EP2179138B1 - Displacement machine according to the spiral principle - Google Patents

Displacement machine according to the spiral principle Download PDF

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Publication number
EP2179138B1
EP2179138B1 EP08757302.8A EP08757302A EP2179138B1 EP 2179138 B1 EP2179138 B1 EP 2179138B1 EP 08757302 A EP08757302 A EP 08757302A EP 2179138 B1 EP2179138 B1 EP 2179138B1
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EP
European Patent Office
Prior art keywords
bearing
drive shaft
housing
displacement machine
machine according
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.)
Not-in-force
Application number
EP08757302.8A
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German (de)
French (fr)
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EP2179138A2 (en
Inventor
Fritz Spinnler
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Spinnler Engineering
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Spinnler Engineering
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Publication date
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Publication of EP2179138A2 publication Critical patent/EP2179138A2/en
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Publication of EP2179138B1 publication Critical patent/EP2179138B1/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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/02—Arrangements of bearings
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C18/0223—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C27/009—Shaft sealings specially adapted for pumps
    • 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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • 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
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/52—Bearings for assemblies with supports on both sides
    • 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F04C2240/601—Shaft flexion

Definitions

  • the present invention relates to a displacement machine for compressible media according to the preamble of claim 1.
  • Displacement machines of this type are for example from the DE-A-33 13 000 , of the EP 0 557 598 A or the EP 0 371 305 A of which the latter can be considered as the closest prior art, and have a housing consisting of two halves, in which a displacement body is arranged.
  • the displacer is mounted by means of a bearing on an eccentric disc, which is connected to a drivable drive shaft.
  • the drive shaft is mounted in the housing by means of two bearings, which are opposite to each other with respect to the eccentric disk. Between each bearing and the eccentric disc each one connected to the drive shaft counterweight is arranged.
  • the drive shaft extending through the housing wall on its drive side carries a drive disk on its drive-side end which is connected to a drive.
  • a compressor operating on this principle is characterized by a low-pulsation delivery of the gaseous working medium, e.g. Air, from and could therefore be used with advantage, inter alia, for charging purposes in internal combustion engines.
  • the gaseous working medium e.g. Air
  • the present invention is based on the object to provide a positive displacement machine of the type mentioned, in which the lying outside the housing drive pulley relatively far from the housing can be arranged and the drive shaft in operation does not deflect too much, not even at high speeds.
  • the in the Fig. 1 and 2 in front view or in section shown displacement machine has a two housing halves 1a, 1b existing housing 1, in which a displacement body 2 is mounted.
  • the two housing halves 1 a, 1 b are screwed together in a manner not shown.
  • In the presentation of the Fig. 1 is the one housing half 1a ( Fig. 2 ) away.
  • the displacement body 2 has a carrier disk 3 which carries on each side a spiraling displacement element 4, 5.
  • the displacement elements 4, 5 are designed as protruding from the disc 3 strips in the form of spiral leaves.
  • a drive shaft 6 is provided, whose axis of rotation is denoted by 6a.
  • the drive shaft 6 is mounted in the housing halves 1 a, 1 b by means of a first bearing 7 and a second bearing 8 and has an eccentric disc 9, whose axis of symmetry is designated 9 a.
  • the distance between the axis of rotation 6a of the drive shaft 6 and the axis of symmetry 9a of the eccentric disc 9 (eccentricity) is in the Fig. 1 denoted by e.
  • the hub 11 of the disc 3 is supported by means of a hub bearing 10, which is a rolling bearing in the present case.
  • the disk 3 and thus the displacer 2 are driven via the drive shaft 6 and the eccentric disk 9.
  • the driving force is transmitted via the hub bearing 10 to the hub 11 of the disk 3.
  • the guide of the displacement body 2 via a rocker 12 which is rotatably mounted on a shaft 13 at one end ( Fig. 1 ).
  • the rocker 12 carries a bolt 14 which is rotatably mounted in an eye 15 of the disc 3.
  • the housing 1 has an inlet 16 and an outlet 17 for the conveying medium, preferably air, as well as two delivery chambers 18, 18 '.
  • a passage 19 (or more passages) is present, through which the fluid can pass from the pumping chamber 18 into the delivery chamber 18 '.
  • two counterweights 20, 21 are arranged, which are as close as possible to the eccentric 9 zoom zoomed so that during operation a deflection of the drive shaft 6 is kept as small as possible or even prevented.
  • the distance between the bearings 7 and 8 and the respective adjacent counterweight 20 and 21 and thus also the distance between the bearings 7, 8 and the eccentric disc 9 is also kept as small as possible, which further contributes to a deflection of the drive shaft. 6 to keep small in operation or prevent.
  • This small bearing distance is achieved in that the bearing receptacles 48 a and 48 b, with which the two housing halves 1 a and 1 b are provided, completely in the housing interior in the pumping chambers 18 'BEZW. 18 protrude and that the centers of the two bearings 7, 8 lie in a vertical plane within the respective delivery chamber 18 ', 18. This in contrast to those known solutions in which the bearing mounts and the bearings are either in the plane of the housing walls or even outside of it.
  • the drive shaft 6 extends with respect to the eccentric disc 9 on the side of the second bearing 8 through the wall of the housing part 1b and carries at its protruding from the housing 1 end a drive pulley 23.
  • the arranged on the outside of the housing 1 drive pulley 23 is not on shown in more detail, eg by means of a drive belt, connected to a drive, not shown.
  • the drive shaft 6 is supported on its drive-side, the drive disk 23 bearing end by means of a third bearing 24, which is preferably a roller bearing, in particular a ball bearing.
  • the third bearing 24 is seated in the region of the drive pulley 23 on the drive shaft 6, preferably approximately in the center plane of the drive pulley 23 in order to minimize the influence of the clamping force of a driven over the drive pulley 23 drive belt (not shown) to the deflection of the drive shaft 6 or to eliminate.
  • the third bearing 24 is held in a projecting in the direction of the axis 6a of the drive shaft 6 from the housing 1 support member 25 which is in one piece in the embodiment shown with the housing part 1b.
  • the support member 25 may also be formed as a separate from the housing 1 component which is fixed to the housing 1.
  • the third bearing 24 is formed in the embodiment shown as a thrust bearing, which serves for the axial alignment of the drive shaft 6 in the housing 1.
  • the outer ring of the third bearing 24 is supported in the axial direction in the support member 25 and secured by a securing ring 26.
  • the inner ring 24b of the third bearing 24 is located between a pushed onto the drive shaft 6 spacer sleeve which bears against a shoulder formed on the drive shaft 6, and the hub 23a of the drive pulley 23.
  • the spacer sleeve, the inner ring 24b of the third bearing 24 and the hub 23a the drive plate 23 are braced against the shoulder by means of a screwed onto a thread 29 at the end of the drive shaft 6 nut 30.
  • the third bearing 24 is as in Fig. 2 shown grease-lubricated.
  • constructive means ensure that the same pressure, namely the ambient pressure, prevails on both sides of the third bearing 24.
  • a passage is formed in the support member 25, which connects the space on the side of the third bearing 24, which faces the spacer sleeve, with the environment.
  • the pressure prevailing in this environment pressure acts both on the first side facing the spacer sleeve as well as on the second side of the third bearing 24 opposite this first side in the axial direction.
  • the additional support of the drive shaft 6 at its drive-side end makes it possible to freely choose the distance between the second bearing 8 and the attachment point of the drive pulley 23 on the drive shaft 6 on the one hand or the magnetic coupling on the other hand without the risk of deflection of the drive shaft 6 in purchasing to have to.
  • a labyrinth seal is arranged in the region of the passage of the drive shaft 6 through the wall of the housing 1.
  • This consists of two in the longitudinal direction of the drive shaft 6 successively arranged throttle points.
  • Each throttle point has a stationary sealing member, which engages in a groove in the co-rotating with the drive shaft 6 spacer sleeve.
  • the sealing members are preferably formed by piston rings and are held under prestress in the support member 25.
  • a connecting line In the space between the throttle points opens a connecting line, which opens into the inlet 16 at the other end. This connecting line thus connects the inlet 16 with the space between the throttling points.
  • the second bearing 8 for the drive shaft 6 is also grease lubricated, taking care that the second bearing 8 does not dry out during operation. For this purpose, appropriate structural measures are taken so that on both sides of the second bearing 8, the same pressure prevails.
  • the counterweight 21 facing first side of the second bearing 8 is acted upon by the pressure in the delivery chamber 18.
  • a connecting line 38 is provided which connects the delivery chamber 18 with this other, second side of the second bearing 8.
  • Both the first bearing 7 for the drive shaft 6 and the hub bearing 10 for the eccentric disc 9 are lubricated in a manner not shown with a liquid lubricant, preferably lubricating oil.
  • the bearings 7 and 10 are sealed by means of annular sealing elements 39 with respect to the delivery chambers 18, 18 '.
  • each counterweight 20, 21 is formed by a fixing member 46 non-rotatably connected to the drive shaft 6 and a mass member 47 integral with the fixing member 46.
  • the fastening part 46 of each counterweight 20, 21 has as small a dimension as possible in the axial direction, which makes it possible to bring the first and second bearings 7 and 8 as close as possible to the eccentric disk 9. With this measure, the deflection of the drive shaft 6 during operation can be virtually prevented.
  • the inner radius R of the mass part 47 ( Fig. 3 ) is sized to be larger than the one in Fig. 2 D designated radial dimension of the hub 11 of the disc 3 and also larger than the outer diameter of the bearing mounts 48a, 48b. This makes it possible to arrange the mass portion 47 in the radial direction outside the hub 11, like that Fig. 2 is apparent.
  • the dimension of the mass portion 47 of each counterweight 20, 21 can therefore be selected in the axial direction greater than the axial dimension of the fastening part 46. This makes it possible to arrange the fastening part 46 very close to the eccentric disc 9 and the hub 11 and still have a certain freedom in the design of the mass member 47.
  • the size of the balance caused by the counterweights 20, 21 can be determined by a suitable dimensioning of the mass parts 47.
  • the counterweights have a T-shaped cross section, wherein the crossbars represent the actual mass parts 47 and are configured so that they cover both the hub 11 and the bearing receivers 48 a, 48 b on both sides, at least partially.
  • the displacement machines shown in the figures and described above are particularly suitable as superchargers for internal combustion engines.

Description

Die vorliegende Erfindung betrifft eine Verdrängermaschine für kompressible Medien gemäss Oberbegriff des Patentanspruches 1.The present invention relates to a displacement machine for compressible media according to the preamble of claim 1.

Verdrängermaschinen dieser Art sind beispielsweise aus der DE-A-33 13 000 , der EP 0 557 598 A oder der EP 0 371 305 A bekannt, von denen letztere als nächstliegender Stand der Technik betrachtet werden kann, und weisen ein aus zwei Hälften bestehendes Gehäuse auf, in dem ein Verdrängerkörper angeordnet ist. Der Verdrängerkörper ist mittels einer Lagerung auf einer Exzenterscheibe gelagert, die mit einer antreibbaren Antriebswelle verbunden ist. Die Antriebswelle ist mittels zweier Lager, die sich bezüglich der Exzenterscheibe gegenüberliegen, im Gehäuse gelagert. Zwischen jedem Lager und der Exzenterscheibe ist je ein mit der Antriebswelle verbundenes Gegengewicht angeordnet. Die sich auf ihrer Antriebsseite durch die Gehäusewand hindurch erstreckende Antriebswelle trägt an ihrem antriebsseitigen Ende eine Antriebsscheibe, die mit einem Antrieb in Verbindung steht.Displacement machines of this type are for example from the DE-A-33 13 000 , of the EP 0 557 598 A or the EP 0 371 305 A of which the latter can be considered as the closest prior art, and have a housing consisting of two halves, in which a displacement body is arranged. The displacer is mounted by means of a bearing on an eccentric disc, which is connected to a drivable drive shaft. The drive shaft is mounted in the housing by means of two bearings, which are opposite to each other with respect to the eccentric disk. Between each bearing and the eccentric disc each one connected to the drive shaft counterweight is arranged. The drive shaft extending through the housing wall on its drive side carries a drive disk on its drive-side end which is connected to a drive.

Während des Betriebs einer solchen Verdrängermaschine werden in der Verdränger- oder Förderkammer zwischen dem spiralförmig ausgebildeten Verdrängerkörper und den beiden Umfangswänden mehrere, etwa sichelförmige Arbeitsräume eingeschlossen, die sich vom Einlass durch die Förderkammer hindurch zum Auslass hin bewegen, wobei ihr Volumen ständig verringert und der Druck des Arbeitsmittels dementsprechend erhöht wird. Ein nach diesem Prinzip arbeitender Verdichter zeichnet sich durch eine pulsationsarme Förderung des gasförmigen Arbeitsmittels, z.B. Luft, aus und könnte daher mit Vorteil unter anderem für Aufladezwecke bei Brennkraftmaschinen herangezogen werden.During operation of such a displacement machine, a plurality of generally crescent-shaped working spaces are trapped in the displacer chamber between the spirally-formed displacer and the two peripheral walls, moving from the inlet through the delivery chamber to the outlet, constantly reducing its volume and pressure of the working fluid is increased accordingly. A compressor operating on this principle is characterized by a low-pulsation delivery of the gaseous working medium, e.g. Air, from and could therefore be used with advantage, inter alia, for charging purposes in internal combustion engines.

Um zu verhindern, dass sich die Antriebswelle im Betrieb durchbiegt, insbesondere bei hohen Drehzahlen, sind bei den vorstehend erwähnten bekannten Verdrängermaschinen die Gegengewichte sehr nahe an der Exzenterscheibe angeordnet. Hinsichtlich der Anordnung der Lager gilt, dass der Abstand zwischen demjenigen Lager, das bezüglich der Exzenterscheibe auf der Seite der Antriebsscheibe liegt, und dieser Antriebsscheibe nicht zu gross werden darf, da sonst die Gefahr einer Durchbiegung der Antriebswelle im Betrieb besteht.In order to prevent that the drive shaft bends in operation, especially at high speeds, are in the above-mentioned known displacement machines arranged the counterweights very close to the eccentric disc. With regard to the arrangement of the bearing is that the distance between that bearing, which is with respect to the eccentric disc on the side of the drive pulley, and this drive pulley must not be too large, otherwise there is a risk of deflection of the drive shaft during operation.

Der vorliegenden Erfindung liegt nun die Aufgabe zugrunde, eine Verdrängermaschine der eingangs genannten Art zu schaffen, bei der die ausserhalb des Gehäuses liegende Antriebsscheibe verhältnismassig weit vom Gehäuse angeordnet werden kann und sich die Antriebswelle im Betrieb nicht zu stark durchbiegt, auch bei hohen Drehzahlen nicht.The present invention is based on the object to provide a positive displacement machine of the type mentioned, in which the lying outside the housing drive pulley relatively far from the housing can be arranged and the drive shaft in operation does not deflect too much, not even at high speeds.

Diese Aufgabe wird mit den kennzeichnenden Merkmalen des Anspruches 1 gelöst.This object is achieved with the characterizing features of claim 1.

Zwar ist es aus der Fig. 6 der DE 32 31 756 A1 ein Spirallader bekannt mit einer vollständig ins Laderinnere gerichteten Lageraufnahme. Jedoch handelt es sich bei dieser Ausführung um einen einseitig gelagerten Exzenter, auf dessen freien Seite sich die Fliehgewichte befinden. Die Lagerung der Haupt- Exzenterwelle findet zwar in zwei Lagerstellen statt, im Gegensatz zur vorliegenden Ausführung jedoch in nur einer Gehäusehälfte. Eine solche Ausführung ist für die sichere Beherrschung der heute verlangten höheren Förderdrücke nicht geeignet.Although it is from FIG. 6 of the DE 32 31 756 A1 a spiral loader known with a fully directed into the loader storage mount. However, this version is a cantilevered eccentric, on its free side, the centrifugal weights are. Although the bearing of the main eccentric shaft takes place in two bearings, in contrast to the present embodiment, however, in only one housing half. Such a design is not suitable for the safe control of today required higher discharge pressures.

Der geringe Abstand zwischen erstem und zweiten Lager, welcher dadurch erreicht wird, dass die Mittelpunkte der beiden Lager in einer Vertikalebene innerhalb des jeweiligen Förderraums liegen. sowie die Abstützung der Antriebswelle an ihrem aus dem Gehäuse herausragenden, antriebsseitigen Ende mittels eines weiteren Lagers ermöglicht es, den Abstand zwischen dem Antrieb und demjenigen Lager im Innern des Gehäuses, das bezüglich der Exzenterscheibe auf der Seite des Antriebs liegt, freier zu wählen.The small distance between the first and second bearing, which is achieved in that the centers of the two bearings lie in a vertical plane within the respective pumping chamber. as well as the support of the drive shaft at its projecting from the housing, drive end by means of another bearing makes it possible to choose the distance between the drive and that bearing inside the housing, which is relative to the eccentric disc on the side of the drive, more free.

Bevorzugte Weiterausgestaltungen der erfindungsgemässen Verdrängermaschine bilden Gegenstand der abhängigen Patentansprüche.Preferred further developments of the inventive displacement machine form the subject of the dependent claims.

Im Folgenden wird anhand der Zeichnung ein Ausführungsbeispiel des Erfindungsgegenstandes näher erläutert. Es zeigt rein schematisch:

Fig. 1
in Vorderansicht den antriebsseitigen Gehäuseteil einer Verdrängermaschine,
Fig. 2
die Verdrängermaschine gemäss Fig. 1 in einem Längsschnitt entlang der Linie II-II in Fig. 1,
Fig. 3
einen Schnitt entlang der Linie V-V in Fig. 2.
In the following an embodiment of the subject invention is explained in detail with reference to the drawing. It shows purely schematically:
Fig. 1
in front view of the drive-side housing part of a positive displacement machine,
Fig. 2
the displacement machine according to Fig. 1 in a longitudinal section along the line II-II in Fig. 1 .
Fig. 3
a section along the line VV in Fig. 2 ,

Die in den Fig. 1 und 2 in Vorderansicht bzw. im Schnitt gezeigte Verdrängermaschine weist ein aus zwei Gehäusehälften 1a, 1b bestehendes Gehäuse 1 auf, in dem ein Verdrängerkörper 2 gelagert ist. Die beiden Gehäusehälften 1 a, 1 b sind auf nicht näher dargestellte Weise miteinander verschraubt. In der Darstellung der Fig. 1 ist die eine Gehäusehälfte 1a (Fig. 2) entfernt.The in the Fig. 1 and 2 in front view or in section shown displacement machine has a two housing halves 1a, 1b existing housing 1, in which a displacement body 2 is mounted. The two housing halves 1 a, 1 b are screwed together in a manner not shown. In the presentation of the Fig. 1 is the one housing half 1a ( Fig. 2 ) away.

Der Verdrängerkörper 2 weist eine Trägerscheibe 3 auf, die auf jeder Seite ein spiralförmig verlaufendes Verdrängerelement 4, 5 trägt. Die Verdrängerelemente 4, 5 sind als von der Scheibe 3 abstehende Leisten in Form von Spiralblättern ausgebildet. Zur Lagerung der Scheibe 3 ist eine Antriebswelle 6 vorgesehen, deren Drehachse mit 6a bezeichnet ist. Die Antriebswelle 6 ist in den Gehäusehälften 1 a, 1 b mittels eines ersten Lagers 7 und eines zweiten Lagers 8 gelagert und weist eine Exzenterscheibe 9 auf, deren Symmetrieachse mit 9a bezeichnet ist. Der Abstand zwischen der Drehachse 6a der Antriebswelle 6 und der Symmetrieachse 9a der Exzenterscheibe 9 (Exzentrizität) ist in der Fig. 1 mit e bezeichnet.The displacement body 2 has a carrier disk 3 which carries on each side a spiraling displacement element 4, 5. The displacement elements 4, 5 are designed as protruding from the disc 3 strips in the form of spiral leaves. For the storage of the disc 3, a drive shaft 6 is provided, whose axis of rotation is denoted by 6a. The drive shaft 6 is mounted in the housing halves 1 a, 1 b by means of a first bearing 7 and a second bearing 8 and has an eccentric disc 9, whose axis of symmetry is designated 9 a. The distance between the axis of rotation 6a of the drive shaft 6 and the axis of symmetry 9a of the eccentric disc 9 (eccentricity) is in the Fig. 1 denoted by e.

Auf der Exzenterscheibe 9 ist mittels eines Nabenlagers 10, das im vorliegenden Fall ein Wälzlager ist, die Nabe 11 der Scheibe 3 gelagert. Angetrieben wird die Scheibe 3 und somit der Verdrängerkörper 2 über die Antriebswelle 6 und die Exzenterscheibe 9. Dabei wird die Antriebskraft über das Nabenlager 10 auf die Nabe 11 der Scheibe 3 übertragen. Die Führung des Verdrängerkörpers 2 erfolgt über eine Schwinge 12, die am einen Ende drehbar auf einer Welle 13 gelagert ist (Fig. 1). Am andern Ende trägt die Schwinge 12 einen Bolzen 14, der drehbar in einem Auge 15 der Scheibe 3 gelagert ist.On the eccentric disc 9, the hub 11 of the disc 3 is supported by means of a hub bearing 10, which is a rolling bearing in the present case. The disk 3 and thus the displacer 2 are driven via the drive shaft 6 and the eccentric disk 9. The driving force is transmitted via the hub bearing 10 to the hub 11 of the disk 3. The guide of the displacement body 2 via a rocker 12 which is rotatably mounted on a shaft 13 at one end ( Fig. 1 ). At the other end, the rocker 12 carries a bolt 14 which is rotatably mounted in an eye 15 of the disc 3.

Das Gehäuse 1 weist einen Einlass 16 und einen Auslass 17 für das Fördermedium, vorzugsweise Luft, sowie zwei Förderräume 18, 18' auf. In der Scheibe 3 ist ein Durchlass 19 (oder mehrere Durchlässe) vorhanden, durch den das Fördermedium vom Förderraum 18 in den Förderraum 18' gelangen kann.The housing 1 has an inlet 16 and an outlet 17 for the conveying medium, preferably air, as well as two delivery chambers 18, 18 '. In the disc 3, a passage 19 (or more passages) is present, through which the fluid can pass from the pumping chamber 18 into the delivery chamber 18 '.

Zum Ausgleich der beim exzentrischen Antrieb des Verdrängerkörpers 2 entstehenden Massenkräfte sind auf der Antriebswelle 6 zwei Gegengewichte 20, 21 angeordnet, die so nahe als möglich an die Exzenterscheibe 9 heran gerückt sind, damit im Betrieb eine Durchbiegung der Antriebswelle 6 so klein wie möglich gehalten oder gar verhindert wird. Der Abstand zwischen den Lagern 7 und 8 und dem jeweils benachbarten Gegengewicht 20 bzw. 21 und damit auch der Abstand zwischen den Lagern 7, 8 und der Exzenterscheibe 9 ist ebenfalls so klein als möglich gehalten, was weiter dazu beiträgt, eine Durchbiegung der Antriebswelle 6 im Betrieb klein zu halten bzw. zu verhindern.To compensate for the resulting in the eccentric drive of the displacer 2 mass forces on the drive shaft 6, two counterweights 20, 21 are arranged, which are as close as possible to the eccentric 9 zoom zoomed so that during operation a deflection of the drive shaft 6 is kept as small as possible or even prevented. The distance between the bearings 7 and 8 and the respective adjacent counterweight 20 and 21 and thus also the distance between the bearings 7, 8 and the eccentric disc 9 is also kept as small as possible, which further contributes to a deflection of the drive shaft. 6 to keep small in operation or prevent.

Dieser geringe Lagerabstand wird dadurch erreicht, dass die Lageraufnahmen 48a und 48b, mit denen die beiden Gehäusehälften 1 a und 1 b versehen sind, vollständig in das Gehäuseinnere in die Förderräume 18' bezw. 18 hineinkragen und dass die Mittelpunkte der beiden Lager 7, 8 in einer Vertikalebene innerhalb des jeweiligen Förderraums 18', 18 liegen. Dies im Gegensatz zu denen bekannten Lösungen, bei denen sich die Lageraufnahmen und die Lager jeweils entweder in der Ebene der Gehäusewände oder sogar ausserhalb davon befinden.This small bearing distance is achieved in that the bearing receptacles 48 a and 48 b, with which the two housing halves 1 a and 1 b are provided, completely in the housing interior in the pumping chambers 18 'BEZW. 18 protrude and that the centers of the two bearings 7, 8 lie in a vertical plane within the respective delivery chamber 18 ', 18. This in contrast to those known solutions in which the bearing mounts and the bearings are either in the plane of the housing walls or even outside of it.

Die Antriebswelle 6 erstreckt sich bezüglich der Exzenterscheibe 9 auf der Seite des zweiten Lagers 8 durch die Wand des Gehäuseteils 1b hindurch und trägt an ihrem aus dem Gehäuse 1 herausragenden Ende eine Antriebsscheibe 23. Die auf der Aussenseite des Gehäuses 1 angeordnete Antriebsscheibe 23 ist auf nicht näher dargestellte Weise, z.B. mittels eines Antriebsriemens, mit einem nicht gezeigten Antrieb verbunden.The drive shaft 6 extends with respect to the eccentric disc 9 on the side of the second bearing 8 through the wall of the housing part 1b and carries at its protruding from the housing 1 end a drive pulley 23. The arranged on the outside of the housing 1 drive pulley 23 is not on shown in more detail, eg by means of a drive belt, connected to a drive, not shown.

Beim gezeigten Beispiel ist die Antriebswelle 6 an ihrem antriebsseitigen, die Antriebsscheibe 23 tragenden Ende mittels eines dritten Lagers 24 abgestützt, das vorzugsweise ein Wälzlager, insbesondere ein Kugellager ist. Das dritte Lager 24 sitzt im Bereich der Antriebsscheibe 23 auf der Antriebswelle 6, vorzugsweise etwa in der Mittelebene der Antriebsscheibe 23, um den Einfluss der Spannkraft eines über die Antriebsscheibe 23 geführten Antriebsriemens (nicht gezeigt) auf die Durchbiegung der Antriebswelle 6 zu minimieren bzw. zu eliminieren. Das dritte Lager 24 ist in einem in Richtung der Achse 6a der Antriebswelle 6 vom Gehäuse 1 abstehenden Stützteil 25 gehalten, der beim gezeigten Ausführungsbeispiel mit dem Gehäuseteil 1b einstückig ist. Der Stützteil 25 kann aber auch als ein vom Gehäuse 1 getrennter Bauteil ausgebildet sein, der am Gehäuse 1 befestigt ist.In the example shown, the drive shaft 6 is supported on its drive-side, the drive disk 23 bearing end by means of a third bearing 24, which is preferably a roller bearing, in particular a ball bearing. The third bearing 24 is seated in the region of the drive pulley 23 on the drive shaft 6, preferably approximately in the center plane of the drive pulley 23 in order to minimize the influence of the clamping force of a driven over the drive pulley 23 drive belt (not shown) to the deflection of the drive shaft 6 or to eliminate. The third bearing 24 is held in a projecting in the direction of the axis 6a of the drive shaft 6 from the housing 1 support member 25 which is in one piece in the embodiment shown with the housing part 1b. However, the support member 25 may also be formed as a separate from the housing 1 component which is fixed to the housing 1.

Das dritte Lager 24 ist beim gezeigten Ausführungsbeispiel als Axiallager ausgebildet, das zur axialen Ausrichtung der Antriebswelle 6 im Gehäuse 1 dient. Der Aussenring des dritten Lagers 24 ist in axialer Richtung im Stützteil 25 abgestützt und mittels eines Sicherungsringes 26 gesichert. Der Innenring 24b des dritten Lagers 24 liegt zwischen einer auf die Antriebswelle 6 aufgeschobenen Distanzhülse, die an einer an der Antriebswelle 6 ausgebildeten Schulter anliegt, und der Nabe 23a der Antriebsscheibe 23. Die Distanzhülse, der Innenring 24b des dritten Lagers 24 und die Nabe 23a der Antriebscheibe 23 sind mittels einer auf ein Gewinde 29 am Ende der Antriebswelle 6 aufgeschraubten Schraubenmutter 30 gegen die Schulter verspannt.The third bearing 24 is formed in the embodiment shown as a thrust bearing, which serves for the axial alignment of the drive shaft 6 in the housing 1. The outer ring of the third bearing 24 is supported in the axial direction in the support member 25 and secured by a securing ring 26. The inner ring 24b of the third bearing 24 is located between a pushed onto the drive shaft 6 spacer sleeve which bears against a shoulder formed on the drive shaft 6, and the hub 23a of the drive pulley 23. The spacer sleeve, the inner ring 24b of the third bearing 24 and the hub 23a the drive plate 23 are braced against the shoulder by means of a screwed onto a thread 29 at the end of the drive shaft 6 nut 30.

Das dritte Lager 24 ist wie in Fig. 2 gezeigt fettgeschmiert. Um zu verhindern, dass das dritte Lager 24 während des Betriebs austrocknet, ist mit konstruktiven Mitteln dafür gesorgt, dass auf beiden Seiten des dritten Lagers 24 derselbe Druck, nämlich der Umgebungsdruck, herrscht. Zu diesem Zweck ist im Stützteil 25 ein Durchlass ausgebildet, der den Raum auf derjenigen Seite des dritten Lagers 24, die der Distanzhülse zugekehrt ist, mit der Umgebung verbindet. Somit wirkt der in dieser Umgebung herrschende Druck sowohl auf die der Distanzhülse zugekehrte erste Seite wie auch auf die dieser ersten Seite in axialer Richtung gegenüberliegende zweite Seite des dritten Lagers 24.The third bearing 24 is as in Fig. 2 shown grease-lubricated. In order to prevent the third bearing 24 from drying out during operation, constructive means ensure that the same pressure, namely the ambient pressure, prevails on both sides of the third bearing 24. For this purpose, a passage is formed in the support member 25, which connects the space on the side of the third bearing 24, which faces the spacer sleeve, with the environment. Thus, the pressure prevailing in this environment pressure acts both on the first side facing the spacer sleeve as well as on the second side of the third bearing 24 opposite this first side in the axial direction.

Die zusätzliche Abstützung der Antriebswelle 6 an ihrem antriebsseitigen Ende ermöglicht es, den Abstand zwischen dem zweiten Lager 8 und der Befestigungsstelle der Antriebsscheibe 23 auf der Antriebswelle 6 einerseits oder der Magnetkupplung andererseits freier zu wählen, ohne die Gefahr einer Durchbiegung der Antriebswelle 6 in Kauf nehmen zu müssen.The additional support of the drive shaft 6 at its drive-side end makes it possible to freely choose the distance between the second bearing 8 and the attachment point of the drive pulley 23 on the drive shaft 6 on the one hand or the magnetic coupling on the other hand without the risk of deflection of the drive shaft 6 in purchasing to have to.

Damit verhindert werden kann, dass während des Betriebs Fördermedium aus dem Förderraum 18, 18' nach aussen in die Umgebung austreten kann, ist im Bereich des Durchtrittes der Antriebswelle 6 durch die Wand des Gehäuses 1 eine Labyrinthdichtung angeordnet. Diese besteht aus zwei in Längsrichtung der Antriebswelle 6 hintereinander angeordneten Drosselstellen. Jede Drosselstelle weist ein ortsfestes Dichtungsorgan auf, das in eine Nut in der mit der Antriebswelle 6 mitdrehenden Distanzhülse heingreift. Die Dichtungsorgane sind vorzugsweise durch Kolbenringe gebildet und sind unter Vorspannung im Stützteil 25 gehalten. In den Raum zwischen den Drosselstellen mündet eine Verbindungsleitung, die am andern Ende in den Einlass 16 mündet. Diese Verbindungsleitung verbindet demnach den Einlass 16 mit dem Raum zwischen den Drosselstellen. Das bedeutet, dass im Betrieb zwischen den Drosselstellen ein Druck herrscht, der etwa dem Druck im Einlass 16 entspricht, der niedriger ist als der Umgebungsdruck. Durch die erste Drosselstelle austretendes Fördermedium wird über die Verbindungsleitung in den Einlass 16 zurück geführt und kann nicht in Längsrichtung der Antriebswelle 6 nach aussen austreten.In order to prevent pumped medium from escaping out of the delivery chamber 18, 18 'into the environment during operation, a labyrinth seal is arranged in the region of the passage of the drive shaft 6 through the wall of the housing 1. This consists of two in the longitudinal direction of the drive shaft 6 successively arranged throttle points. Each throttle point has a stationary sealing member, which engages in a groove in the co-rotating with the drive shaft 6 spacer sleeve. The sealing members are preferably formed by piston rings and are held under prestress in the support member 25. In the space between the throttle points opens a connecting line, which opens into the inlet 16 at the other end. This connecting line thus connects the inlet 16 with the space between the throttling points. This means that in operation between the throttle points there is a pressure which corresponds approximately to the pressure in the inlet 16, which is lower than the ambient pressure. By the first throttling point escaping conveying medium is guided back via the connecting line in the inlet 16 and can not escape in the longitudinal direction of the drive shaft 6 to the outside.

Das zweite Lager 8 für die Antriebswelle 6 ist ebenfalls fettgeschmiert, wobei dafür gesorgt ist, dass das zweite Lager 8 während des Betriebs nicht austrocknet. Zu diesem Zweck sind geeignete konstruktive Massnahmen getroffen, damit auf beiden Seiten des zweiten Lagers 8 derselbe Druck herrscht. Die dem Gegengewicht 21 zugekehrte erste Seite des zweiten Lagers 8 wird durch den Druck im Förderraum 18 beaufschlagt. Damit auch auf der andern, zweiten Seite des zweiten Lagers 8 derselbe Druck herrscht ist eine Verbindungsleitung 38 vorgesehen, die den Förderraum 18 mit dieser andern, zweiten Seite des zweiten Lagers 8 verbindet.The second bearing 8 for the drive shaft 6 is also grease lubricated, taking care that the second bearing 8 does not dry out during operation. For this purpose, appropriate structural measures are taken so that on both sides of the second bearing 8, the same pressure prevails. The counterweight 21 facing first side of the second bearing 8 is acted upon by the pressure in the delivery chamber 18. Thus, the same pressure prevails on the other, second side of the second bearing 8, a connecting line 38 is provided which connects the delivery chamber 18 with this other, second side of the second bearing 8.

Sowohl das erste Lager 7 für die Antriebswelle 6 wie auch das Nabenlager 10 für die Exzenterscheibe 9 werden auf nicht näher dargestellte Weise mit einem flüssigen Schmiermittel, vorzugsweise Schmieröl, geschmiert. Die Lager 7 und 10 sind mittels ringförmiger Dichtelemente 39 gegenüber den Förderräumen 18, 18' abgedichtet.Both the first bearing 7 for the drive shaft 6 and the hub bearing 10 for the eccentric disc 9 are lubricated in a manner not shown with a liquid lubricant, preferably lubricating oil. The bearings 7 and 10 are sealed by means of annular sealing elements 39 with respect to the delivery chambers 18, 18 '.

Wie aus den Fig. 2 und 3 ersichtlich ist, wird jedes Gegengewicht 20, 21 durch einen mit der Antriebswelle 6 drehfest verbundenen Befestigungsteil 46 und einen Massenteil 47, der mit dem Befestigungsteil 46 aus einem Stück besteht, gebildet. Der Befestigungsteil 46 jedes Gegengewichtes 20, 21 hat in axialer Richtung gesehen eine möglichst geringe Abmessung, was es ermöglicht, das erste und zweite Lager 7 bzw. 8 so nahe als möglich an die Exzenterscheibe 9 heran zu rücken. Mit dieser Massnahme kann die Durchbiegung der Antriebswelle 6 während des Betriebs quasi verhindert werden.Like from the FIGS. 2 and 3 it can be seen, each counterweight 20, 21 is formed by a fixing member 46 non-rotatably connected to the drive shaft 6 and a mass member 47 integral with the fixing member 46. The fastening part 46 of each counterweight 20, 21 has as small a dimension as possible in the axial direction, which makes it possible to bring the first and second bearings 7 and 8 as close as possible to the eccentric disk 9. With this measure, the deflection of the drive shaft 6 during operation can be virtually prevented.

Der innere Radius R des Massenteils 47 (Fig. 3) ist so bemessen, dass er grösser ist als die in Fig. 2 mit D bezeichnete radiale Abmessung der Nabe 11 der Scheibe 3 und auch grösser als der Aussendurchmesser der Lageraufnahmen 48a, 48b. Das erlaubt es, den Massenteil 47 in radialer Richtung ausserhalb der Nabe 11 anzuordnen, wie das aus Fig. 2 ersichtlich ist. Die Abmessung des Massenteils 47 jedes Gegengewichtes 20, 21 kann daher in axialer Richtung gesehen grösser als die axiale Abmessung des Befestigungsteils 46 gewählt werden. Dies ermöglicht es, den Befestigungsteil 46 ganz nahe an der Exzenterscheibe 9 und der Nabe 11 anzuordnen und trotzdem bei der Ausgestaltung des Massenteils 47 eine gewisse Freiheit zu haben.The inner radius R of the mass part 47 ( Fig. 3 ) is sized to be larger than the one in Fig. 2 D designated radial dimension of the hub 11 of the disc 3 and also larger than the outer diameter of the bearing mounts 48a, 48b. This makes it possible to arrange the mass portion 47 in the radial direction outside the hub 11, like that Fig. 2 is apparent. The dimension of the mass portion 47 of each counterweight 20, 21 can therefore be selected in the axial direction greater than the axial dimension of the fastening part 46. This makes it possible to arrange the fastening part 46 very close to the eccentric disc 9 and the hub 11 and still have a certain freedom in the design of the mass member 47.

Die Grösse des durch die Gegengewichte 20, 21 bewirkten Massenausgleichs kann durch eine geeignete Dimensionierung der Massenteile 47 bestimmt werden. Im vorliegenden Beispiel weisen die Gegengewichte einen T-förmigen Querschnitt auf, wobei die Querbalken die eigentlichen Massenteile 47 darstellen und so konfiguriert sind, dass sie sowohl die Nabe 11 als auch die Lageraufnahmen 48a, 48b beidseitig überdecken, zumindest teilweise.The size of the balance caused by the counterweights 20, 21 can be determined by a suitable dimensioning of the mass parts 47. In the present example, the counterweights have a T-shaped cross section, wherein the crossbars represent the actual mass parts 47 and are configured so that they cover both the hub 11 and the bearing receivers 48 a, 48 b on both sides, at least partially.

Die in den Figuren gezeigten und vorstehend beschriebenen Verdrängermaschinen eignen sich insbesondere als Aufladeaggregate für Brennkraftmaschinen. The displacement machines shown in the figures and described above are particularly suitable as superchargers for internal combustion engines.

Claims (9)

  1. A displacement machine for compressible media, comprising at least one spiral-shaped conveying space (18, 18') which is arranged in a fixed housing (1) consisting of two housing halves (1 a, 1 b) and comprises an inlet (16) which opens into the radial outer region of the spiral-shaped conveying space (18, 18'), and comprising an outlet (17) which is arranged in the radial inner region of the conveying space (18, 18'), and a displacement body (2) which is associated with the conveying space (18, 18') and substantially consists of a support disc (3) and spiral leaves (4, 5) which protrude therefrom on both sides, wherein the displacement body is mounted by means of a bearing (10) on an eccentric disc (9), which is connected to a driveable drive shaft (6) that is rotatable about a rotational axis (6a) and is rotatably mounted on either side of the eccentric disc (9) by means of a first and second bearing (7, 8) in the housing (1), and having counterweights (20, 21) which are seated on either side of the eccentric disc (9) on the drive shaft (6) and which are respectively arranged directly adjacent to the eccentric disc (9) between said disc and one of the two bearings (7, 8) on the drive shaft (6) and are connected to the drive shaft (6) in a torsion-proof manner, wherein the drive shaft (6) extends on the drive side through the housing wall of the housing half (1 b) and carries a drive disc (23) at its end on the drive side, characterized in that each half (1 a, 1 b) of the housing is provided with a bearing receiver (48a, 48b) which protrudes into the respective conveying space (18, 18'), so that the distance between the bearings (7, 8) and the respectively adjacent counterweight (20, 21) is kept as small as possible, wherein the centre points of the two bearings (7, 8) respectively lie in a plane with respect to their extension parallel to the rotational axis (6a), which plane extends perpendicularly to the rotational axis (6a) of the drive shaft (6), wherein said plane respectively lies within the respective conveying space (18', 18).
  2. A displacement machine according to claim 1, characterized in that each counterweight (20, 21) comprises a mass part (47) which is arranged at a distance from the rotational axis (6a) of the drive shaft (6) and which is connected to a fastening part (46) which is coupled in a torsion-proof manner to the drive shaft (6) and whose axial dimension in the direction of the rotational axis (6a) of the drive shaft (6) is smaller than the respective axial dimension of the mass part (47), and that the mass part (47), in its axial extension, covers both the hub 11 and also the respective bearing receiver (48a, 48b) at least partly on both sides.
  3. A displacement machine according to one of the preceding claims 1 to 2, characterized in that the counterweights (20, 21) are arranged in a T-shaped manner and the mass part (47) covers both the hub (11) and also the bearing receiver (48, 48b) on both sides to the same extent.
  4. A displacement machine according to one of the preceding claims 1 to 3, characterized by a support part (25) which protrudes in the direction of the longitudinal axis (6a) of the drive shaft (6) from the housing (1) of the housing half and is connected to the latter, and is penetrated by the drive shaft (6) and in which a third bearing (24) is supported.
  5. A displacement machine according to one of the preceding claims 1 to 4, characterized in that the second bearing (8) is lubricated by grease and the bearing receiver (48b) of the second bearing (8) is provided with a connecting line (38) between the conveying space (18) and the second bearing (8), and the same pressure prevails on both sides of the second bearing (8).
  6. A displacement machine according to one of the preceding claims 1 to 5 characterized by a labyrinth seal which is arranged in the region of the passage of the drive shaft (6) through the housing (1) between the latter and the drive shaft (6), and which consists of at least two throttling points which are arranged one behind the other in the longitudinal direction of the drive shaft (6), wherein a connecting line opens into the space between two adjacent throttling points, which connecting line is connected to the inlet (16) of the displacement machine.
  7. A displacement machine according to claim 5, characterized in that the third bearing (24) is lubricated by grease, wherein means are present so that the ambient pressure prevails on both sides of the third bearing (24).
  8. A displacement machine according to claim 7, characterized in that a passage is arranged in the support part (25) which connects the space on one side of the third bearing (24) to the ambient environment.
  9. A displacement machine according to one of the preceding claims 1 to 8, characterized in that the first bearing (7) and the hub bearing (10) of the displacement machine are lubricated by a liquid lubricant.
EP08757302.8A 2007-07-26 2008-07-10 Displacement machine according to the spiral principle Not-in-force EP2179138B1 (en)

Applications Claiming Priority (2)

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CH11962007 2007-07-26
PCT/CH2008/000310 WO2009012606A2 (en) 2007-07-26 2008-07-10 Displacement machine according to the spiral principle, comprising a bearing assembly on both sides

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EP2179138A2 EP2179138A2 (en) 2010-04-28
EP2179138B1 true EP2179138B1 (en) 2015-09-09

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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
CN101947812B (en) * 2010-09-09 2012-05-30 太原重工股份有限公司 Supporting roll device of carbon extruding machine extrusion rod
US11055952B2 (en) 2019-03-18 2021-07-06 Igt Gaming system and method providing free activations with pattern matching feature

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EP0807759A2 (en) * 1990-02-13 1997-11-19 Iwata Air Compressor Mfg. Co.,Ltd. Scroll-type fluid machinery
WO2000049275A1 (en) * 1999-02-18 2000-08-24 Fritz Spinnler Displacement machine based on the spiral principle

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DE3313000A1 (en) * 1983-04-12 1984-10-18 Volkswagenwerk Ag, 3180 Wolfsburg Displacement machine for compressible media
JPH0680317B2 (en) * 1985-03-20 1994-10-12 トキコ株式会社 Oil-free scroll compressor
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EP0371305B1 (en) * 1988-11-30 1993-09-22 AGINFOR AG für industrielle Forschung Excentric shaft with a counter weight
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EP0201774A1 (en) * 1985-04-26 1986-11-20 BBC Brown Boveri AG Rotary piston positive-displacement machine
EP0807759A2 (en) * 1990-02-13 1997-11-19 Iwata Air Compressor Mfg. Co.,Ltd. Scroll-type fluid machinery
WO2000049275A1 (en) * 1999-02-18 2000-08-24 Fritz Spinnler Displacement machine based on the spiral principle

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WO2009012606A3 (en) 2009-05-28
CN101765700A (en) 2010-06-30
EP2179138A2 (en) 2010-04-28
CN101765700B (en) 2012-03-21
US20100183466A1 (en) 2010-07-22
US8529233B2 (en) 2013-09-10
WO2009012606A2 (en) 2009-01-29

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