to a working medium outlet , their volume is constantly reduced and the pressure of the working fluid is increased accordingly. The displacement bodies are formed by spiral strips, which are held essentially vertically on the disk-shaped rotor and have a relatively large axial length in relation to their thickness. Similar conditions exist on the side of the fixed housing, where spiral, strip-like webs also remain between the conveying chambers with a relatively large length in the axial and circumferential directions in relation to the wall thickness.

Eine präzise Abwälzung eines Verdrängerkörpers nach dem Spi­ralprinzip durch eine translatorische Kreisbewegung wird durch einen Doppelkurbeltrieb erreicht, wie er beispielsweise aus der DE-A-3 230 979 bekannt ist und bei dem eine Kurbel an­treibt und die zweite Kurbel führt. Um nun Längendifferenzen zwischen den beiden Angriffspunkten der Antriebs- und der Füh­rungsanordnung ausgleichen zu können, sieht diese bekannte Lösung ein längenverschiebbares Uebertragungsglied vor, und zwar in Richtung der Verbindungslinie der Angriffspunkte. Dieses Uebertragungsglied besteht aus einem in der Führungsan­ordnung des Läufers verstellbar gehaltenen Halterungsglied, welches ein Gleitstein sein kann, der in einer Parallelführung verschiebbar ist. Die Parallelführung umfasst eines der zwei Lager der Führungsanordnung, über die somit ein allfälliger Ausgleich von Dehnungsdifferenzen stattfinden kann.A precise rolling of a displacement body according to the spiral principle by a translatory circular movement is achieved by a double crank drive, as is known for example from DE-A-3 230 979 and in which one crank drives and the second crank guides. In order to be able to compensate for length differences between the two points of attack of the drive and the guide arrangement, this known solution provides a transfer member which can be shifted in length, namely in the direction of the connecting line of the points of attack. This transmission member consists of a support member which is adjustable in the guide arrangement of the rotor and which can be a sliding block which can be displaced in a parallel guide. The parallel guide comprises one of the two bearings of the guide arrangement, via which a possible compensation of expansion differences can take place.

Eine andere Lösung für dieses Problem ist in der DE-A-3 107231 beschrieben. Zur Vermeidung von unzulässig hohen Belastungen, die durch Toleranzsummierung bei der Fertigung oder durch unterschiedliche Wärmedehung zwischen den beiden Angriffspunk­ten an dem kreisenden Läufer auftreten können, ist an wenig­stens einem der Angriffspunkte, vorzugsweise an dem Angriffs­punkt der Führungsvorrichtung, eine mit einer elastischen Bet­tung versehene Lageranordnung vorgesehen. Diese elastische Bettung kann beispielsweise durch einen gummielastischen Ring gebildet sein, welcher zwischen Lageraussenring und Lagerauge sitzt.Another solution to this problem is described in DE-A-3 107231. In order to avoid impermissibly high loads that can occur due to tolerance accumulation during production or due to different thermal expansion between the two points of attack on the rotating rotor, a bearing arrangement provided with an elastic bedding is provided on at least one of the points of attack, preferably at the point of application of the guide device . This elastic bedding can be formed, for example, by a rubber-elastic ring which sits between the outer bearing ring and the bearing eye.

Darstellung der ErfindungPresentation of the invention

Die der Erfindung zugrundeliegende Aufgabe ist es, bei einer Verdrängermaschine der eingangs genannten Art eine weitere Möglichkeit zur Aufnahme von zwischen zwei Angriffspunkten auftretenden Längenänderungen zu schaffen, die möglichst einfach ausgebildet ist und einen selbsttätigen Ausgleich bewirkt.The object on which the invention is based is to provide, in a displacement machine of the type mentioned at the outset, a further possibility for accommodating changes in length occurring between two points of attack, which is as simple as possible and brings about an automatic compensation.

Erfindungsgemäss wird dies dadurch erreicht, dass das Füh­rungsauge der Führungsexzenteranordnung mit dem scheibenförmi­gen Läufer über eine Rippe verbunden ist, die als tangentiale Verlängerung einer der spiralförmigen Leisten an deren ein­lassseitigem Ende ausgebildet ist.According to the invention, this is achieved in that the guide eye of the guide eccentric arrangement is connected to the disk-shaped rotor via a rib, which is designed as a tangential extension of one of the spiral strips at its end on the inlet side.

Mit dieser Massnahme wir eine hohe Steifigkeit in tangentialer Richtung und eine hohe Elastizität in radialer Richtung er­reicht.With this measure, high rigidity in the tangential direction and high elasticity in the radial direction are achieved.

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 zeigt:

  • Fig. 1 ein Gehäuseteil der Verdrängermaschine
  • Fig. 2 einen Läufer mit erfindungsgemässem Führungsexzenter
  • Fig. 3 einen Längsschnitt durch die Verdrängermaschine
  • Fig. 4 eine perspektivische Teildarstellung des Führungsex­zenters
It shows:
  • Fig. 1 shows a housing part of the displacement machine
  • 2 shows a runner with a guide eccentric according to the invention
  • Fig. 3 shows a longitudinal section through the displacement machine
  • Fig. 4 is a partial perspective view of the guide eccentric

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.For an explanation of 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.

Der Uebersichtlichkeit wegen ist die Maschine in den Fig. 1 und 2 in demontiertem Zustand gezeigt.For the sake of clarity, the machine is shown in the disassembled state in FIGS. 1 and 2.

Mit 1 ist der Läufer der Maschine insgesamt bezeichnet. An beiden Seiten der Scheibe 2 sind je zwei, um 180° zueinander versetzte, spiralförmig verlaufende Verdrängerkörper angeord­net. Es handelt sich um Leisten 3,3′, die senkrecht auf der Scheibe 2 gehalten sind. Die Spiralen selbst sind im gezeigten Beispiel aus mehreren, aneinander anschliessenden Kreisbögen gebildet. Infolge des eingangs erwähnten grossen Verhältnisses zwischen axialer Länge zur Wandstärke (Fig. 3) ist das ein­trittsseitige Ende der Leisten 3,3′ jeweils verstärkt ausge­führt. Mit 4 ist die Nabe bezeichnet, mit welcher die Scheibe 2 auf einem Wälzlager 22 aufgezogen ist. Das Lager selbst sitzt auf einer Exzenterscheibe 23, die ihrerseits Teil der Antriebswelle 24 ist. Mit 5 ist ein radial ausserhalb der Lei­sten 3,3′ angeordnetes Auge bezeichnet für die Aufnahme eines Führungslagers 25, welches auf einem Exzenterbolzen 26 aufge­zogen ist. Dieser ist seinerseits Teil einer Führungswelle 27. Die Exzentrizität e der Exzenterscheibe auf der Antriebswelle entspricht jener des Exzenterbolzens auf der Führungswelle. Am Spiralenaustritt sind in der Scheibe 2 Durchbrüche 6 vorgese­hen, damit das Medium von einer Scheibenseite zur andern ge­langen kann, beispielsweise um in einem nur einseitig ange­ordneten zentralen Auslass abgezogen zu werden.The rotor of the machine is designated as a whole by 1. Arranged on both sides of the disk 2 are two, displaced by 180 ° to each other, spirally extending displacement body. It is strips 3.3 ', which are held vertically on the disc 2. In the example shown, the spirals themselves are formed from a plurality of circular arcs adjoining one another. As a result of the large ratio mentioned at the beginning between the axial length to the wall thickness (Fig. 3), the entry-side end of the strips 3.3 'is each reinforced. 4 with the hub is designated with which the disc 2 is mounted on a roller bearing 22. The bearing itself sits on an eccentric disk 23, which in turn is part of the drive shaft 24. 5 with a radially outside of the strips 3,3 '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. The eccentricity e of the eccentric disc on the drive shaft corresponds to that of the eccentric bolt on the guide shaft. At the spiral outlet 2 openings 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 in a central outlet arranged only on one side.

In Fig. 1 ist die in Fig. 3 links dargestellte Gehäusehälfte 7 des aus zwei Hälften (7,7′) zusammengesetzten, über Befesti­gungsaugen 8 zur Aufnahme von Verschraubungen miteinander verbundenen Maschinengehäuses gezeigt. 9 symbolisiert die Aufnahme für die Antriebswelle, 10 die Aufnahme für die Führungswelle. 11 und 11′ bezeichnen die zwei 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 12,12′ zu einem im Gehäuseinneren vorgesehenen, beiden Förderräumen gemeinsamen Auslass 13. Sie weisen im wesentlichen parallele, in gleich­bleibendem Abstand zueinander angeordnete Zylinderwände 14, 14′, 15,15′ auf, die im vorliegenden Fall wie die Verdränger­körper der Scheibe 2 eine Spirale von ca. 360° umfassen. Zwi­schen diesen Zylinderwänden greifen die Verdrängerkörper 3,3′ ein, deren Krümmung so bemessen ist, dass die Leisten die inneren und die äusseren Zylinderwände des Gehäuses an mehreren, beispielsweise an jeweils zwei Stellen nahezu berüh­ren.In Fig. 1 the housing half 7 shown in Fig. 3 on the left of two halves (7,7 ') composed, via fastening eyes 8 for receiving screw connections interconnected machine housing is shown. 9 symbolizes the holder for the drive shaft, 10 the holder for the guide shaft. 11 and 11 'denote the two delivery spaces, each offset by 180 °, which are incorporated in the manner of a spiral slot in the two housing halves. They each run from an inlet 12, 12 '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. They have essentially parallel cylinder walls 14, 14', 15, 15 arranged at a constant distance from one another 'On, which in the present case, like the displacement body of the disc 2, comprise a spiral of approximately 360 °. Between these cylinder walls engage the displacer 3,3 ', 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.

An den freien Stirnseiten der Leisten 3,3′ und der Stege 17,18 sind federbelastete Dichtungen 21 in entsprechenden Nuten ein­gelegt. Mit ihnen werden die Arbeitsräume gegen die Seiten­wände 28 des Gehäuses resp. gegen die Verdrängerscheibe ge­dichtet.On the free end faces of the strips 3,3 'and the webs 17, 18, spring-loaded seals 21 are inserted in corresponding grooves. With them, the working spaces against the side walls 28 of the housing, respectively. sealed against the displacement disc.

Aus Fig. 1 ist erkennbar, dass im Bereich des Einlasses 12′ der Steg 17 mit der äusseren Zylinderwand 14 sich im Steg 18′ mit der inneren Zylinderwand 15′ fortsetzt. Diese Massnahme trifft auch im Bereich des Einlasses 12 zu. Der Uebergang er­folgt hier vom Steg 17′ zum Steg 18.From Fig. 1 it can be seen that in the region of the inlet 12 'of the web 17 with the outer cylinder wall 14 continues in the web 18' with the inner cylinder wall 15 '. This measure also applies in the area of the inlet 12. The transition takes place here from web 17 'to web 18.

Den Antrieb und die Führung des Läufers 1 besorgen die zwei beabstandeten Exzenteranordnungen (23,24 resp. 26,27). Um in den Totpunktlagen eine eindeutige Führung des Läufers zu er­zielen, werden die beiden Exzenteranordnungen über einen Zahn­riemenantrieb 16 winkelgenau synchronisiert. Dieser Doppelex­zenterantrieb sorgt dafür, dass alle Punkte der Läuferscheibe und damit auch alle Punkte der beiden Leisten 3 und 3′ eine kreisförmige Verschiebebewegung ausführen.The drive and the guide of the rotor 1 are provided by the two spaced-apart eccentric arrangements (23, 24 and 26, 27, respectively). In order to achieve clear guidance of the rotor in the dead center positions, the two eccentric arrangements are synchronized by a toothed belt drive 16 with precise angles. This double eccentric drive ensures that all points of the rotor disc and thus all points of the two strips 3 and 3 'perform a circular displacement movement.

Infolge der mehrfachen abwechselnden Annäherungen der Leisten 3,3′ an die inneren und äusseren Zylinderwände der zugeordne­ten Förderkammern ergeben sich auf beiden Seiten der Leisten sichelförmige, das Arbeitsmedium einschliessende Arbeitsräume, die während des Antriebes 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.As a result of the multiple alternating approaches of the strips 3, 3 'to the inner and outer cylinder walls of the associated delivery chambers, crescent-shaped work spaces enclosing the working medium result on both sides of the strips, 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 are reduced and the pressure of the working fluid is increased accordingly.

Die Fig. 1 zeigt, dass die Scheibe 2 - abgesehen von dem ra­dial überstehenden Auge 5 - radial mit den Leisten 3,3′ ab­schliesst. Dies bedeutet, dass die Scheibe in radialer Rich­tung im Bereich der Einlässe 12,12′ mindestens eine Gehäuse­hälfte durchdringen muss. Im vorliegenden Fall geschieht dies an der in Fig. 3 links dargestellten Gehäusehälfte 7. Hierzu sind deren innenliegenden Stege 18,18′ gegenüber den aussen­ liegenden Stegen 17,17′ um den Betrag der Scheibendicke abge­senkt. Diese Massnahme weist den Vorteil auf, dass in dieser Gehäusehälfte nur an den inneren Stegen 18,18′ Dichtleisten anzuordnen sind, die bis zum Auslass hin die Förderräume 11, 11′ über die Scheibe 2 gegeneinander abdichten.Fig. 1 shows that the disc 2 - apart from the radially projecting eye 5 - closes radially with the strips 3.3 '. This means that the disk has to penetrate at least one half of the housing in the radial direction in the area of the inlets 12, 12 '. In the present case, this is done on the housing half 7 shown in FIG. 3 on the left lying webs 17, 17 'lowered by the amount of the pane thickness. This measure has the advantage that in this housing half only on the inner webs 18, 18 'sealing strips are to be arranged, which seal the delivery spaces 11, 11' against the disk 2 against each other up to the outlet.

Würde nun der Uebergang vom Steg 17 zum Steg 18′ scharfkantig und radial erfolgen und demzufolge auch die Scheibe 2 an den entsprechenden Eintrittspartien radial abschliessen, so ent­stünde eine Undichtigkeit zwischen den Förderkammern 11 und 11′.If the transition from the web 17 to the web 18 'were now sharp-edged and radial and consequently the disc 2 was also closed radially at the corresponding inlet parts, a leakage would occur between the delivery chambers 11 and 11'.

Wie aus Fig. 1 erkennbar, wird dieser Uebergang nunmehr als kreisrunder Absatz 19,19′ mit dem Radius R1 ausgebildet. Die Gegenfläche an der Scheibe 2 wird mit einer entsprechend kreisbogenförmigen Aussparung 20,20′ versehen, wobei der Radius R2 dieser Aussparung der Exzentrizität e + Radius R1 entspricht. Diese Absätze 19,19′ kooperieren anlässlich des Maschinenbetriebes zwecks Bildung einer Dichtlinie mit den kreisbogenförmigen Aussparungen 20,20′.As can be seen from Fig. 1, this transition is now formed as a circular shoulder 19,19 'with the radius R1. The counter surface on the disc 2 is provided with a corresponding circular arc-shaped recess 20, 20 ', the radius R2 of this recess corresponding to the eccentricity e + radius R1. These paragraphs 19,19 'cooperate on the occasion of the machine operation to form a sealing line with the circular arc-shaped recesses 20.20'.

Im Gegensatz zur eingangs besprochenen Bauart nach DE-A-3 107 231 - bei welcher der Angriffspunkt der Führungs­vorrichtung, d.h. das Führungsauge zur Aufnahme des Exzenters, in der Verdrängerscheibe starr integriert ist - ist im vorlie­genden Fall das Führungsauge 5 mit dem Läufer 1 über eine Rip­pe 29 verbunden.In contrast to the design according to DE-A-3 107 231 discussed at the beginning - in which the point of application of the guide device, i.e. the guide eye for receiving the eccentric, is rigidly integrated in the displacement disk - in the present case, the guide eye 5 is connected to the rotor 1 via a rib 29.

In ihrer Längserstreckung verläuft die Rippe 29 tangential zur Spirale. Sie ist mit dem einlasseitigen Ende der Spiralleiste 3 verbunden. In Fig. 4 ist sie als einstückig mit dem Läufer hergestellte Rippe dargestellt. Ihre Breite entspricht vor­zugsweise der Breite des Führungsauges 5; ihre Dicke ist so gewählt, dass das Führungsauge in radialer Richtung elastisch ist.In its longitudinal extension, the rib 29 extends tangentially to the spiral. It is connected to the inlet end of the spiral strip 3. In Fig. 4 it is shown as a one-piece rib made with the rotor. Its width preferably corresponds to the width of the guide eye 5; its thickness is chosen so that the guide eye is elastic in the radial direction.

In Abweichung zur gezeigten Ausbildung, bei welcher die Rippe 29 aus dem gleichen Material wie der Läufer ist, kann die Rip­pe mit oder ohne Führungsauge auch gesondert gefertigt werden, beispielsweise aus einem Material, welches für die auftreten­den Belastungen besonders geeignet ist. In diesem Fall kann die Rippe auf jede geeignete Art mit dem Läufer verbunden wer­den, wobei insbesondere eine Gelenkanordnung vorgesehen sein kann.In deviation from the embodiment shown, in which the rib 29 is made of the same material as the rotor, the rib can also be manufactured separately with or without a guide eye, for example from a material that is particularly suitable for the loads that occur. In this case, the rib can be connected to the runner in any suitable manner, and in particular a joint arrangement can be provided.

Claims (3)

1. Verdrängermaschine für kompressible Medien mit mindestens vier in einem feststehenden Gehäuse angeordneten Förder­räumen, wobei bei vier Förderräumen jede Gehäusehälfte (7,7′) zwei um ca. 180° gegeneinander versetzte und spi­ralförmig von einem Einlass (12,12′) zu einem Auslass (13) verlaufende Förderräume (11,11′) aufweist und wobei jedem Förderraum ein in diesen eingreifenden Verdränger­körper zugeordnet ist, der als spiralförmige Leiste (3, 3′) senkrecht auf einem gegenüber dem Gehäuse exzentrisch antreibbaren scheibenförmigen Läufer (1) gehalten ist, zu dessen Führung im Gehäuse eine zu einer ersten Antriebs­exzenteranordnung (23,24) mit Abstand angeordnete zweite Führungsexzenteranordnung (26,27) vorgesehen ist, wobei zur nachgiebigen Aufnahme von allfälligen Längendifferen­zen zwischen Förderraum und Verdrängerkörper ein Aus­gleichsmittel am Läufer vorgesehen ist, dadurch gekenn­zeichnet, dass das Führungsauge (5) der Führungsexzenter­anordnung (26,27) mit dem scheibenförmigen Läufer (1) über eine Rippe (29) verbunden ist, die als tangentiale Verlängerung einer der spiralförmigen Leisten (3) an de­ren einlassseitigem Ende ausgebildet ist.1. Displacement machine for compressible media with at least four delivery rooms arranged in a fixed housing, with four delivery rooms each housing half (7,7 ') two offset by approximately 180 ° and spirally from an inlet (12,12') to an outlet (13) has running conveying spaces (11, 11 ') and wherein each conveying space is assigned a displacement body which engages in it and which is held vertically as a spiral bar (3, 3') on a disk-shaped rotor (1) which can be driven eccentrically with respect to the housing, To guide it in the housing, a second guide eccentric arrangement (26, 27) arranged at a distance from a first drive eccentric arrangement (23, 24) is provided, with a compensating means being provided on the rotor for the flexible absorption of any length differences between the conveying space and displacement body, characterized in that the guide eye (5) of the guide eccentric arrangement (26, 27) with the disk-shaped Runner (1) is connected via a rib (29) which is designed as a tangential extension of one of the spiral strips (3) at its inlet end. 2. Verdrängermaschine nach Anspruch 1, dadurch gekennzeich­net, dass die Rippe aus dem gleichen Material besteht wie die damit verbunde Leiste und mit dem Läufer vorzugsweise einstückig hergestellt ist.2. Displacement machine according to claim 1, characterized in that the rib consists of the same material as the associated strip and is preferably made in one piece with the rotor. 3. Verdrängermaschine nach Anspruch 1, dadurch gekennzeich­net, dass die Rippe gelenkig mit dem Läufer verbunden ist.3. Displacement machine according to claim 1, characterized in that the rib is articulated to the rotor.
EP88120414A 1987-12-21 1988-12-07 Fluid displacement apparatus with a spiral element Expired - Lifetime EP0321781B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88120414T ATE72878T1 (en) 1987-12-21 1988-12-07 DISPLACEMENT MACHINE ACCORDING TO THE SPIRAL PRINCIPLE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH4982/87A CH673680A5 (en) 1987-12-21 1987-12-21
CH4982/87 1987-12-21

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EP0321781A1 true EP0321781A1 (en) 1989-06-28
EP0321781B1 EP0321781B1 (en) 1992-02-26

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EP88120414A Expired - Lifetime EP0321781B1 (en) 1987-12-21 1988-12-07 Fluid displacement apparatus with a spiral element

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US (1) US4950138A (en)
EP (1) EP0321781B1 (en)
JP (1) JP2758178B2 (en)
AT (1) ATE72878T1 (en)
CH (1) CH673680A5 (en)
DE (1) DE3868609D1 (en)
ES (1) ES2028978T3 (en)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0463370A2 (en) * 1990-05-30 1992-01-02 Volkswagen Aktiengesellschaft Eccentric drive for a rotating mass
EP0545190A1 (en) * 1991-12-05 1993-06-09 AGINFOR AG für industrielle Forschung Scroll-type fluid displacement machine
EP0545188A1 (en) * 1991-12-05 1993-06-09 AGINFOR AG für industrielle Forschung Scroll type fluid displacement machine
EP0547491A1 (en) * 1991-12-16 1993-06-23 Asea Brown Boveri Ag Fluid displacement apparatus with a spiral element
EP0560009A1 (en) * 1992-03-13 1993-09-15 Asea Brown Boveri Ag Positive displacement machine on the spiral principle
EP0899423A1 (en) * 1997-08-26 1999-03-03 SIG Schweizerische Industrie-Gesellschaft Scroll compressible fluid displacement machine

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ES2164398T3 (en) * 1997-08-26 2002-02-16 Crt Common Rail Tech Ag SPIRAL DISPLACEMENT MACHINES FOR COMPRESSIBLE MEDIA.
US6364643B1 (en) * 2000-11-10 2002-04-02 Scroll Technologies Scroll compressor with dual suction passages which merge into suction path
JP2006097531A (en) * 2004-09-29 2006-04-13 Anest Iwata Corp Turning scroll in scroll fluid machine
JP4969878B2 (en) * 2006-03-13 2012-07-04 アネスト岩田株式会社 Scroll fluid machinery
DE102007043674B4 (en) * 2007-09-13 2009-11-12 Handtmann Systemtechnik Gmbh & Co. Kg Spiral compressor with double spiral
EP2402611A3 (en) * 2010-07-02 2013-06-26 Handtmann Systemtechnik GmbH & Co. KG Loading device for compacting charge air for a combustion engine

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Cited By (9)

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Publication number Priority date Publication date Assignee Title
EP0463370A2 (en) * 1990-05-30 1992-01-02 Volkswagen Aktiengesellschaft Eccentric drive for a rotating mass
EP0463370A3 (en) * 1990-05-30 1993-08-18 Volkswagen Ag Eccentric drive for a rotating mass
EP0545190A1 (en) * 1991-12-05 1993-06-09 AGINFOR AG für industrielle Forschung Scroll-type fluid displacement machine
EP0545188A1 (en) * 1991-12-05 1993-06-09 AGINFOR AG für industrielle Forschung Scroll type fluid displacement machine
US5322426A (en) * 1991-12-05 1994-06-21 Aginfor Ag Fur Industrielle Forschung Displacement machine spiral shaped strip with different curvatures
EP0547491A1 (en) * 1991-12-16 1993-06-23 Asea Brown Boveri Ag Fluid displacement apparatus with a spiral element
EP0560009A1 (en) * 1992-03-13 1993-09-15 Asea Brown Boveri Ag Positive displacement machine on the spiral principle
DE4207984A1 (en) * 1992-03-13 1993-09-16 Asea Brown Boveri DISPLACEMENT MACHINE ACCORDING TO THE SPIRAL PRINCIPLE
EP0899423A1 (en) * 1997-08-26 1999-03-03 SIG Schweizerische Industrie-Gesellschaft Scroll compressible fluid displacement machine

Also Published As

Publication number Publication date
EP0321781B1 (en) 1992-02-26
JPH01206101A (en) 1989-08-18
DE3868609D1 (en) 1992-04-02
US4950138A (en) 1990-08-21
CH673680A5 (en) 1990-03-30
ATE72878T1 (en) 1992-03-15
JP2758178B2 (en) 1998-05-28
ES2028978T3 (en) 1992-07-16

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