EP0842363B1 - Spiral compressor, useful in particular to generate compressed air for rail vehicles - Google Patents

Spiral compressor, useful in particular to generate compressed air for rail vehicles Download PDF

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Publication number
EP0842363B1
EP0842363B1 EP96925640A EP96925640A EP0842363B1 EP 0842363 B1 EP0842363 B1 EP 0842363B1 EP 96925640 A EP96925640 A EP 96925640A EP 96925640 A EP96925640 A EP 96925640A EP 0842363 B1 EP0842363 B1 EP 0842363B1
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EP
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Prior art keywords
spiral
pressure
pressure chambers
oil
spirals
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EP96925640A
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German (de)
French (fr)
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EP0842363A2 (en
Inventor
Christian Holzapfel
Wilfried ZÖRNER
Robert Frank
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Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
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Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
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Priority claimed from DE19604447A external-priority patent/DE19604447C2/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
    • 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

  • the invention relates to a scroll compressor according to the preamble of the claim 1.
  • EP 0 482 209 A1 shows a generic scroll compressor.
  • the scroll compressor is equipped with two spirals that run into one another, which are each supported by a bearing and their for the compression effect required relative movement to each other by mutual displacement of their axes of rotation is generated, with the purpose of compensating for that of the spirals on the Bearings exerted axial forces on the inside of a connected to the first spiral Pressure ring pressure chambers are provided, which under the pressure of the Compressed air fed by the scroll compressor press the two scrolls towards each other.
  • Oil-free scroll compressors are increasingly used in the field of rail vehicles increased attention, especially to the accumulation of oily condensate avoid and to simplify maintenance. Due to the compared to today's commercial, Oil-free scroll compressors in rail vehicle use can be greatly enlarged Performance (e.g. intake volume flow of approx. 1,600 l / min) and the associated high A simple enlargement of such compressors is not a burden on the scroll compressor possible, especially in view of the very high axial forces. which the inclination have to push apart the spirals of the compressor. With so-called one-sided Spiral arrangement is particularly problematic in supporting such axial forces because very large bearings are required. This problem is exacerbated by the required Oil-free compression, which makes the friction of the bearings very difficult to remove is. Compressors with a spiral arrangement at the end have hitherto been derived from the aforementioned Considered reasons in the rail vehicle area as not usable.
  • the object of the invention is preferably one completely oil-free scroll compressor with one-sided scroll arrangement large intake volume flow as well as with large compression ratios to design that account for the aforementioned problems of high axial forces will be carried; in particular, despite the required volume and Compression quantities are free of high axial forces and therefore as possible wear-free running of the compressor be made possible.
  • Scroll compressor 1 shown, which an inventive arrangement for Compensation for the high ones that act on the bearings of the compressor Has axial forces.
  • the scroll compressor 1 is provided with a housing 3, in which two interlocking spirals run, namely one by means of a shaft 5 driven spiral 7 and a spiral dragged by the spiral 7 9. Die both spirals perform a pure rotational movement; through the purely rotational movements of the spirals do not occur unbalance forces, provided that Spirals are balanced in each case.
  • a device for Axial force compensation provided.
  • This device consists of pressure chambers 35, which is between the inside of the print collar 5 and one on the back the spiral 9 attached washer 37 are provided.
  • the pressure chambers 35 are very low volumes, each between the washer 37 and the facing inner surface of the pressure ring 15 exist.
  • the size and the The shape of the pressure chambers is determined by dry-running seals 39, which the pressure chambers in relation to outside air i.e.
  • the scroll compressor When the scroll compressor is operating, it builds up as a result of that described above Pressure supply of the pressure chambers 35 in this a pressure on which the two Presses spirals facing each other, since the pressure ring 15 with the spiral 7th is connected and the washer 37 in the rear region of the spiral 9 from this is worn, e.g. by radial cooling fins 47 connected to the spiral 9 or by the journals of the support rollers 17, which are at an angular distance enforce each other the washer 37, as in the upper half of the cut Drawing can be seen.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Description

Die Erfindung betrifft einen Spiralverdichter nach dem Gattungsbegriff des Patentanspruchs 1.The invention relates to a scroll compressor according to the preamble of the claim 1.

Bei der Drucklufterzeugung, insbesondere bei der ölfreien Drucklufterzeugung in Schienenfahrzeugen, sind infolge der großen, zu erzeugenden Luftmengen und der extrem rauen Bedingungen besondere Anforderungen an die Verdichtertechnik zu stellen. Selbst unter rauen Umgebungsbedingungen (Temperatur, Schwingungen, Stöße, etc.) ist stets volle Betriebsfähigkeit zu gewährleisten.In compressed air generation, especially in oil-free compressed air generation in rail vehicles, are due to the large amounts of air to be generated and the extremely harsh conditions to make special demands on the compressor technology. Even under rough Ambient conditions (temperature, vibrations, shocks, etc.) are always fully operational to ensure.

Aus der EP 0 482 209 A1 geht ein gattungsgemäßer Spiralverdichter hervor. Der Spiralverdichter ist mit zwei in einem Gehäuse angeordneten, ineinanderlaufenden Spiralen ausgestattet, welche je von einem Lager getragen sind und deren für die Verdichtungswirkung erforderliche Relativbewegung zueinander durch eine gegenseitige Versetzung ihrer Rotationsachsen erzeugt wird, wobei zum Zwecke der Kompensation der von den Spiralen auf die Lager ausgeübten Axialkräfte an der Innenseite eines mit der ersten Spirale verbundenen Druckkranzes Druckkammern vorgesehen sind, welche unter Druckeinwirkung der vom Spiralverdichter eingespeisten Druckluft die beiden Spiralen einander zugewandt drücken. EP 0 482 209 A1 shows a generic scroll compressor. The scroll compressor is equipped with two spirals that run into one another, which are each supported by a bearing and their for the compression effect required relative movement to each other by mutual displacement of their axes of rotation is generated, with the purpose of compensating for that of the spirals on the Bearings exerted axial forces on the inside of a connected to the first spiral Pressure ring pressure chambers are provided, which under the pressure of the Compressed air fed by the scroll compressor press the two scrolls towards each other.

In zunehmendem Maße wird im Bereich der Schienenfahrzeuge ölfreien Spiralverdichtern erhöhte Aufmerksamkeit gewidmet, insbesondere um den Anfall ölhaltigen Kondensats zu vermeiden und um die Wartung zu vereinfachen. Aufgrund der gegenüber heutigen handelsüblichen, ölfreien Spiralverdichtern im Schienenfahrzeugeinsatz stark zu vergrößernden Leistung (z. B. Ansaugvolumenstrom von ca. 1.600 l/min) und der damit verbundenen hohen Belastungen des Spiralverdichters ist eine einfache Vergrößerung derartiger Verdichter nicht möglich, insbesondere im Hinblick auf die sehr hohen Axialkräfte. welche die Neigung besitzen, die Spiralen des Verdichters auseinanderzudrücken. Bei sogenannter einseitiger Spiralanordnung ist insbesondere die Abstützung derartiger Axialkräfte problematisch, da sehr große Lager erforderlich sind. Verschärft wird diese Problematik durch die geforderte ölfreie Verdichtung, aufgrund welcher die Reibleistung der Lager nur sehr schwer abführbar ist. Verdichter mit endseitiger Spiralanordnung wurden bis dato aus den vorgenannten Gründen im Schienenfahrzeugbereich als nicht einsetzbar angesehen. Oil-free scroll compressors are increasingly used in the field of rail vehicles increased attention, especially to the accumulation of oily condensate avoid and to simplify maintenance. Due to the compared to today's commercial, Oil-free scroll compressors in rail vehicle use can be greatly enlarged Performance (e.g. intake volume flow of approx. 1,600 l / min) and the associated high A simple enlargement of such compressors is not a burden on the scroll compressor possible, especially in view of the very high axial forces. which the inclination have to push apart the spirals of the compressor. With so-called one-sided Spiral arrangement is particularly problematic in supporting such axial forces because very large bearings are required. This problem is exacerbated by the required Oil-free compression, which makes the friction of the bearings very difficult to remove is. Compressors with a spiral arrangement at the end have hitherto been derived from the aforementioned Considered reasons in the rail vehicle area as not usable.

Davon ausgehend besteht die Aufgabe der Erfindung darin, einen vorzugsweise vollständig ölfrei arbeitenden Spiralverdichter mit einseitiger Spiralanordnung bei großem Ansaugvolumenstrom als auch bei großen Verdichtungsverhältnissen so auszugestalten, daß den vorgenannten Problemen hoher Axialkräfte Rechnung getragen wird; im besonderen soll trotz der geforderten Volumen- und Verdichtungsgrößen ein von hohen Axialkräften freier und somit möglichst verschleißfreier Lauf des Verdichters ermöglicht sein.Based on this, the object of the invention is preferably one completely oil-free scroll compressor with one-sided scroll arrangement large intake volume flow as well as with large compression ratios to design that account for the aforementioned problems of high axial forces will be carried; in particular, despite the required volume and Compression quantities are free of high axial forces and therefore as possible wear-free running of the compressor be made possible.

Zur Lösung dieser Aufgabe dienen die Merkmale nach dem Kennzeichnungsteil des Patentanspruches 1.To solve this problem, the features according to the labeling part of the Claim 1.

Bei einseitiger Anordnung der Spiralen, nämlich der antreibenden und der geschleppten Spirale, ist durch die von den Verdichtungstaschen des Spiralverdichters gespeisten Druckkammern in sehr einfacher Weise eine Vorrichtung geschaffen, mittels welcher den sehr hohen, auf die Lager wirkenden Axialkräften entgegengewirkt werden kann; es ist mithin eine Kompensation dieser Axialkräfte erzielbar. Trotz der hohen Umlaufgeschwindigkeiten der beiden Spiralen ist die Funktion der Druckkammern bei insbesondere Trockenlaufeigenschaften der die Druckkammern begrenzenden Dichtungen sichergestellt, da nur eine geringe Relativgeschwindigkeit zwischen den Spiralen, also auch im Bereich des Druckkranzes und der mit dem Druckkranz die Druckkammern bildenden Ringscheibe besteht.With one-sided arrangement of the spirals, namely the driving and the dragged spiral, is by the of the compression pockets of the Spiral compressor fed pressure chambers in a very simple manner Device created by means of which the very high, acting on the bearings Axial forces can be counteracted; it is therefore a compensation for this Axial forces can be achieved. Despite the high circulation speeds of the two spirals is the function of the pressure chambers with dry running properties in particular seals that limit the pressure chambers, since only a small one Relative speed between the spirals, i.e. also in the range of Pressure wreath and the pressure chambers forming the pressure wreath There is an annular disc.

Vorteilhafte Ausgestaltungen und Weiterbildungen sind in weiteren Patentansprüchen aufgeführt.Advantageous refinements and developments are in others Claims listed.

Die Erfindung ist nachfolgend anhand eines Ausführungsbeispiels unter Bezugnahme auf die beigefügte einzige Zeichnung erläutert. Diese zeigt in Schnittansicht den Spiralverdichter nach der Erfindung.The invention is described below using an exemplary embodiment Explained with reference to the accompanying single drawing. This shows in Sectional view of the scroll compressor according to the invention.

In der Zeichnung ist ein mit einer einseitigen Spiralanordnung versehener Spiralverdichter 1 dargestellt, welcher eine erfindungsgemäße Anordnung zur Kompensation der hohen, gegenüber den Lagern des Verdichters wirkenden Axialkräfte aufweist. Der Spiralverdichter 1 ist mit einem Gehäuse 3 versehen, in welchem zwei ineinandergreifende Spiralen laufen, nämlich eine mittels einer Welle 5 angetriebene Spirale 7 und eine durch die Spirale 7 geschleppte Spirale 9. Die beiden Spiralen führen jeweils eine reine Rotationsbewegung aus; durch die rein rotatorische Bewegung der Spiralen treten keine Unwuchtkräfte auf, sofern die Spiralen jeweils in sich ausgewuchtet sind.In the drawing is a one-sided spiral arrangement Scroll compressor 1 shown, which an inventive arrangement for Compensation for the high ones that act on the bearings of the compressor Has axial forces. The scroll compressor 1 is provided with a housing 3, in which two interlocking spirals run, namely one by means of a shaft 5 driven spiral 7 and a spiral dragged by the spiral 7 9. Die both spirals perform a pure rotational movement; through the purely rotational movements of the spirals do not occur unbalance forces, provided that Spirals are balanced in each case.

Die für eine Verdichtungswirkung erforderliche Relativbewegung beider Spiralen zueinander wird erzeugt, indem die Rotationsachsen 11 und 13 beider Spiralen einen gewissen Abstand zueinander aufweisen. Fernerhin ist die geschleppte Spirale 9 von einem Druckkranz 15 umgriffen, welcher mit der angetriebenen Spirale 7 (über nicht dargestellte Befestigungsmittel) fest verschraubt oder auf sonstige Weise verbunden ist. Um die Funktion des sogenannten "co-rotating"-Prinzips beider Spiralen zu gewährleisten, d.h. um jederzeit die korrekte Relativstellung der beiden Spiralen zueinander sicherzustellen, wirkt zwischen den beiden Spiralen ein "Antirotationsmechanismus" in Form einer Zwangsführung, welche z.B. aus drei von der geschleppten Spirale 9 getragenen Stützrollen 17 besteht, die in unter gleichem Winkelabstand zueinander angeordneten Bohrungen 19 im Druckkranz 15 laufen. Demnach sind drei unter einem Winkelabstand von jeweils 120° zueinander angeordneten Stützrollen drei unter gleichem Winkelabstand zueinander angeordnete Bohrungen 19 zugeordnet. Da sich der Druckkranz 15 mit der angetriebenen Spirale 7 dreht, nimmt dieser mittels der Wandungen der Bohrungen und die Stützrollen 17 die Spirale 9 mit, d.h. diese wird geschleppt, wobei die beiden Spiralen infolge der Versetzung der Rotationsachsen 11 und 13 innerhalb des Freiheitsgrades der Bohrungen "orbitierende" Bewegungen zueinander ausführen. Diese orbitierenden Bewegungen der Spiralen zueinander erzeugen zwischen diesen im Volumen sich verändernde Spiraltaschen, welche zur Verdichtung des über den Ansaugkanal 21 angesaugten Gas- bzw. Luftvolumens beitragen. Die verdichtete Luft wird durch eine im Zentrum der Spirale 9 liegende Axialbohrung 23 und einen Druckstutzen 25 aus dem Verdichtungsraum 27 ausgeschoben. Die angetriebene Welle 5 der Spirale 7 läuft in einem Lager 29, während die Welle 31 der geschleppten Spirale 9 in einem Lager 33 läuft. The relative movement of both spirals required for a compression effect to each other is generated by the axes of rotation 11 and 13 of both spirals have a certain distance from each other. Furthermore, the dragged spiral 9 encompassed by a pressure ring 15 which is connected to the driven spiral 7 (via Fasteners not shown) screwed tightly or in any other way connected is. To the function of the so-called "co-rotating" principle of both To ensure spirals, i.e. to ensure the correct relative position of the two at all times Ensuring spirals to each other acts between the two spirals "Anti-rotation mechanism" in the form of a forced operation, which e.g. out of three of the dragged spiral 9 carried support rollers 17, which in the same Bores 19 arranged at an angular distance from one another run in the pressure ring 15. Accordingly, three are at an angular distance of 120 ° to each other arranged support rollers three at the same angular distance from each other arranged holes 19 assigned. Since the pressure ring 15 with the driven spiral 7 rotates, this takes place by means of the walls of the holes and the support rollers 17 with the spiral 9, i.e. this is towed, the two Spirals due to the displacement of the axes of rotation 11 and 13 within the Execute degrees of freedom of the holes "orbiting" movements to each other. These orbiting movements of the spirals to each other generate between this spiral pockets changing in volume, which to compress the Contribute gas or air volume sucked in via the intake duct 21. The compressed air is through an axial bore 23 located in the center of the spiral 9 and a pressure port 25 is pushed out of the compression chamber 27. The driven shaft 5 of the spiral 7 runs in a bearing 29, while the shaft 31 the dragged spiral 9 runs in a bearing 33.

Bei einem Spiralverdichter der vorstehend beschriebenen einseitigen Spiralenanordnung ist es bei komplett ölfreiem Lauf erwünscht, ein großes Verdichtungsverhältnis zu erreichen, ohne daß es infolge der daraus resultierenden Axialkräfte an den Spiralen zu einer zu starken Belastung der Lager kommt. Um diesem Problem zu begegnen, ist gemäß der Erfindung eine Vorrichtung zur Axialkraftkompensation vorgesehen. Diese Vorrichtung besteht aus Druckkammern 35, welche zwischen der Innenseite des Druckkranzes 5 und einer auf der Rückseite der Spirale 9 angebrachten Ringscheibe 37 vorgesehen sind. Im dargestellten Ausführungsbeispiel handelt es sich bei den Druckkammern 35 um die sehr niedrigen Volumina, welche jeweils zwischen der Ringscheibe 37 und der zugewandten Innenfläche des Druckkranzes 15 bestehen. Die Größe und die Formgebung der Druckkammern ist durch trockenlaufende Dichtungen 39 bestimmt, welche die Druckkammern gegenüber Außenluft d.h. gegenüber dem Außenluftvolumen zwischen Kühllufteintritt 40 und Kühlluftaustritt 41 der Spirale 9 abdichten. Im dargestellten Ausführungsbeispiel sind unter gleichem Winkelabstand von 120° zueinander jeweils zwischen den Bohrungen 19 befindlich drei Druckkammern 35 vorgesehen, welche jeweils über Bohrungen 43 mit Druckluft aus den Verdichtungstaschen 45 der Spiralen versorgt werden.In the case of a scroll compressor of the one-sided type described above Spiral arrangement is desirable with a completely oil-free run, a large one To achieve compression ratio without resulting from it Axial forces on the spirals lead to excessive load on the bearings. Around To solve this problem, according to the invention, is a device for Axial force compensation provided. This device consists of pressure chambers 35, which is between the inside of the print collar 5 and one on the back the spiral 9 attached washer 37 are provided. In the illustrated Embodiment, the pressure chambers 35 are very low volumes, each between the washer 37 and the facing inner surface of the pressure ring 15 exist. The size and the The shape of the pressure chambers is determined by dry-running seals 39, which the pressure chambers in relation to outside air i.e. compared to the Outside air volume between cooling air inlet 40 and cooling air outlet 41 of the spiral 9 caulk. In the illustrated embodiment are at the same angular distance of 120 ° to each other between the bores 19 three Pressure chambers 35 are provided, each of which has holes 43 with compressed air the compression pockets 45 of the spirals are supplied.

Bei Betrieb des Spiralverdichters baut sich infolge der vorstehend beschriebenen Druckversorgung der Druckkammern 35 in diesen ein Druck auf, welcher die beiden Spiralen einander zugewandt drückt, da der Druckkranz 15 mit der Spirale 7 verbunden ist und die Ringscheibe 37 im rückwärtigen Bereich der Spirale 9 von dieser getragen wird, z.B. durch mit der Spirale 9 verbundene, radiale Kühlrippen 47 bzw. durch die Lagerzapfen der Stützrollen 17, welche unter Winkelabstand zueinander die Ringscheibe 37 durchsetzen, wie in der oberen Schnitthälfte der Zeichnung ersichtlich ist. Da die Spiralen 7 und 9 mittels der vorstehend beschriebenen Vorrichtung zur Axialkraftkompensation aufeinander zugewandt gedrückt werden, werden die Lager 29 und 33 in gleichem Maße von Axialkräften entlastet, weshalb ölfrei arbeitende Spiralverdichter der beschriebenen Art auch mit großem Verdichtungsverhältnis bei großem Ansaugvolumen arbeiten können. When the scroll compressor is operating, it builds up as a result of that described above Pressure supply of the pressure chambers 35 in this a pressure on which the two Presses spirals facing each other, since the pressure ring 15 with the spiral 7th is connected and the washer 37 in the rear region of the spiral 9 from this is worn, e.g. by radial cooling fins 47 connected to the spiral 9 or by the journals of the support rollers 17, which are at an angular distance enforce each other the washer 37, as in the upper half of the cut Drawing can be seen. Since the spirals 7 and 9 by means of the above described device for axial force compensation facing each other are pressed, the bearings 29 and 33 to the same extent by axial forces relieves, which is why oil-free scroll compressors of the type described also large compression ratio can work with large intake volume.

Außer der vorgenannten Kühlluftanordnung für die Spirale 9 ist auch an der Spirale 7 ein entsprechendes Kühlsystem vorgesehen, d.h. es besteht ein Kühllufteintritt 49 und ein Kühlluftaustritt 51; desweiteren sind mit der Spirale 7 verbundene, radiale Kühlrippen 53 vorgesehen. In addition to the aforementioned cooling air arrangement for the spiral 9, there is also a spiral 7 an appropriate cooling system is provided, i.e. there is a cooling air inlet 49 and a cooling air outlet 51; furthermore, are connected to the spiral 7, radial Cooling fins 53 are provided.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Spiralverdichterscroll compressor
33
Gehäusecasing
55
Wellewave
77
Spiralespiral
99
Spiralespiral
1111
Rotationsachseaxis of rotation
1313
Rotationsachseaxis of rotation
1515
Druckkranzpressure ring
1717
Stützrollesupporting role
1919
Bohrungdrilling
2121
Ansaugkanalintake port
2323
Axialbohrungaxial bore
2525
Druckstutzenpressure port
2727
Verdichtungsraumcompression chamber
2929
Lagercamp
3131
Wellewave
3333
Lagercamp
3535
Druckkammerpressure chamber
3737
Ringscheibewasher
3939
Dichtungpoetry
4040
KühllufteintrittCooling air inlet
4141
KühlluftaustrittCooling air outlet
4343
Bohrungdrilling
4545
Verdichtungstaschecompression bag
4747
Kühlrippencooling fins
4949
KühllufteintrittCooling air inlet
5151
KühlluftaustrittCooling air outlet
5353
Kühlrippencooling fins

Claims (7)

  1. Spiral compressor operating without oil, particularly for the generation of compressed air for rail vehicles, comprising at least two spirals (7, 9) disposed in a housing (3) and engaging into each other, whereof each is supported by a bearing (29, 33) and whose movement relative to each other, which is necessary for the compressing effect, is induced by a mutual displacement of their axes of rotation (11, 13), with pressure chambers (35) being provided on the inner side of a pressure rim (15) that is connected with the first one (7) of said intermeshing spirals for the purpose of compensating the axial forces created by said spirals (7, 9) on said bearings (29, 33), which pressure chambers (35) produce a pressure while facing each other under the effect of the pressure created by the compressed air supplied by the spiral compressor, characterised by the following features:
    (a) said pressure chambers (35) are formed between the inner side of said pressure rim (15) and an annular disk (38) bearing against the latter;
    (b) on its side turned away from said pressure chambers (35), said annular disk (37) is supported on radial cooling fins (47) connected to said second spiral (9); and
    (c) said annular disk (37) overlaps said pressure chambers (35) with a sliding speed corresponding to the relative speed between said two spirals (8, 9);
    (d) said pressure chambers (35) are supplied with compressed air from compression pockets (45) of the spiral compressor via bores (43) extending through said cooling fins (47) and via apertures in said annular disk (37).
  2. Spiral compressor operating without oil according to Claim 1, characterized by the following feature:
    each of said pressure chambers (35) is limited by a respective pressure chamber seal recessed in said pressure rim (15) and having dry running properties.
  3. Spiral compressor operating without oil, according to any of the preceding Claims, characterised by three pressure chambers (35) disposed at a respective angular spacing by 120° relative to each other between the inner surface of said pressure rim (15) and the facing inner surface of said annular disk (37).
  4. Spiral compressor operating without oil, according to any of the preceding Claims, characterised in that said first spiral (7) is driven and that said second spiral (9) is dragged by said first spiral by means of forced guidance.
  5. Spiral compressor operating without oil, according to Claim 4, characterised by the following features:
    (a) supporting rollers (17) supported for rotation extend from the rear side of said second spiral (9), which faces said pressure rim (15); and
    (b) said supporting rollers (17) roll in bores machined into said pressure rim (15).
  6. Spiral compressor operating without oil, according to Claim 4 or 5, characterised by three supporting rollers (17) disposed at a respective angular spacing by 120° relative to each other on the rear side of said second spiral (9) and extending from the latter, with each of said supporting rollers rolling in said bores (19) in said pressure rim (15) connected to said first spiral (7).
  7. Spiral compressor operating without oil, according to any of the preceding Claims, characterised in that said supporting rollers (17) and said pressure chambers (35) are disposed in alternation on a pitch circle.
EP96925640A 1995-07-31 1996-07-19 Spiral compressor, useful in particular to generate compressed air for rail vehicles Expired - Lifetime EP0842363B1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19528005 1995-07-31
DE19528005 1995-07-31
DE19604447 1996-02-07
DE19604447A DE19604447C2 (en) 1995-07-31 1996-02-07 scroll compressor
PCT/DE1996/001329 WO1997005389A1 (en) 1995-07-31 1996-07-19 Spiral compressor, useful in particular to generate compressed air for rail vehicles

Publications (2)

Publication Number Publication Date
EP0842363A2 EP0842363A2 (en) 1998-05-20
EP0842363B1 true EP0842363B1 (en) 2002-12-04

Family

ID=26017293

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96925640A Expired - Lifetime EP0842363B1 (en) 1995-07-31 1996-07-19 Spiral compressor, useful in particular to generate compressed air for rail vehicles

Country Status (4)

Country Link
US (1) US6017204A (en)
EP (1) EP0842363B1 (en)
JP (1) JPH11509902A (en)
WO (1) WO1997005389A1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10065821A1 (en) 2000-12-22 2002-07-11 Bitzer Kuehlmaschinenbau Gmbh compressor
JP5373103B2 (en) 2008-11-14 2013-12-18 アルフレツド ケルヒヤー ゲーエムベーハー ウント コンパニー カーゲー High pressure washer
WO2010091698A1 (en) 2009-02-13 2010-08-19 Alfred Kärcher Gmbh & Co. Kg Motor pump unit
DE102009010461A1 (en) 2009-02-13 2010-08-19 Alfred Kärcher Gmbh & Co. Kg Motor pump unit
WO2010091699A1 (en) 2009-02-13 2010-08-19 Alfred Kärcher Gmbh & Co. Kg Motor pump unit
JP6698726B2 (en) * 2018-03-12 2020-05-27 三菱重工業株式会社 Double rotary scroll compressor

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3817664A (en) * 1972-12-11 1974-06-18 J Bennett Rotary fluid pump or motor with intermeshed spiral walls
DE3604235C2 (en) * 1986-02-11 1993-11-25 Bosch Gmbh Robert Scroll compressor
CH678969A5 (en) * 1989-04-08 1991-11-29 Aginfor Ag
JPH0788822B2 (en) * 1989-04-20 1995-09-27 株式会社日立製作所 Oil-free scroll type fluid machine
WO1991018207A1 (en) * 1990-05-11 1991-11-28 Sanyo Electric Co., Ltd. Scroll compressor
US5178526A (en) * 1991-12-17 1993-01-12 Carrier Corporation Coupling mechanism for co-orbiting scroll members
US5256042A (en) * 1992-02-20 1993-10-26 Arthur D. Little, Inc. Bearing and lubrication system for a scroll fluid device

Also Published As

Publication number Publication date
JPH11509902A (en) 1999-08-31
EP0842363A2 (en) 1998-05-20
WO1997005389A1 (en) 1997-02-13
US6017204A (en) 2000-01-25

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