EP0201774A1 - Rotary piston positive-displacement machine - Google Patents

Rotary piston positive-displacement machine Download PDF

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Publication number
EP0201774A1
EP0201774A1 EP86105671A EP86105671A EP0201774A1 EP 0201774 A1 EP0201774 A1 EP 0201774A1 EP 86105671 A EP86105671 A EP 86105671A EP 86105671 A EP86105671 A EP 86105671A EP 0201774 A1 EP0201774 A1 EP 0201774A1
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EP
European Patent Office
Prior art keywords
rotor
housing
spiral
section
displacers
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP86105671A
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German (de)
French (fr)
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EP0201774B1 (en
Inventor
Heinrich Güttinger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BBC Brown Boveri AG Switzerland
Aginfor AG
Original Assignee
BBC Brown Boveri AG Switzerland
Aginfor AG fuer industrielle Forschung
Aginfor AG
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Application filed by BBC Brown Boveri AG Switzerland, Aginfor AG fuer industrielle Forschung, Aginfor AG filed Critical BBC Brown Boveri AG Switzerland
Priority to AT86105671T priority Critical patent/ATE36895T1/en
Publication of EP0201774A1 publication Critical patent/EP0201774A1/en
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Publication of EP0201774B1 publication Critical patent/EP0201774B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/0207—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F01C1/0215—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F01C1/0223—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving with symmetrical double wraps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F01C1/0246—Details concerning the involute wraps or their base, e.g. geometry
    • 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
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/50—Inlet or outlet

Definitions

  • Such a displacement machine is suitable for charging an internal combustion engine, since it is characterized by an almost pulsation-free delivery of the working medium, which consists, for example, of air or an air / fuel mixture.
  • the working medium which consists, for example, of air or an air / fuel mixture.
  • a machine of the type mentioned is known from DE-31 41 525 Al. With this compressor, two displacers mounted on a rotor mesh with each other.
  • the associated conveying spaces in the fixed housing each run from an inlet space provided on the outer periphery of the housing to an outlet space provided on the inner periphery of the housing, via which the compressed working medium is discharged.
  • the centrally arranged drive shaft for the rotor together with a part of the shaft bearing and the rotor bearings is also housed in the interior of the housing. These parts are washed by the hot, compressed air and are therefore not accessible for cooling.
  • there is no longer any space for accommodating cooling chambers as are known, for example, from DE-26 03 462 C2 already mentioned, and moreover still need to be connected to a separate cooling circuit.
  • the present invention is therefore based on the object of providing a displacement machine of the type mentioned at the outset, in which heat can be dissipated during the compression.
  • the advantage of the invention is, on the one hand, that the drive bearings are now in the suction area of the spirals and are therefore cooled with fresh air, which is an important prerequisite for maintenance-free or at least low-maintenance bearings.
  • the spiral arrangement due to the spiral arrangement, access for the cooling medium to the hot part of the spirals, which is favorable for heat dissipation during compression, is achieved, so that, if it is intended to be used as a charging device for internal combustion engines, a separate after-cooling of the charge air can be dispensed with.
  • the housing is expediently provided with cooling fins all around.
  • the machine which is represented in approximately 80% of its natural size, is equipped with two conveying rooms on each rotor side.
  • the direction of flow of the working medium, for example air, is indicated by arrows.
  • the fixed housing is composed of the drive-side part housing 1 and the air-side part housing 2, which are attached to the housing periphery via several Flanges 3 are screwed together.
  • the two delivery spaces 4 are incorporated in the housing parts in the manner of a spiral slot. These conveying spaces each run from an inlet 5 arranged at the outer spiral end to an outlet 6 arranged at the inner spiral end.
  • the two inlets 5 and the outlets 6 communicate with one another in a manner not shown and are each provided with an air inlet 9 or air outlet on the partial housing 2 on the air side.
  • Air outlet 10 connected (Fig. 2).
  • the disk-shaped rotor is designated as a whole by 11.
  • displacer 13 On both sides of the disc 12 are spiral extending displacer 13 is provided, which are arranged as band-shaped strips on the disc. These displacers 13 are held between the peripheral walls 7, 8 of the delivery spaces 4. Their curvature is dimensioned such that they almost touch the inner peripheral walls 7 and the outer peripheral walls 8 at several points B1, B2 and B3 at the same time.
  • the centers 14 of the two displacers 13 are offset eccentrically with respect to the centers 15 of the two delivery spaces 4 (FIG. 1).
  • the displacers 13 must have the same geometry as the conveying spaces, that is to say form a spiral with the centers 14, 34 consisting of two circular sections 130 ′, 130 ′′, which comprises more than 360 °.
  • the displacers 13 and thus the rotor 11 are mounted and guided in order to carry out a circular, rotation-free movement.
  • the rotor is arranged on an eccentric disk 17 by means of a ball bearing 16.
  • This eccentric disc sits on a drive shaft 18, which in turn is mounted in the fixed housing in ball bearings 19, 20, 21 and 22. Not shown is the drive of the shaft 18, which usually takes place via a V-belt pulley. To compensate for the inertial forces arising when the rotor 11 is eccentrically driven, bearings 19 and 20, respectively. 21 and 22 arranged on the drive shaft counterweights 23.
  • the eccentric drive of the disk-shaped rotor having the displacers results in a circular movement of each of the points of the displacers, this circular movement being limited by the peripheral walls of the delivery spaces is.
  • crescent-shaped work spaces 24 which contain the working medium, result on both sides of the displacers, which are advanced as a result of the eccentric movement through the delivery spaces in the direction of the respective outlet 6. The volume of these working spaces is reduced and the pressure of the working fluid increases accordingly.
  • Shaft bearings 19 to 22 are located all around in the intake area and be cooled accordingly with fresh air.
  • the centers 14, 15 of the first spiral sections 40 ', 130' are located approximately in the middle between the machine axis and the outlets 6, which results in a very space-saving spiral configuration.
  • the air is thus conveyed from the inside to the outside, making the machine parts heated due to the compression easy to cool.
  • the outer peripheral walls 8 of the hot spiral sections are provided with cooling fins 27 throughout.
  • the two housing parts 1, 2 are expediently equipped with such cooling fins over their entire circumference (FIG. 1).
  • the rotor disk 12 In order to guide the sucked in working fluid from the air-side to the drive-side delivery areas, respectively. To discharge in the opposite direction, the rotor disk 12 is provided with openings 28 of corresponding shape in the area of the inlets 5 and outlets 6 (FIG. 3).
  • the compressed air in the outlet 10 is in the same state throughout, since it is always a mixture of an inner working chamber 24 'and an outer working chamber 24 ".
  • the eccentric disc 17 is namely aligned in this way on the drive shaft 18, that - as in the example in FIG. 1 - the points B1 and B2 (of the two displacers 13 with the peripheral walls of the delivery spaces 4), the centers 14, 15 of the two spirals and the axes 25, 26 of the drive shaft and eccentric disc in a certain position lie on a common line 29.
  • the displacer forms the narrowest gap with the outer peripheral wall 8, in the case of the lower spiral at point B2, however, with the inner peripheral wall 7 of the delivery space 4.
  • the central symmetrical spiral arrangement also compensates for the tilting moment which would arise when operating with a single spiral with the drive bearing moved from the center. This has the advantage that the device required for translatory guiding of the rotor 11 can be of simple design.
  • the runner is guided by means of four free-running roller bolts 30, which are distributed over the circumference of the machine. It is not necessary for the rolling pins to be on the same pitch circle, nor for them to have the same angular distances from one another. These freedoms allow the guide device to be accommodated in a space-saving manner without impairing the spiral course.
  • a rolling pin rolls in a bore 31 of the rotor and a matching, identical bore 32 in both housing parts 1, 2. So that the rolling pin is in a secure system at all times, its diameter is smaller by the eccentricity between the eccentric axis 26 and the drive axis 25 than the diameter of the housing bores 32.
  • the roller pin position shown in FIG. 3 corresponds to the displacer position in FIG. 1, in which the upper displacer almost touches the outer peripheral wall 8 of the delivery chamber 4 at point B2.
  • the invention is not limited to what is shown and described.
  • classic spiral shapes such as for example the Archimedean spiral or even involutes are used. It is only necessary to ensure that the radius of curvature of the second section is always significantly smaller than that of the first section.
  • a fan could be mounted outside the housing on the drive shaft, for example, which forcibly ventilates the cooling fins during operation.
  • This fan could possibly also be arranged on the air side of the housing if, for example, the drive shaft were passed through the partial housing 2.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Reciprocating Pumps (AREA)
  • Supercharger (AREA)

Abstract

In a rotary-piston displacement machine, as is suitable, for example, for supercharging internal combustion engines, having at least two spiral-like delivery chambers in a stationary housing and spiral-like displacers engaging therein which execute a circulating, torsion-free movement with respect to the delivery chambers, the displacers are arranged on an eccentrically driven, disk-shaped rotor. The rotor is driven via a shaft centrally arranged in the inside of the housing. The two spirals run centro-symmetrically to one another in such a way that their suction-side ends are arranged around the drive bearings and at the same time cool the latter with fresh air. The air is delivered outwards from the inside of the housing, as a result of which heat dissipation of the outer housing parts during compression is provided for, which housing parts are provided with cooling ribs.

Description

Die Erfindung betrifft eine Rotationskolben-Verdrängungsarbeitsmaschine für kompressible Medien

  • - mit mindestens zwei in einem feststehenden Gehäuse spiralartig verlaufenden, mehr als 360° umspannenden Förderräumen, die je von einem Einlass zu einem Auslass führen;
  • - mit einem jedem Förderraum zugeordneten und in diesen eingreifenden, ebenfalls spiralartig verlaufenden und mehr als 360° umspannenden Verdränger, der als bandförmige Leiste auf einem gegenüber dem Gehäuse exzentrisch angetriebenen scheibenförmigen Läufer angeordnet ist, und der in Bezug auf die Förderräume zur Ausführung einer kreisenden, verdrehungsfreien Bewegung gelagert und geführt ist;
  • - bei welcher die spiralartigen Förderräume und Verdränger aus jeweils zwei Abschnitten bestehen, wobei sich an das auslasseitige Ende eines ersten, weniger als 360° umspannenden Abschnittes stetig ein zweiter Abschnitt anschliesst, dessen Krümmungsradius wesentlich kleiner ist als der kleinste Krümmungsradius des ersten Abschnittes, so dass der zweite Abschnitt zwischen dem auslasseitigen Ende und dem Zentrum des ersten Abschnittes liegt.
The invention relates to a rotary piston displacement machine for compressible media
  • - With at least two spiral-shaped, more than 360 ° spanning conveying spaces in a fixed housing, each leading from an inlet to an outlet;
  • - With a displacement chamber which is assigned to each delivery chamber and engages in it, also spiraling and spans more than 360 °, which is arranged as a band-shaped bar on a disc-shaped rotor which is driven eccentrically with respect to the housing, and which, in relation to the delivery rooms, performs a rotating rotation and movement is stored and guided;
  • - In which the spiral-like conveying spaces and displacers each consist of two sections, with a second section continuously adjoining the outlet-side end of a first section spanning less than 360 °, the radius of curvature of which is considerably smaller than the smallest radius of curvature of the first section, so that the second section lies between the outlet end and the center of the first section.

Eine derartige Verdrängungsmaschine, deren Prinzip aus der DE-26 03 462 C2 bekannt ist, eignet sich für die Aufladung einer Brennkraftmaschine, da sie sich durch eine nahezu pulsationsfreie Förderung des beispielsweise aus Luft oder aus einem Luft-Kraftstoff-Gemisch bestehenden Arbeitsmittels auszeichnet. Während des Betriebes eines derartigen Spiralladers werden entlang des Förderraumes zwischen dem Verdränger und den beiden Umfangswänden des Förderraumes sichelförmige Arbeitsräume eingeschlossen, die sich vom Einlass durch den Förderraum hindurch zum Auslass hin bewegen. Hierbei verringert sich ihr Volumen zunehmend bei einer entsprechenden Erhöhung des Arbeitsmitteldruckes.Such a displacement machine, the principle of which is known from DE-26 03 462 C2, is suitable for charging an internal combustion engine, since it is characterized by an almost pulsation-free delivery of the working medium, which consists, for example, of air or an air / fuel mixture. During the operation of such a spiral loader, crescent-shaped working spaces are trapped along the delivery space between the displacer and the two peripheral walls of the delivery space, which work spaces move from the inlet through the delivery space to the outlet. Here, their volume decreases increasingly with a corresponding increase in the working fluid pressure.

Eine Maschine der eingangs genannten Art ist bekannt aus der DE-31 41 525 Al. Bei diesem Verdichter greifen zwei auf einem Läufer angebrachte Verdränger ineinander ein. Die hierzu gehörenden Förderräume in dem feststehenden Gehäuse verlaufen jeweils von einem am äusseren Umfang des Gehäuses vorgesehenen Einlassraum zu einem am inneren Umfang des Gehäuses vorgesehenen Auslassraum, über den das verdichtete Arbeitsmittel abgeführt wird. Im Gehäuseinnern ist ebenfalls die zentral angeordnete Antriebswelle für den Läufer mitsamt eines Teiles der Wellenlagerung und der Läuferlager untergebracht. Diese Teile werden von der heissen, verdichteten Luft umspült und sind somit einer Kühlung nicht zugänglich. Insbesondere ist kein Raum mehr vorhanden zum Unterbringenvon Kühlkammern, wie sie beispielsweise aus der bereits genannten DE-26 03 462 C2 bekannt sind, und die zudem noch mit einem separaten Kühlkreislauf verbunden werden müssen.A machine of the type mentioned is known from DE-31 41 525 Al. With this compressor, two displacers mounted on a rotor mesh with each other. The associated conveying spaces in the fixed housing each run from an inlet space provided on the outer periphery of the housing to an outlet space provided on the inner periphery of the housing, via which the compressed working medium is discharged. The centrally arranged drive shaft for the rotor together with a part of the shaft bearing and the rotor bearings is also housed in the interior of the housing. These parts are washed by the hot, compressed air and are therefore not accessible for cooling. In particular, there is no longer any space for accommodating cooling chambers, as are known, for example, from DE-26 03 462 C2 already mentioned, and moreover still need to be connected to a separate cooling circuit.

Der vorliegenden Erfindung liegt deshalb die Aufgabe zugrunde, eine Verdrängungsmaschine der eingangs genannten Art zu schaffen, bei welcher eine Wärmeabfuhr während der Verdichtung stattfinden kann.The present invention is therefore based on the object of providing a displacement machine of the type mentioned at the outset, in which heat can be dissipated during the compression.

Erfindungsgemäss wird dies dadurch erreicht,

  • - dass die mindestens zwei spiralartigen Förderräume, ohne einen gemeinsamen Pol aufzuweisen, zentralsymmetrisch zueinander angeordnet sind,
  • - dass die einlasseitigen Enden der Förderräume um die Antriebslagerung des Läufers herum angeordnet sind.
According to the invention, this is achieved by
  • that the at least two spiral conveying spaces, without having a common pole, are arranged centrally symmetrically to one another,
  • - That the inlet-side ends of the delivery spaces are arranged around the drive bearing of the rotor.

Der Vorteil der Erfindung ist zum einen darin zu sehen, dass die Antriebslager nunmehr im Ansaugbereich der Spiralen liegen und somit mit Frischluft gekühlt werden, was eine wichtige Voraussetzung für wartungsfreie oder zumindest wartungsarme Lager ist. Zum andern wird infolge der Spiralenanordnung ein für die Wärmeabfuhr während der Verdichtung günstiger Zugang des Kühlmediums zum heissen Teil der Spiralen erzielt, so dass, falls eine Verwendung als Aufladegerät für Verbrennungsmotoren beabsichtigt ist, auf eine gesonderte Nachkühlung der Ladeluft verzichtet werden kann.The advantage of the invention is, on the one hand, that the drive bearings are now in the suction area of the spirals and are therefore cooled with fresh air, which is an important prerequisite for maintenance-free or at least low-maintenance bearings. On the other hand, due to the spiral arrangement, access for the cooling medium to the hot part of the spirals, which is favorable for heat dissipation during compression, is achieved, so that, if it is intended to be used as a charging device for internal combustion engines, a separate after-cooling of the charge air can be dispensed with.

Zweckmässigerweise wird das Gehäuse hierzu rundum mit Kühlrippen versehen.For this purpose, the housing is expediently provided with cooling fins all around.

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

Es zeigen:

  • Fig. 1 einen Querschnitt durch die Verdrängungsmaschine in der Ebene der Förderräume
  • Fig. 2 einen Längsschnitt nach Schnittlinie C-C in Fig. 1
  • Fig. 3 einen Querschnitt in der Ebene der Läuferscheibe
  • Fig. 4 einen Längsschnitt nach Schnittlinie D-D in Fig. 3.
Show it:
  • Fig. 1 shows a cross section through the displacement machine in the plane of the delivery rooms
  • FIG. 2 shows a longitudinal section along section line CC in FIG. 1
  • Fig. 3 shows a cross section in the plane of the rotor disk
  • 4 shows a longitudinal section along section line DD in FIG. 3.

Die in etwa 80 % ihrer natürlichen Grösse dargestellte Maschine ist mit je zwei Förderräumen pro Läuferseite ausgerüstet. Die Strömungsrichtung des Arbeitsmediums, beispielsweise Luft, ist mit Pfeilen bezeichnet.The machine, which is represented in approximately 80% of its natural size, is equipped with two conveying rooms on each rotor side. The direction of flow of the working medium, for example air, is indicated by arrows.

Zur Erläuterung der Funktionsweise des Verdichters, welche nicht Gegenstand der Erfindung ist, wird auf die genannte DE-26 03 462 C2 verwiesen. Nachstehend wird nur der für das Verständnis notwendige Maschinenaufbau und Prozessablauf kurz beschrieben.To explain the operation of the compressor, which is not the subject of the invention, reference is made to the aforementioned DE-26 03 462 C2. In the following, only the machine structure and process flow necessary for understanding are briefly described.

Der besseren Uebersicht wegen ist in der Fig. 3 die Schnittfläche des Läufers nicht schraffiert, hingegen sind die nicht geschnittenen spiralartigen Verdränger punktiert dargestellt.For the sake of a better overview, the cut surface of the rotor is not hatched in FIG. 3, on the other hand the uncut spiral-type displacers are shown in dotted lines.

Das feststehende Gehäuse setzt sich aus dem antriebsseitigen Teilgehäuse 1 und dem luftseitigen Teilgehäuse 2 zusammen, die über mehrere, am Gehäuseumfang angebrachte Flansche 3 miteinander verschraubt sind. In die Gehäuseteile sind die beiden Förderräume 4 nach Art eines spiralförmigen Schlitzes eingearbeitet. Diese Förderräume verlaufen von je einem am äusseren Spiralenende angeordneten Einlass 5 zu einem am inneren Spiralenende angeordneten Auslass 6. Die beiden Einlässe 5 bzw. die Auslässe 6 kommunizieren untereinander auf nicht dargestellte Weise und sind mit je einem am luftseitigen Teilgehäuse 2 angeordneten Lufteintritt 9 resp. Luftaustritt 10 verbunden (Fig. 2).The fixed housing is composed of the drive-side part housing 1 and the air-side part housing 2, which are attached to the housing periphery via several Flanges 3 are screwed together. The two delivery spaces 4 are incorporated in the housing parts in the manner of a spiral slot. These conveying spaces each run from an inlet 5 arranged at the outer spiral end to an outlet 6 arranged at the inner spiral end. The two inlets 5 and the outlets 6 communicate with one another in a manner not shown and are each provided with an air inlet 9 or air outlet on the partial housing 2 on the air side. Air outlet 10 connected (Fig. 2).

Die Förderräume 4 weisen parallele, in gleichbleibendem Abstand zueinander angeordnete Umfangswände 7, 8 auf, die eine Spirale von mehr als 360° umfassen. Hierbei setzt sich die Spirale aus zwei Abschnitten zusammen, die in Fig. 1 am Beispiel der äusseren Umfangswand 8 der unteren Spirale erläutert sind:

  • Zunächst ein erster Abschnitt 40' in Form eines Kreisbogens, der weniger als 360° umspannt. Im vorliegenden Fall umspannt dieser erste Kreisbogen mit seinem Zentrum 15 einen Winkel von ca. 240° und beginnt am einlasseitigen Ende des Förderraumes 4. An seinem auslasseitigen Ende schliesst sich stetig ein zweiter Abschnitt 40" ebenfalls in Form eines Kreisbogens mit dem Zentrum 33 an, der hier einen Winkel von ca. 180° umfasst. Der Krümmungsradius des zweiten Abschnittes 40" ist wesentlich kleiner als jener des ersten Abschnittes 40'. Dadurch findet der ganze zweite Abschnitt 40" Platz zwischen dem auslasseitigen Ende des ersten Abschnittes 40' und dessen Zentrum 15.
The conveying spaces 4 have parallel circumferential walls 7, 8 which are arranged at a constant distance from one another and which comprise a spiral of more than 360 °. Here, the spiral is composed of two sections, which are explained in FIG. 1 using the example of the outer peripheral wall 8 of the lower spiral:
  • First, a first section 40 'in the form of an arc that spans less than 360 °. In the present case, this first circular arc spans an angle of approximately 240 ° with its center 15 and begins at the inlet-side end of the delivery chamber 4. At its outlet-side end, a second section 40 "also continuously adjoins in the form of a circular arc with the center 33, which here encompasses an angle of approximately 180 °. The radius of curvature of the second section 40 ″ is substantially smaller than that of the first section 40 ′. As a result, the entire second section 40 ″ finds space between the outlet-side end of the first section 40 ′ and its center 15.

Mit 11 ist der scheibenförmige Läufer insgesamt bezeichnet. An beiden Seiten der Scheibe 12 sind spiralförmig verlaufende Verdränger 13 vorgesehen, die als bandförmige Leisten auf der Scheibe angeordnet sind. Diese Verdränger 13 werden zwischen den Umfangswänden 7, 8 der Förderräume 4 gehalten. Ihre Krümmung ist so bemessen, dass sie gleichzeitig die inneren Umfangswände 7 und die äusseren Umfangswände 8 an mehreren Stellen Bl, B2 und B3 nahezu berühren. Hierzu sind die Zentren 14 der beiden Verdränger 13 gegenüber den Zentren 15 der beiden Förderräume 4 exzentrisch versetzt (Fig. l). Es versteht sich, dass die Verdränger 13 die gleiche Geometrie aufweisen müssen wie die Förderräume, d.h. eine aus zwei kreisförmigen Abschnitten 130', 130" bestehende Spirale mit den Zentren 14, 34 bilden, die mehr als 360° umfasst.The disk-shaped rotor is designated as a whole by 11. On both sides of the disc 12 are spiral extending displacer 13 is provided, which are arranged as band-shaped strips on the disc. These displacers 13 are held between the peripheral walls 7, 8 of the delivery spaces 4. Their curvature is dimensioned such that they almost touch the inner peripheral walls 7 and the outer peripheral walls 8 at several points B1, B2 and B3 at the same time. For this purpose, the centers 14 of the two displacers 13 are offset eccentrically with respect to the centers 15 of the two delivery spaces 4 (FIG. 1). It goes without saying that the displacers 13 must have the same geometry as the conveying spaces, that is to say form a spiral with the centers 14, 34 consisting of two circular sections 130 ′, 130 ″, which comprises more than 360 °.

In Bezug auf die Förderräume sind die Verdränger 13 und damit der Läufer 11 zur Ausführung einer kreisenden, verdrehungsfreien Bewegung gelagert und geführt. Hierzu ist der Läufer mittels eines Kugellagers 16 auf einer Exzenterscheibe 17 angeordnet.With regard to the conveying spaces, the displacers 13 and thus the rotor 11 are mounted and guided in order to carry out a circular, rotation-free movement. For this purpose, the rotor is arranged on an eccentric disk 17 by means of a ball bearing 16.

Diese Exzenterscheibe sitzt auf einer Antriebswelle 18, die ihrerseits im feststehenden Gehäuse in Kugellagern 19, 20, 21 und 22 gelagert ist. Nicht gezeigt ist der üblicherweise über eine Keilriemenscheibe erfolgende Antrieb der Welle 18. Zum Ausgleich der beim exzentrischen Antrieb des Läufers 11 entstehenden Massenkräfte sind zwischen den Lagern 19 und 20 resp. 21 und 22 auf der Antriebswelle Gegengewichte 23 angeordnet.This eccentric disc sits on a drive shaft 18, which in turn is mounted in the fixed housing in ball bearings 19, 20, 21 and 22. Not shown is the drive of the shaft 18, which usually takes place via a V-belt pulley. To compensate for the inertial forces arising when the rotor 11 is eccentrically driven, bearings 19 and 20, respectively. 21 and 22 arranged on the drive shaft counterweights 23.

Während des Betriebes der Maschine stellt sich durch den exzentrischen Antrieb des scheibenförmigen, die Verdränger aufweisenden Läufers eine Kreisbewegung jedes der Punkte der Verdränger ein, wobei diese Kreisbewegung durch die Umfangswände der Förderräume begrenzt ist. Infolge der mehrfachen, abwechselnden Annäherung der Verdränger an die inneren und äusseren Umfangswände ergeben sich auf beiden Seiten der Verdränger sichelförmige, das Arbeitsmedium einschliessende Arbeitsräume 24, die infolge der exzentrischen Bewegung durch die Förderräume in Richtung auf den jeweiligen Auslass 6 vorgeschoben werden. Hierbei verringert sich das Volumen dieser Arbeitsräume und der Druck des Arbeitsmittels erhöht sich entsprechend. Bei Originalgrösse und der in den Figuren dargestellten Spiralengeometrie und Exzentrizität ist mit Luft als Arbeitsmittel bei einer Antriebswellendrehzahl von 12'500 Umdrehungen pro Minute ein Fördervolumen von ca. 130 Liter pro Sekunde mit einem Druckverhältnis PAustritt zu PEintritt von ca. 1,5 erzielbar.During operation of the machine, the eccentric drive of the disk-shaped rotor having the displacers results in a circular movement of each of the points of the displacers, this circular movement being limited by the peripheral walls of the delivery spaces is. As a result of the multiple, alternating approach of the displacers to the inner and outer circumferential walls, crescent-shaped work spaces 24, which contain the working medium, result on both sides of the displacers, which are advanced as a result of the eccentric movement through the delivery spaces in the direction of the respective outlet 6. The volume of these working spaces is reduced and the pressure of the working fluid increases accordingly. With the original size and the spiral geometry and eccentricity shown in the figures, with air as the working medium at a drive shaft speed of 12,500 revolutions per minute, a delivery volume of approx. 130 liters per second with a pressure ratio P outlet to P inlet of approx. 1.5 achievable.

Soweit sind Verdrängermaschinen und hierfür geeignete Antriebe bekannt mit der Einschränkung, dass bei allen bisherigen Spiralformen deren erster Abschnitt einen Winkel von ca. 3600 umfasste.Insofar as positive displacement and suitable for this purpose known drives with the proviso that in all previous spiral forms the first section at an angle of about 360 0 included.

Gemäss der Erfindung sind nun die beiden Spiralen jeder Scheibenseite resp. jedes Teilgehäuses zentralsymmetrisch zueinander angeordnet, wobei die Zentren 14, 15 der ersten Spiralenabschnitte 40', 130' nicht mit der Achse 25 der Antriebswelle 18 resp. der Mittelachse 26 des exzentrisch versetzten Läufers 11 zusammenfallen. Lediglich das Symmetriezentrum der Förderräume 4 liegt in der Antriebsachse 25, und demzufolge liegt das Symmetriezentrum der Verdränger 13 in der Exzenterachse 26. Die Spiralen sind nun so angeordnet, dass die einlassseitigen Enden der ersten Spiralenabschnitte 40', 130' um die Antriebslagerung des Läufers herum angeordnet sind. Sie sind so ineinander verschränkt dass sich die. Wellenlager 19 bis 22 rundum im Ansaugbereich befinden und dementsprechend mit Frischluft gekühlt werden. Die Zentren 14, 15 der ersten Spiralenabschnitte 40', 130' befinden sich ca. mittig zwischen Maschinenachse und den Auslässen 6, was eine sehr platzsparende Spiralenkonfiguration zur Folge hat.According to the invention, the two spirals on each side of the disc. each sub-housing arranged centrally symmetrical to each other, the centers 14, 15 of the first spiral sections 40 ', 130' not with the axis 25 of the drive shaft 18 or. the central axis 26 of the eccentrically offset rotor 11 coincide. Only the center of symmetry of the delivery chambers 4 lies in the drive axis 25, and consequently the center of symmetry of the displacers 13 lies in the eccentric axis 26. The spirals are now arranged such that the inlet-side ends of the first spiral sections 40 ', 130' around the drive bearing of the rotor are arranged. They are so intertwined that the. Shaft bearings 19 to 22 are located all around in the intake area and be cooled accordingly with fresh air. The centers 14, 15 of the first spiral sections 40 ', 130' are located approximately in the middle between the machine axis and the outlets 6, which results in a very space-saving spiral configuration.

Die Luftförderung erfolgt somit von innen nach aussen, wodurch die anlässlich der Verdichtung erwärmten Maschinenteile einer sehr einfachen Kühlmöglichkeit zugänglich werden. Hierzu sind die äusseren Umfangswände 8 der heissen Spiralenabschnitte durchwegs mit Kühlrippen 27 versehen. Zweckmässigerweise sind die beiden Gehäuseteile 1, 2 über ihren ganzen Umfang mit derartigen Kühlrippen bestückt (Fig. 1).The air is thus conveyed from the inside to the outside, making the machine parts heated due to the compression easy to cool. For this purpose, the outer peripheral walls 8 of the hot spiral sections are provided with cooling fins 27 throughout. The two housing parts 1, 2 are expediently equipped with such cooling fins over their entire circumference (FIG. 1).

Um das angesaugte Arbeitsmittel von den luftseitigen zu den antriebsseitigen Förderräumen zu führen resp. in umgekehrter Richtung abzuführen, ist die Läuferscheibe 12 im Bereich der Einlässe 5 und Auslässe 6 mit Durchbrüchen 28 entsprechender Form versehen (Fig. 3).In order to guide the sucked in working fluid from the air-side to the drive-side delivery areas, respectively. To discharge in the opposite direction, the rotor disk 12 is provided with openings 28 of corresponding shape in the area of the inlets 5 and outlets 6 (FIG. 3).

Durch die zentralsymmetrische Spiralenanordnung weist die verdichtete Luft im Austritt 10 durchwegs den gleichen Zustand auf, da es sich immer um ein Gemisch aus einer inneren Arbeitskammer 24' und einer äusseren Arbeitskammer 24" handelt. Die Exzenterscheibe 17 ist nämlich derart auf der Antriebswelle 18 ausgerichtet, dass - wie im Beispiel der Fig. l - in einer bestimmten Stellung die Punkte Bl und B2 (der beiden Verdränger 13 mit den Umfangswänden der Förderräume 4), die Zentren 14, 15 der beiden Spiralen sowie die Achsen 25, 26 von Antriebswelle und Exzenterscheibe auf einer gemeinsamen Linie 29 liegen. Dabei bildet der Verdränger bei der oberen Spirale in Punkt B2 den engsten Spalt mit der äusseren Umfangswand 8, bei der unteren Spirale im Punkt B2 hingegen mit der inneren Umfangswand 7 des Förderraums 4.Due to the centrally symmetrical spiral arrangement, the compressed air in the outlet 10 is in the same state throughout, since it is always a mixture of an inner working chamber 24 'and an outer working chamber 24 ". The eccentric disc 17 is namely aligned in this way on the drive shaft 18, that - as in the example in FIG. 1 - the points B1 and B2 (of the two displacers 13 with the peripheral walls of the delivery spaces 4), the centers 14, 15 of the two spirals and the axes 25, 26 of the drive shaft and eccentric disc in a certain position lie on a common line 29. In the case of the upper spiral at point B2, the displacer forms the narrowest gap with the outer peripheral wall 8, in the case of the lower spiral at point B2, however, with the inner peripheral wall 7 of the delivery space 4.

Die zentralsymmetrische Spiralenanordnung bewirkt überdies einen Ausgleich des Kippmomentes, welches beim Betrieb mit einer einzelnen Spirale mit aus dem Zentrum verlegter Antriebslagerung entstünde. Dies hat den Vorteil, dass die zur translatorischen Führung des Läufers 11 erforderliche Einrichtung einfacher Ausbildung sein kann.The central symmetrical spiral arrangement also compensates for the tilting moment which would arise when operating with a single spiral with the drive bearing moved from the center. This has the advantage that the device required for translatory guiding of the rotor 11 can be of simple design.

Geführt wird der Läufer mittels vier freilaufender Rollbolzen 30, die über den Umfang der Maschine verteilt sind. Hierbei ist es weder erforderlich, dass sich die Rollbolzen auf einem gleichen Teilkreis befinden noch dass sie gleiche Winkelabstände untereinander aufweisen. Diese Freiheiten erlauben es, die Führungseinrichtung ohne Beeinträchtigung des Spiralenverlaufs platzsparend unterzubringen. Ein Rollbolzen rollt jeweils in einer Bohrung 31 des Läufers und einer darauf abgestimmten, gleich grossen Bohrung 32 in beiden Gehäuseteilen 1, 2. Damit der Rollbolzen jederzeit in gesicherter Anlage ist, ist sein Durchmesser um die Exzentrizität zwischen Exzenterachse 26 und Antriebsachse 25 kleiner zu bemessen als der Durchmesser der Gehäusebohrungen 32. Die in Fig. 3 gezeigte Rollbolzenstellung entspricht der Verdrängerstellung in Fig. 1, bei der der obere Verdränger im Punkt B2 die äussere Umfangswand 8 des Förderraumes 4 fast berührt.The runner is guided by means of four free-running roller bolts 30, which are distributed over the circumference of the machine. It is not necessary for the rolling pins to be on the same pitch circle, nor for them to have the same angular distances from one another. These freedoms allow the guide device to be accommodated in a space-saving manner without impairing the spiral course. A rolling pin rolls in a bore 31 of the rotor and a matching, identical bore 32 in both housing parts 1, 2. So that the rolling pin is in a secure system at all times, its diameter is smaller by the eccentricity between the eccentric axis 26 and the drive axis 25 than the diameter of the housing bores 32. The roller pin position shown in FIG. 3 corresponds to the displacer position in FIG. 1, in which the upper displacer almost touches the outer peripheral wall 8 of the delivery chamber 4 at point B2.

Selbstverständlich ist die Erfindung nicht auf das Gezeigte und Beschriebene beschränkt. In Abweichung zur dargestellten Spiralenform, die hier aus zwei Kreisbögen besteht, können selbstverständlich klassische Spiralformen, wie beispielsweise die archimedische Spirale oder sogar Evolventen zur Anwendung gelangen. Es ist lediglich darauf zu achten, dass der Krümmungsradius des zweiten Abschnittes immer wesentlich kleiner ist als jener des ersten Abschnittes.Of course, the invention is not limited to what is shown and described. In deviation from the spiral shape shown, which here consists of two arcs, classic spiral shapes such as for example the Archimedean spiral or even involutes are used. It is only necessary to ensure that the radius of curvature of the second section is always significantly smaller than that of the first section.

Ferner könnte beispielsweise ausserhalb des Gehäuses auf der Antriebswelle ein Lüfter aufgezogen sein, der während des Betriebes die Kühlrippen zwangsbelüftet. Dieser Lüfter könnte ev. auch auf der luftseitigen Gehäuseseite angeordnet sein, wenn beispielsweise die Antriebswelle durch das Teilgehäuse 2 hindurchgeführt würde.Furthermore, a fan could be mounted outside the housing on the drive shaft, for example, which forcibly ventilates the cooling fins during operation. This fan could possibly also be arranged on the air side of the housing if, for example, the drive shaft were passed through the partial housing 2.

Claims (5)

1. Rotationskolben-Verdrängungsarbeitsmaschine für kompressible Medien - mit mindestens zwei in einem feststehenden Gehäuse (1, 2) spiralartig verlaufenden, mehr als 360° umspannenden Förderräumen (4), die je von einem Einlass (5) zu einem Auslass (6) führen, - mit einem jedem Förderraum zugeordneten und in diesen eingreifenden, ebenfalls spiralartig verlaufenden und mehr als 360° umspannenden Verdränger (13), der als bandförmige Leiste auf einem gegenüber dem Gehäuse exzentrisch angetriebenen scheibenförmigen Läufer (11) angeordnet ist, und der in Bezug auf die Förderräume (4) zur Ausführung einer kreisenden, verdrehungsfreien Bewegung gelagert und geführt ist, - bei welcher die spiralartigen Förderräume (4) und Verdränger (13) aus jeweils zwei Abschnitten bestehen, wobei sich an das auslasseitige Ende eines ersten, weniger als 360° umspannenden Abschnittes (40', 130') stetig ein zweiter Abschnitt (40", 130") anschliesst, dessen Krümmungsradius wesentlich kleiner ist als der kleinste Krümmungsradius des ersten Abschnittes, so dass der zweite Abschnitt zwischen dem auslasseitigen Ende und dem Zentrum (14, 15) des ersten Abschnittes (40', 130') liegt, dadurch gekennzeichnet, - dass die mindestens zwei spiralartigen Förderräume (4), ohne einen gemeinsamen Pol aufzuweisen, zentralsymmetrisch zueinander angeordnet sind, - dass die einlasseitigen Enden der Förderräume (4) um die Antriebslagerung (19, 20, 21, 22) des Läufers (11) herum angeordnet sind. 1. Rotary piston displacement machine for compressible media - With at least two conveying spaces (4) which run in a fixed manner (1, 2) in a spiral manner and span more than 360 ° and each lead from an inlet (5) to an outlet (6), - With an associated and each engaging in this, also spiral-like and more than 360 ° spanning displacer (13), which is arranged as a band-shaped bar on a disc-shaped rotor (11) driven eccentrically with respect to the housing, and with respect to the Conveying spaces (4) are mounted and guided for executing a circular, rotation-free movement, - in which the spiral-like conveying spaces (4) and displacers (13) each consist of two sections, a second section (40 ', 130') continuously extending at the outlet end of a first section (40 ', 130') spanning less than 360 °, 130 "), whose radius of curvature is significantly smaller than the smallest radius of curvature of the first section, so that the second section lies between the outlet-side end and the center (14, 15) of the first section (40 ', 130'), characterized in that that the at least two spiral conveying spaces (4) are arranged centrally symmetrically to one another without having a common pole, - That the inlet-side ends of the delivery spaces (4) are arranged around the drive bearing (19, 20, 21, 22) of the rotor (11). 2. Maschine nach Anspruch 1, dadurch gekennzeichnet, dass die Antriebsachse (25) mit dem Symmetriezentrum der Förderräume (4) und die exzentrisch versetzte Mittelachse (26) des Läufers (11) mit dem Symmetriezentrum der Verdränger (13) zusammenfallen.2. Machine according to claim 1, characterized in that the drive axis (25) with the center of symmetry of the conveying spaces (4) and the eccentrically offset central axis (26) of the rotor (11) coincide with the center of symmetry of the displacer (13). 3. Maschine nach Anspruch 1, dadurch gekennzeichiet, dass das Gehäuse (1, 2) mit vorzugsweise über den ganzen Umfang angeordneten Kühlrippen (27) versehen ist.3. Machine according to claim 1, characterized in that the housing (1, 2) is preferably provided with cooling fins (27) arranged over the entire circumference. 4. Verdrängungsmaschine, bei welcher der Läufer (11) beidseitig mit Verdrängern (13) ausgerüstet ist nach Anspruch 1, dadurch gekennzeichnet, dass der,Läufer (11) sowohl eintrittsseitig als auch austrittsseitig mit Durchbrüchen (28) versehen ist.4. Displacement machine in which the rotor (11) is equipped on both sides with displacers (13) according to claim 1, characterized in that the rotor (11) is provided with openings (28) both on the inlet side and on the outlet side. 5. Maschine nach Anspruch 1, dadurch gekennzeictnet, dass der Läufer (11) im Gehäuse (1,2) über mehrere Rollbolzen (30) geführt ist, und dabei jeweils ein Rollbolzen (30) in eine Bohrung (31) des Läuwers sowie eine darauf abgestimmte, gleich grosse Behrung (32) des Gehäuses eingreift, wobei der Durchmesser der Rollbolzen (30) um die Exzentrizität zwischen Antriebsachse (25) und Mittelachse (26) des Beufers kleiner ist als jener der Gehäusebohrungen (32).5. Machine according to claim 1, characterized in that the rotor (11) in the housing (1, 2) is guided over a plurality of roller bolts (30), and in each case one roller bolt (30) in a bore (31) of the rotor and one matching, the same sized bore (32) of the housing engages, the diameter of the rolling pin (30) around the eccentricity between the drive axis (25) and central axis (26) of the fan being smaller than that of the housing bores (32).
EP86105671A 1985-04-26 1986-04-24 Rotary piston positive-displacement machine Expired EP0201774B1 (en)

Priority Applications (1)

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AT86105671T ATE36895T1 (en) 1985-04-26 1986-04-24 DISPLACEMENT ROTARY PISTON MACHINE.

Applications Claiming Priority (2)

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CH1780/85A CH667497A5 (en) 1985-04-26 1985-04-26 ROTARY PISTON DISPLACEMENT MACHINE.
CH1780/85 1985-04-26

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JP (1) JPS61250392A (en)
AT (1) ATE36895T1 (en)
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DE (1) DE3660636D1 (en)

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DE3744866C2 (en) * 1987-08-12 1990-04-26 Dancho Zochev Dipl.-Ing. 1000 Berlin De Donkov Rotary piston compressor with radial channels
EP0545190A1 (en) * 1991-12-05 1993-06-09 AGINFOR AG für industrielle Forschung Scroll-type fluid displacement machine
EP0579888A1 (en) * 1992-07-20 1994-01-26 AGINFOR AG für industrielle Forschung Rotating scroll pump
DE19500774A1 (en) * 1995-01-13 1996-07-18 Adolf Dr Ing Hupe Rotary piston engine
EP2402611A3 (en) * 2010-07-02 2013-06-26 Handtmann Systemtechnik GmbH & Co. KG Loading device for compacting charge air for a combustion engine
US8529233B2 (en) 2007-07-26 2013-09-10 Spinnler Engineering Displacement machine with improved support
EP4323649A4 (en) * 2021-05-05 2024-08-14 Gazi Univ Spiral vane scroll compressor

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US5171140A (en) * 1990-10-19 1992-12-15 Volkswagen Ag Spiral displacement machine with angularly offset spiral vanes
DE4215038A1 (en) * 1992-05-07 1993-11-11 Bitzer Kuehlmaschinenbau Gmbh Spiral compressor for compressible media - has sets of compression chambers formed by spiral grooves enclosing spiral ribs and eccentrically displaced
US5616015A (en) * 1995-06-07 1997-04-01 Varian Associates, Inc. High displacement rate, scroll-type, fluid handling apparatus
ATE229612T1 (en) * 1997-08-26 2002-12-15 Crt Common Rail Tech Ag SPIRAL DISPLACEMENT MACHINE FOR COMPRESSIBLE MEDIA
WO2000049275A1 (en) * 1999-02-18 2000-08-24 Fritz Spinnler Displacement machine based on the spiral principle
US20150260091A1 (en) * 2014-03-14 2015-09-17 Chung-Shan Institute Of Science And Technology, Armaments Bureau, M.N.D External cooling fin for rotary engine
US20160305315A1 (en) * 2014-03-14 2016-10-20 National Chung_Shan Institute Of Science And Technology External cooling fin for rotary engine

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EP0545190A1 (en) * 1991-12-05 1993-06-09 AGINFOR AG für industrielle Forschung Scroll-type fluid displacement machine
EP0579888A1 (en) * 1992-07-20 1994-01-26 AGINFOR AG für industrielle Forschung Rotating scroll pump
DE19500774A1 (en) * 1995-01-13 1996-07-18 Adolf Dr Ing Hupe Rotary piston engine
US8529233B2 (en) 2007-07-26 2013-09-10 Spinnler Engineering Displacement machine with improved support
EP2179138B1 (en) * 2007-07-26 2015-09-09 Spinnler Engineering Displacement machine according to the spiral principle
EP2402611A3 (en) * 2010-07-02 2013-06-26 Handtmann Systemtechnik GmbH & Co. KG Loading device for compacting charge air for a combustion engine
EP4323649A4 (en) * 2021-05-05 2024-08-14 Gazi Univ Spiral vane scroll compressor

Also Published As

Publication number Publication date
EP0201774B1 (en) 1988-08-31
JPS61250392A (en) 1986-11-07
CH667497A5 (en) 1988-10-14
US4715797A (en) 1987-12-29
DE3660636D1 (en) 1988-10-06
ATE36895T1 (en) 1988-09-15

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