EP0351690B1 - Rotary scroll compressor for compressible fluids - Google Patents

Rotary scroll compressor for compressible fluids Download PDF

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Publication number
EP0351690B1
EP0351690B1 EP89112618A EP89112618A EP0351690B1 EP 0351690 B1 EP0351690 B1 EP 0351690B1 EP 89112618 A EP89112618 A EP 89112618A EP 89112618 A EP89112618 A EP 89112618A EP 0351690 B1 EP0351690 B1 EP 0351690B1
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EP
European Patent Office
Prior art keywords
displacement
housing
disc
discs
scroll compressor
Prior art date
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Expired - Lifetime
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EP89112618A
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German (de)
French (fr)
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EP0351690A1 (en
Inventor
Frank Güttinger
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Aginfor AG
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Aginfor AG fuer industrielle Forschung
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Classifications

    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F04C28/265—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels being obtained by displacing a lateral sealing face
    • 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
    • F04C18/023—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 both members are moving
    • 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
    • F04C27/005—Axial sealings for working fluid

Definitions

  • a spiral loader with rotating displacement disks is known from DE-C-2603462, Fig. 5. It is characterized by an almost pulsation-free delivery of the gaseous working medium, which consists, for example, of air or an air-fuel mixture, and can therefore be used with advantage for charging purposes of internal combustion engines.
  • the gaseous working medium which consists, for example, of air or an air-fuel mixture
  • several, approximately sickle-shaped work spaces are enclosed along the conveying space between the spirally shaped ribs. These move from an inlet to an outlet, their volume constantly decreasing and the pressure of the working fluid being increased accordingly.
  • the delivery rate for a given delivery rate and the maximum boost pressure are determined by the drive ratio, especially since the internal pressure ratio is fixed by the selected spiral geometry.
  • the charger also conveys in those operating states in which charging is not required, for example at partial load or even at idle. This would result in a loss of performance and possibly unfavorable temperature increases if the conveyed equipment was relaxed and returned to the inlet of the loader.
  • a loader of the type mentioned is known from CH-A-501838. It is the one in FIGS. 8 and 9 shown variant around a two-speed, single-stage machine, in which the two movable displacement disks are loosely arranged on fixed eccentric axes. One of the axes is hollow in order to lead the work equipment to be conveyed out of the machine.
  • the displacement disks are provided with toothed rings on their circumference, in which a common gearwheel arranged on a drive shaft engages.
  • FIGS. 5 and 6 of this same document Another variant of this working principle is shown in FIGS. 5 and 6 of this same document.
  • one of the two discs is also connected to a central drive shaft. When this one disk is rotated, the second disk is taken along in the same direction of rotation by means of power transmission via the spiral ribs.
  • an axially movable annular disk which is firmly attached to the back of one of the disks is provided.
  • Via a pressure compensation chamber which is connected to the machine outlet and a disc spring, the ring disc presses the two displacement discs together.
  • the disadvantage of this arrangement is that the ring disk must be sealed against the housing, which can only be done on the outer circumference with a large diameter and thus high sliding speeds.
  • the invention has for its object to design a spiral charger of the type mentioned above to be switched off, i.e. to at least largely prevent the promotion of the work equipment.
  • the object is achieved in that the pressure chamber can be connected to the atmosphere via a valve.
  • a drive shaft with an exchangeable toothed belt gear is arranged outside the displacement disks, belt pulleys being connected in a rotationally fixed manner to the hubs of the displacement disks. Due to this non-centric drive type, the interior of the displacement disks remains free and the pumped medium can flow freely through a hollow stub axle.
  • the two-speed, single-stage machine is shown in approximately natural size.
  • the direction of flow of the working fluid is indicated by arrows.
  • 1 denotes the housing composed of two halves.
  • the two halves are connected to one another via fastening eyes, not shown, for receiving screw connections.
  • Axle stub 2 or 2 are in the housing halves on both sides. 3 arranged, which protrude into the interior of the housing.
  • the longitudinal axes 4 respectively. 5 of the 2 stub axles are offset from each other by the eccentricity e.
  • the rotatable displacement disks 6 and 7 are placed loosely on this axle stub.
  • the hub 9 of the right displacement disk 7 is mounted on the axle stub 3 by means of two ball bearings 11 and is axially secured.
  • the left displacement disk 6 is designed to be axially displaceable.
  • the displacement discs 6 and 7 are constructed symmetrically. They consist essentially of a flat plate 13, which run parallel to each other in the assembled state and from Ribs 14 which are held vertically on the respective plate 13. These ribs 14 run in a spiral (FIG. 2), ie they can either be classic spirals or can be composed of a plurality of circular arcs adjoining one another.
  • the ribs 14 have an arc length of one and a half turns, which the machine enters the name "one stage".
  • Each plate 13 is equipped with two such ribs 14, the ribs being offset from one another by 180 °. This leads to the designation "two-course”.
  • four parallel working spaces 15 are formed, which represent the actual conveying space. On the occasion of the operation, these working spaces open at a 1/4 turn against the outlet 16. At the outer diameter, the spirals open toward the inlet 17, from which they draw in fresh air.
  • the system is driven by a drive shaft 18 which is mounted outside the displacement disks in the housing 1 by means of ball bearings 19. On this shaft sit pulleys 20 which drive the pulleys 22 and 23 via toothed belts 21, which in turn with the hubs 8 and. 9 of the displacement disks are connected in a rotationally fixed manner.
  • a pressure chamber 26 is therefore formed between the axially displaceable displacement disk 6 and the housing wall, which is acted upon by the pressure of the working medium in the outlet 16.
  • the hollow stub shaft 2 is connected to the pressure chamber 26 via a removal tube 27.
  • the pressure in the chamber acts on an annular disc 28 which is attached to the housing 1 by means of bellows 29 in an airtight manner using suitable means.
  • the annular disk 28 slides with its hub 30 on the stub axle 2. In doing so, it displaces the inner cage of the axial bearing 12 the plates opposite each other.
  • the seal 31 is advantageously installed in a rotating manner, so that its lip seals against the standing ring disk hub on the smallest possible diameter.
  • a valve 32 is screwed into the housing wall to vent the pressure chamber 26. This can either be operated manually or it opens automatically via a motor-specific or loader-specific parameter. If the valve 32 opens, atmospheric pressure enters the pressure chamber 26 and pressure is equal on both sides of the annular disk 28. The internal pressure in the outlet 16 moves the displacement disk 6 with hub 8 / axial bearing 12 / annular disk 28 functional unit to the left. Since the sealing strips 25 are as a rule firmly inserted in the grooves of the end faces 24 (and are not spring-supported), the axial sealing effect is canceled at the slightest displacement, which interrupts the pressure build-up within the spirals and the conveying process.

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

Description

Die Erfindung betrifft einen rotierenden Spirallader für kompressible Medien, im wesentlichen bestehend aus einem Gehäuse, in dem zwei symmetrisch aufgebaute Verdrängerscheiben mittels Antriebselementen drehbar angeordnet sind,

  • ― wozu die Verdrängerscheiben lose auf im Gehäuse angeordneten Achsstummeln aufgezogen sind, deren Längsachsen gegeneinander versetzt sind,
  • ― bei welchem Lader die beiden Verdrängerscheiben jeweils an einer Seite mit spiralförmig verlaufenden Rippen versehen sind, welche zwecks Bildung eines Förderraumes ineinandergreifen und mit ihren freien Stirnseiten gegen die gegenüberliegende Verdrängerscheibe dichten,
  • ― und bei dem zwecks Aufrechterhaltung der Dichtwirkung eine Druckkammer vorgesehen ist, die mit dem Auslass des Laders kommuniziert und über die eine axial verschiebbare Ringscheibe beaufschlagbar ist, welche in Wirkverbindung mit einer ebenfalls axial verschiebbaren Verdrängerscheibe steht.
The invention relates to a rotating spiral loader for compressible media, consisting essentially of a housing in which two symmetrically constructed displacement disks are rotatably arranged by means of drive elements.
  • - for which purpose the displacement disks are loosely mounted on stub axles arranged in the housing, the longitudinal axes of which are offset from one another,
  • In which loader the two displacement disks are each provided on one side with spirally extending ribs which interlock to form a conveying space and which seal with their free end faces against the opposite displacement disk,
  • - And in order to maintain the sealing effect, a pressure chamber is provided which communicates with the outlet of the charger and via which an axially displaceable annular disc can be acted upon, which is in operative connection with an likewise axially displaceable displacement disc.

Ein Spirallader mit rotierenden Verdrängerscheiben ist aus der DE-C-2603462, Fig. 5 bekannt. Er zeichnet sich durch eine nahezu pulsationsfreie Förderung des beispielsweise aus Luft oder einem Luft-Kraftstoff-Gemisch bestehenden gasförmigen Arbeitsmittels aus und kann daher mit Vorteil für Aufladezwecke von Brennkraftmaschinen verwendet werden. Während des Betriebes eines solchen Verdichters werden entlang des Förderrraumes zwischen den spiralförmig ausgebildeten Rippen mehrere, etwa sichelförmige Arbeitsräume eingeschlossen. Diese bewegen sich von einem Einlass hindurch zu einem Auslass, wobei sich ihr Volumen ständig verringert und der Druck des Arbeitsmittels dementsprechend erhöht wird. Bei diesen Spiralladern ist die Fördermenge bei gegebenem Liefergrad sowie der maximale Ladedruck durch die Antriebsübersetzung festgelegt, zumal das innere Druckverhältnis durch die gewählte Spiralgeometrie fest vorgegeben ist. Wenn eine starre Antriebsverbindung zwischen dem Spiralverdichter und der antreibenden Brennkraftmaschine vorgesehen ist, fördert also der Lader auch noch in solchen Betriebszuständen, in denen eine Aufladung nicht erforderlich ist, beispielsweise bei Teillast oder sogar im Leerlauf. Es würden somit Leistungsverluste entstehen und möglicherweise ungünstige Temperaturerhöhungen, wenn das geförderte Arbeitsmittel entspannt und wieder in den Einlass des Laders zurückgeführt würde.A spiral loader with rotating displacement disks is known from DE-C-2603462, Fig. 5. It is characterized by an almost pulsation-free delivery of the gaseous working medium, which consists, for example, of air or an air-fuel mixture, and can therefore be used with advantage for charging purposes of internal combustion engines. During the operation of such a compressor, several, approximately sickle-shaped work spaces are enclosed along the conveying space between the spirally shaped ribs. These move from an inlet to an outlet, their volume constantly decreasing and the pressure of the working fluid being increased accordingly. With these spiral loaders, the delivery rate for a given delivery rate and the maximum boost pressure are determined by the drive ratio, especially since the internal pressure ratio is fixed by the selected spiral geometry. If a rigid drive connection is provided between the scroll compressor and the driving internal combustion engine, the charger also conveys in those operating states in which charging is not required, for example at partial load or even at idle. This would result in a loss of performance and possibly unfavorable temperature increases if the conveyed equipment was relaxed and returned to the inlet of the loader.

Im Gegensatz zum eingangs erwähnten Lader ist bei dieser bekannten Maschine nur eine Verdrängerscheibe auf einem Achsstummel gelagert. Die zweite Scheibe ist drehfest mit einer Antriebswelle verbunden. Anlässlich der Drehung der zweiten Scheibe wird die erste Scheibe im gleichen Drehsinn und mit der gleichen Drehgeschwindigkeit mitgenommen. Beide Scheiben führen dabei eine Relativbewegung in Form einer Kreisverschiebung aus.In contrast to the loader mentioned at the outset, in this known machine only one displacement disk is mounted on one stub axle. The second disc is non-rotatably connected to a drive shaft. On the occasion of the rotation of the second disc, the first disc is taken along in the same direction and at the same rotational speed. Both disks perform a relative movement in the form of a circular displacement.

Ein Lader der eingangs genannten Art ist bekannt aus der CH-A-501838. Es handelt sich dort bei der in den Fig. 8 und 9 gezeigten Variante um eine zweigängige, einstufige Maschine, bei der die beiden beweglichen Verdrängerscheiben lose auf feststehenden exzentrischen Achsen angeordnet sind. Eine der Achsen ist hohl ausgebildet zwecks Herausführung des zu fördernden Arbeitsmittels aus der Maschine. An ihrem Umfang sind die Verdrängerscheiben mit Zahnkränzen versehen, in welche ein gemeinsames, auf einer Antriebswelle angeordnetes Zahnrad eingreift.A loader of the type mentioned is known from CH-A-501838. It is the one in FIGS. 8 and 9 shown variant around a two-speed, single-stage machine, in which the two movable displacement disks are loosely arranged on fixed eccentric axes. One of the axes is hollow in order to lead the work equipment to be conveyed out of the machine. The displacement disks are provided with toothed rings on their circumference, in which a common gearwheel arranged on a drive shaft engages.

Diese mehrgängigen Maschinen weisen den Vorteil auf, dass zum einen jede Verdrängerscheibe für sich vollkommen ausgewuchtet ist und zum andern, dass ein gleichmässigeres, nahezu pulsationsfreies Fördern möglich ist. Ausserdem ist die radiale Verschiebung der beiden Scheiben und damit die Exzentrizität zwischen den beiden Drehachsen kleiner als bei eingängigen Maschinen, was zu kleineren Gleitgeschwindigkeiten zwischen den spiralförmigen Rippen führt. Im Prinzip können deshalb mit dieser Art von Ladern höhere Drehzahlen gefahren werden.These multi-speed machines have the advantage that, on the one hand, each displacement disc is completely balanced and, on the other hand, that a more uniform, almost pulsation-free conveying is possible. In addition, the radial displacement of the two discs and thus the eccentricity between the two axes of rotation is smaller than in single-engined machines, which leads to lower sliding speeds between the spiral ribs. In principle, therefore, higher speeds can be driven with this type of loader.

Eine weitere Variante dieses Arbeitsprinzips ist in den Fig. 5 und 6 dieser gleichen Druckschrift gezeigt. Bei dieser Maschine ist ebenfalls eine der beiden Scheiben mit einer zentralen Antriebswelle verbunden. Bei Drehung dieser einen Scheibe wird mittels Kraftübertragung über die spiralförmige Rippen die zweite Scheibe im gleichen Drehsinn mitgenommen. Um den axialen Druck in den zwischen den Scheiben gebildeten Arbeitsräumen auszugleichen, ist eine an der Rückseite einer der Scheiben fest anliegende, axial bewegliche Ringscheibe vorgesehen. Ueber eine Druckausgleichkammer, welche mit dem Maschinenauslass verbunden ist und eine Scheibenfeder drückt die Ringscheibe die beiden Verdrängerscheiben zusammen. Von Nachteil ist bei dieser Anordnung, dass die Ringscheibe gegen das Gehäuse abgedichtet werden muss, was nur am äussern Umfang bei grossem Durchmesser und somit hohen Gleitgeschwindigkeiten vorgenommen werden kann. Zudem ist nicht vorgesehen, diese Druckausgleichkammer, die sich zwischen Ringscheibe und Gehäuse befindet, zu entlasten. Diese Massnahme wäre überdies zwecklos, da über die Scheibenfeder eine stetige Anpresskraft ausgeübt wird.Another variant of this working principle is shown in FIGS. 5 and 6 of this same document. In this machine, one of the two discs is also connected to a central drive shaft. When this one disk is rotated, the second disk is taken along in the same direction of rotation by means of power transmission via the spiral ribs. In order to compensate for the axial pressure in the working spaces formed between the disks, an axially movable annular disk which is firmly attached to the back of one of the disks is provided. Via a pressure compensation chamber, which is connected to the machine outlet and a disc spring, the ring disc presses the two displacement discs together. The disadvantage of this arrangement is that the ring disk must be sealed against the housing, which can only be done on the outer circumference with a large diameter and thus high sliding speeds. In addition, there is no provision to relieve this pressure compensation chamber, which is located between the washer and the housing. This measure would also be useless, since a constant contact pressure is exerted via the disc spring.

Der Erfindung liegt die Aufgabe zugrunde, einen Spirallader der eingangs genannten Art abschaltbar zu gestalten, d.h die Förderung des Arbeitsmittels zumindest weitgehend zu unterbinden.The invention has for its object to design a spiral charger of the type mentioned above to be switched off, i.e. to at least largely prevent the promotion of the work equipment.

Erfindungsgemäss wird die Aufgabe dadurch gelöst, dass die Druckkammer über ein Ventil mit der Atmosphäre verbindbar ist.According to the invention, the object is achieved in that the pressure chamber can be connected to the atmosphere via a valve.

Damit ist ein einfaches Mittel geschaffen, über eine Betriebsgrösse oder über eine Prozessgrösse die Druckkammer zu entlasten, wodurch der Axialdruck die Dichtwirkung innerhalb des Förderraumes aufhebt und der Fördervorgang zum Erliegen kommt.This creates a simple means of relieving the pressure chamber of an operating size or a process size, as a result of which the axial pressure cancels the sealing effect within the delivery space and the delivery process comes to a standstill.

Es ist besonders zweckmässig, wenn im Innenraum des Gehäuses die Ringscheibe an ihrem Aussendurchmesser mit einem Balg gegen das Gehäuse dichtet und wenn der Einlass vom Auslass durch eine Lippendichtung getrennt ist, die von der feststehenden Nabe der Ringscheibe gegen die rotierende Nabe der axial beweglichen Verdrängerscheibe wirkt. Hierbei ist von Vorteil, dass grosse Gleitgeschwindigkeiten an der radialen Dichtlippe erreichbar sind, da letztere sich auf dem kleinstmöglichen Durchmesser befindet.It is particularly expedient if the outer diameter of the annular disc seals with a bellows against the housing in the interior of the housing and if the inlet is separated from the outlet by a lip seal which acts from the fixed hub of the annular disc against the rotating hub of the axially movable displacement disc . The advantage here is that high sliding speeds can be achieved on the radial sealing lip, since the latter is located on the smallest possible diameter.

Zum Drehen beider Verdrängerscheiben ist eine Antriebswelle mit auswechselbarem Zahnriemengetriebe ausserhalb der Verdrängerscheiben angeordnet, wobei Riemenscheiben mit den Naben der Verdrängerscheiben drehfest verbunden sind. Durch diese nichtzentrische Antriebsart bleibt der Innenraum der Verdrängerscheiben frei und das geförderte Medium kann ungehindert über einen hohlen Achsstummel ausströmen.To rotate both displacement disks, a drive shaft with an exchangeable toothed belt gear is arranged outside the displacement disks, belt pulleys being connected in a rotationally fixed manner to the hubs of the displacement disks. Due to this non-centric drive type, the interior of the displacement disks remains free and the pumped medium can flow freely through a hollow stub axle.

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

Es zeigen:

  • Fig. 1 einen Längsschnitt durch einen Spirallader;
  • Fig. 2 einen Querschnitt gemäss Linie A-A in Fig. 1.
Show it:
  • 1 shows a longitudinal section through a spiral loader.
  • FIG. 2 shows a cross section along line AA in FIG. 1.

Die zweigängige, einstufige Maschine ist in etwa natürlicher Grösse dargestellt. Die Strömungsrichtung des Arbeitsmittels ist mit Pfeilen bezeichnet.The two-speed, single-stage machine is shown in approximately natural size. The direction of flow of the working fluid is indicated by arrows.

Zwecks Erläuterung der Funktionsweise des Verdichters, welche nicht Gegenstand der Erfindung ist, wird auf die bereits genannte CH-A-501838 verwiesen. Nachstehend wird nur der für das Verständnis der Erfindung 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 already mentioned CH-A-501838. Only the machine structure and process flow necessary for understanding the invention are briefly described below.

In den Figuren ist mit 1 das aus zwei Hälften zusammengesetzte Gehäuse bezeichnet. Die zwei Hälften sind über nicht dargestellte Befestigungsaugen zur Aufnahme von Verschraubungen miteinander verbunden. Beidseitig sind in den Gehäusehälften Achsstummel 2 resp. 3 angeordnet, die in das Gehäuseinnere hineinragen. Die Längsachsen 4 resp. 5 der 2 Achsstummel sind um die Exzentrizität e gegeneinander versetzt. Lose aufgesetzt auf diese Achsstummel sind die drehbaren Verdrängerscheiben 6 und 7. Die Nabe 9 der rechten Verdrängerscheibe 7 ist mittels zwei Kugellagern 11 auf dem Achsstummel 3 gelagert und axial gesichert. Die linke Verdrängerscheibe 6 ist axial verschiebbar ausgebildet. Hierzu ist ihre Nabe 8 über zwei als Traglager wirkende Nadellager 10 auf dem Achsstummel 2 lose aufgezogen. Im Bereich dieser Nadellager ist der Achsstummel 2 geschliffen, da er Lauffläche für die Nadeln bildet. Diese Konfiguration bedarf eines zusätzlichen Axiallagers 12, über das Kräfte auf die Nabe 8 übertragen werden können.In the figures, 1 denotes the housing composed of two halves. The two halves are connected to one another via fastening eyes, not shown, for receiving screw connections. Axle stub 2 or 2 are in the housing halves on both sides. 3 arranged, which protrude into the interior of the housing. The longitudinal axes 4 respectively. 5 of the 2 stub axles are offset from each other by the eccentricity e. The rotatable displacement disks 6 and 7 are placed loosely on this axle stub. The hub 9 of the right displacement disk 7 is mounted on the axle stub 3 by means of two ball bearings 11 and is axially secured. The left displacement disk 6 is designed to be axially displaceable. For this purpose, its hub 8 is loosely mounted on the stub shaft 2 via two needle bearings 10 acting as a support bearing. The stub axle 2 is ground in the area of these needle bearings since it forms a running surface for the needles. This configuration requires an additional thrust bearing 12, via which forces can be transmitted to the hub 8.

Die Verdrängerscheiben 6 und 7 sind symmetrisch aufgebaut. Sie bestehen im wesentlichen aus je einer ebenen Platte 13, die im montierten Zustand parallel zueinander verlaufen sowie aus Rippen 14, die senkrecht auf der jeweiligen Platte 13 gehalten sind. Diese Rippen 14 verlaufen spiralförmig (Fig. 2), d.h. sie können entweder klassische Spiralen sein oder aber aus mehreren aneinander anschliessenden Kreisbögen zusammengesetzt sein.The displacement discs 6 and 7 are constructed symmetrically. They consist essentially of a flat plate 13, which run parallel to each other in the assembled state and from Ribs 14 which are held vertically on the respective plate 13. These ribs 14 run in a spiral (FIG. 2), ie they can either be classic spirals or can be composed of a plurality of circular arcs adjoining one another.

Im gezeigten Fall weisen die Rippen 14 eine Bogenlänge von anderthalb Windungen auf, was der Maschine die Bezeichnung "einstufig" einträgt. Jede Platte 13 ist mit zwei solcher Rippen 14 bestückt, wobei die Rippen um 180° zueinander versetzt sind. Dies führt zur Bezeichnung "zweigängig". Bei solchen zweigängigen Maschinen sind vier parallele Arbeitsräume 15 gebildet, die den eigentlichen Förderraum darstellen. Anlässlich des Betriebes öffnen sich diese Arbeitsräume im Abstand von 1/4-Umdrehung gegen den Auslass 16. Am äusseren Durchmesser öffnen die Spiralen gegen den Einlass 17, aus dem sie Frischluft ansaugen.In the case shown, the ribs 14 have an arc length of one and a half turns, which the machine enters the name "one stage". Each plate 13 is equipped with two such ribs 14, the ribs being offset from one another by 180 °. This leads to the designation "two-course". In such two-course machines, four parallel working spaces 15 are formed, which represent the actual conveying space. On the occasion of the operation, these working spaces open at a 1/4 turn against the outlet 16. At the outer diameter, the spirals open toward the inlet 17, from which they draw in fresh air.

Der Antrieb des Systems erfolgt über eine Antriebswelle 18, die mittels Kugellagern 19 im Gehäuse 1 ausserhalb der Verdrängerscheiben gelagert ist. Auf dieser Welle sitzen Riemenscheiben 20, die über Zahnriemen 21 jeweils die Riemenscheiben 22 und 23 antreiben, welche ihrerseits mit den Naben 8 resp. 9 der Verdrängerscheiben drehfest verbunden sind.The system is driven by a drive shaft 18 which is mounted outside the displacement disks in the housing 1 by means of ball bearings 19. On this shaft sit pulleys 20 which drive the pulleys 22 and 23 via toothed belts 21, which in turn with the hubs 8 and. 9 of the displacement disks are connected in a rotationally fixed manner.

Anlässlich der Drehbewegung öffnen die Spiralen gegen den Einlass 17, aus dem sie Frischluft ansaugen. Infolge der mehrfachen, abwechselnden, gegenseitigen Annäherung der Rippen 14 ergeben sich die sichelförmigen Arbeitsräume 15, die durch die Spiralen hindurch vom Einlass 17 in Richtung Auslass 16 verschoben werden. Das derart geförderte Arbeitsmittel wird anschliessend durch den hohl ausgebildeten Achsstummel 2 aus dem Lader herausgeführt.On the occasion of the rotary movement, the spirals open against the inlet 17, from which they draw in fresh air. As a result of the multiple, alternating, mutual approach of the ribs 14, the crescent-shaped working spaces 15 result, which are displaced through the spirals from the inlet 17 towards the outlet 16. The work equipment conveyed in this way is then led out of the loader through the hollow stub shaft 2.

Es versteht sich, dass für eine ordentliche Funktionsweise nicht nur die radiale Dichtung zwischen den Rippen 14 ― d.h. das Abschliessen der Arbeitsräume 15 in Umfangsrichtung ― wichtig ist. Auch die axiale Dichtigkeit der Förderräume 15 ist von Bedeutung. Hierzu müssen die Rippen 14 mit ihren Stirnseiten 24 an der Platte 13 der gegenüberliegenden Verdrängerscheibe anliegen. Dies geschieht in der Regel durch Dichtstreifen 25, welche in entsprechenden Nuten in den Stirnseiten 24 der Rippen einliegen. Da der gegen das Spiraleninnere zunehmende Druck die Tendenz hat, die beiden Verdrängerscheiben auseinanderzudrücken, müssen Gegenmassnahmen getroffen werden.It goes without saying that not only the radial seal between the ribs 14 - that is to say the closure of the working spaces 15 in the circumferential direction - is important for proper functioning. The axial tightness of the delivery spaces 15 is also important. For this purpose, the ribs 14 with their end faces 24 rest on the plate 13 of the opposite displacement disk. This is usually done by sealing strips 25, which lie in corresponding grooves in the end faces 24 of the ribs. Since the increasing pressure against the inside of the spiral tends to push the two displacement disks apart, countermeasures must be taken.

Zwischen der axial verschiebbaren Verdrängerscheibe 6 und der Gehäusewandung wird deshalb eine Druckkammer 26 gebildet, die vom Druck des Arbeitsmittels im Auslass 16 beaufschlagt ist. Hierzu ist der hohle Achsstummel 2 über ein Entnahmerohr 27 mit der Druckkammer 26 verbunden. Der Druck in der Kammer wirkt auf eine Ringscheibe 28, die mittels Balg 29 am Gehäuse 1 mit geeigneten Mitteln luftdicht befestigt ist.A pressure chamber 26 is therefore formed between the axially displaceable displacement disk 6 and the housing wall, which is acted upon by the pressure of the working medium in the outlet 16. For this purpose, the hollow stub shaft 2 is connected to the pressure chamber 26 via a removal tube 27. The pressure in the chamber acts on an annular disc 28 which is attached to the housing 1 by means of bellows 29 in an airtight manner using suitable means.

Anlässlich einer druckbedingten axialen Verschiebung gleitet die Ringscheibe 28 mit ihrer Nabe 30 auf dem Achsstummel 2. Dabei verschiebt sie den anliegenden inneren Käfig des Axiallagers 12. Ueber die Kugeln dieses Lagers 12 wird die verschiebbare Nabe 8 der Verdrängerscheibe 6 bis zum Anschlag der Rippen 14 an den jeweils gegenüberliegenden Platten mitgenommen.On the occasion of a pressure-related axial displacement, the annular disk 28 slides with its hub 30 on the stub axle 2. In doing so, it displaces the inner cage of the axial bearing 12 the plates opposite each other.

Auf die den Verdrängerscheiben zugekehrte Rückseite der Ringscheibe 28 wirkt jener Druck, der im Einlass 17 herrscht, d.h. der Atmosphärendruck. Es ist somit zu erkennen, dass man über die blosse Dimensionierung der aktiven Ringscheibenfläche ein einfaches Mittel in der Hand hat, um die Anpresskraft der Rippen gegen die Platten zu bestimmen. Allerdings muss hierzu der Einlass vom Auslass druckmässig getrennt werden, da beide über die Lager 10 und 12 kommunizieren. Dies wird über eine Lippendichtung 31 bewerkstelligt, die zwischen der feststehenden Nabe 30 der Ringscheibe 28 und der rotierenden Nabe 8 der Verdrängerscheibe 6 wirkt. Mit Vorteil ist die Dichtung 31 rotierend eingebaut, so dass ihre Lippe auf dem kleinstmöglichen Durchmesser gegen die stehende Ringscheibennabe dichtet.The pressure prevailing in the inlet 17, ie the atmospheric pressure, acts on the rear side of the annular disk 28 facing the displacement disks. It can thus be seen that by simply dimensioning the active surface of the ring disk, one has a simple tool in hand to determine the pressing force of the ribs against the plates. However, the inlet must be separated from the outlet in terms of pressure, since both communicate via the bearings 10 and 12. This is accomplished via a lip seal 31, which acts between the fixed hub 30 of the annular disk 28 and the rotating hub 8 of the displacement disk 6. The seal 31 is advantageously installed in a rotating manner, so that its lip seals against the standing ring disk hub on the smallest possible diameter.

Zur Entlüftung der Druckkammer 26 ist in die Gehäusewandung ein Ventil 32 eingeschraubt. Dieses kann entweder manuell betätigt werden, oder aber es öffnet uns schliesst selbsttätig über eine motorspezifische oder laderspezifische Kenngrösse. Oeffnet das Ventil 32, so gelangt Atmosphärendruck in die Druckkammer 26 und auf beiden Seiten der Ringscheibe 28 herrscht Druckgleichheit. Der Innendruck im Auslass 16 verschiebt die Funktionseinheit Verdrängerscheibe 6 mit Nabe 8 / Axiallager 12 / Ringscheibe 28 nach links. Da die Dichtstreifen 25 in der Regel fest in den Nuten der Stirnseiten 24 eingelegt sind (und nicht federunterstützt sind), wird bei der geringsten Verschiebung die axiale Dichtwirkung aufgehoben, was den Druckaufbau innerhalb der Spiralen und den Fördervorgang unterbricht.A valve 32 is screwed into the housing wall to vent the pressure chamber 26. This can either be operated manually or it opens automatically via a motor-specific or loader-specific parameter. If the valve 32 opens, atmospheric pressure enters the pressure chamber 26 and pressure is equal on both sides of the annular disk 28. The internal pressure in the outlet 16 moves the displacement disk 6 with hub 8 / axial bearing 12 / annular disk 28 functional unit to the left. Since the sealing strips 25 are as a rule firmly inserted in the grooves of the end faces 24 (and are not spring-supported), the axial sealing effect is canceled at the slightest displacement, which interrupts the pressure build-up within the spirals and the conveying process.

Claims (3)

1. Rotary scroll compressor for compressible fluids, consisting essentially of a housing (1), in which two symmetrically constructed displacement discs (6, 7) are arranged rotatably by means of drive elements (18-23),
― for which purpose the displacement discs (6, 7) are drawn loosely onto axle stubs (2, 3) which are arranged in the housing and the longitudinal axes (4, 5) of which are offset relative to one another,
― in which compressor the two displacement discs are each equipped on one side with spiral ribs (14) which engage into one another to form a conveying space (15) and which with their free end faces (24) ensure sealing relative to the opposite displacement disc,
― and in which, to maintain the sealing effect, there is a pressure chamber (26) which communicates with the outlet (16) of the compressor and via which pressure can be exerted on an axially shiftable annular disc (28) connected operatively to a likewise axially shiftable displacement disc (6), characterised in that the pressure chamber (26) can be connected to the atmosphere via a valve (32).
2. Scroll compressor according to Claim 1, characterised in that, in the interior of the housing, the annular disc (28) ensures sealing on its outside diameter relative to the housing (1) by means of a bellows (29), and in that the inlet (17) is separated from the outlet (16) by a lip gasket (31) which acts from the stationary hub (30) of the annular disc (28) towards the rotating hub (8) of the axially moveable displacement disc (6).
3. Scroll compressor according to Claim 1, characterised in that, for the rotation of the two displacement discs, a drive shaft (18) with an exchangeable toothed-belt mechanism (20-23) is arranged outside the displacement discs, belt pulleys (22, 23) being connected fixedly in terms of rotation to the hubs (8, 9) to the displacement discs.
EP89112618A 1988-07-20 1989-07-11 Rotary scroll compressor for compressible fluids Expired - Lifetime EP0351690B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH2786/88 1988-07-20
CH2786/88A CH675896A5 (en) 1988-07-20 1988-07-20

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EP0351690A1 EP0351690A1 (en) 1990-01-24
EP0351690B1 true EP0351690B1 (en) 1991-09-25

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US (1) US4990072A (en)
EP (1) EP0351690B1 (en)
JP (1) JP2740274B2 (en)
CH (1) CH675896A5 (en)
DE (1) DE58900320D1 (en)

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US5741120A (en) 1995-06-07 1998-04-21 Copeland Corporation Capacity modulated scroll machine
US6106247A (en) * 1998-03-18 2000-08-22 Haldex Brake Corporation Scroll-type fluid displacement apparatus including an eccentric crank mechanism having an elongated shaft
GB2401398A (en) * 2003-05-08 2004-11-10 Automotive Motion Tech Ltd Pump with output through central bore in journal bearing
US10865793B2 (en) 2016-12-06 2020-12-15 Air Squared, Inc. Scroll type device having liquid cooling through idler shafts
JP2018119522A (en) * 2017-01-27 2018-08-02 三菱重工オートモーティブサーマルシステムズ株式会社 Scroll type compressor
US11454241B2 (en) 2018-05-04 2022-09-27 Air Squared, Inc. Liquid cooling of fixed and orbiting scroll compressor, expander or vacuum pump
US20200025199A1 (en) 2018-07-17 2020-01-23 Air Squared, Inc. Dual drive co-rotating spinning scroll compressor or expander
US11530703B2 (en) 2018-07-18 2022-12-20 Air Squared, Inc. Orbiting scroll device lubrication
US11473572B2 (en) 2019-06-25 2022-10-18 Air Squared, Inc. Aftercooler for cooling compressed working fluid
US11898557B2 (en) 2020-11-30 2024-02-13 Air Squared, Inc. Liquid cooling of a scroll type compressor with liquid supply through the crankshaft
US11885328B2 (en) 2021-07-19 2024-01-30 Air Squared, Inc. Scroll device with an integrated cooling loop

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Also Published As

Publication number Publication date
DE58900320D1 (en) 1991-10-31
JPH0267487A (en) 1990-03-07
JP2740274B2 (en) 1998-04-15
US4990072A (en) 1991-02-05
EP0351690A1 (en) 1990-01-24
CH675896A5 (en) 1990-11-15

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