EP0538637A1 - Radial-piston machine - Google Patents

Radial-piston machine Download PDF

Info

Publication number
EP0538637A1
EP0538637A1 EP92116323A EP92116323A EP0538637A1 EP 0538637 A1 EP0538637 A1 EP 0538637A1 EP 92116323 A EP92116323 A EP 92116323A EP 92116323 A EP92116323 A EP 92116323A EP 0538637 A1 EP0538637 A1 EP 0538637A1
Authority
EP
European Patent Office
Prior art keywords
bores
rotor
piston
compensating
machine
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.)
Withdrawn
Application number
EP92116323A
Other languages
German (de)
French (fr)
Inventor
Dieter Dipl.-Ing. Fetting
Dieter Ing. Bertsch (Grad.)
Michael Dr. Dr.-Ing. Gaumnitz
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0538637A1 publication Critical patent/EP0538637A1/en
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves
    • F04B1/0465—Distribution members, e.g. valves plate-like

Definitions

  • the invention is based on a radial piston machine according to the preamble of the main claim. With such machines there is the difficulty that the inevitable axial forces acting on the components of the control mirror and rotor have a lifting effect. An axial bearing counteracts these axial forces. However, due to manufacturing tolerances, component deformations and wear during operation, a gap develops between the control mirror and the rotor, through which leakages can flow. This gap constantly changes in size due to changes in load and wear.
  • the axial piston machine according to the invention with the characteristic feature has the advantage that the leaks in the above-mentioned parts are significantly reduced by a gap-closing device.
  • This measure achieved by the compensating piston is supported, inter alia, by the fact that the compensating pistons are not only loaded by a spring element, but that they are pressurized during operation, since they are on the pressure side.
  • FIG. 1 shows a longitudinal section through a radial piston machine, in FIG. 2 a detail which is not shown in detail in FIG. 1 and is designated by A.
  • 10 denotes the housing of a radial piston pump, which has a cylindrical interior 11, which is closed by a cover 12.
  • a cam ring 13 is arranged, the inside 14 of which is spherical.
  • Sliding shoes 15 rest on the inside 14, on which pistons 16 are supported, which slide in approximately radially running bores 17 of a rotor 18.
  • This is fixed in a rotationally fixed manner on a drive shaft 19 which is mounted on the one hand in a slide bearing 20 of the housing 10 and on the other hand in a slide bearing 21 of the cover 12.
  • the shaft 19 is driven via a dog clutch 22, specifically via a drive shaft 23 which is mounted in a double ball bearing 24 of the cover 12.
  • two opposite inlet and outlet channels 28 and 29 are formed in the housing 10. These initially have a radial course and merge into an axial course in the vicinity of the slide bearing 20.
  • the mouths 30 and 31 of these channels are arcuate in a known manner; the bores 26 in the rotor 18 correspond to these channel openings.
  • a control mirror 32 is also arranged, which also has two arcuate slots 33, 34.
  • a device 32 At the end of the shaft 19 opposite the cover 12 there is a device 32 arranged to accommodate the axial thrust compensation. It is not further described because it is not essential to the invention. It lies in a cylindrical recess 36 at the end of the housing 10, which is closed by a cover 37.
  • This device has a compensation plate 39, which is located next to the control mirror 32 and faces the rotor 18 and is designed similarly to the control mirror 32. Before the opening of each bore 26 on the end face of the rotor there is a cylindrical extension 40 in which an annular compensating piston 41 is arranged, which has the shape of a right-angled triangle in cross section, the oblique side facing the compensating plate 39.
  • the compensating piston consists of a relatively solid material, a compression spring 42 arranged in the extension 40 acts on it, which presses it with its oblique side against the oblique side of a sealing ring 43, which is also arranged in the extension 40. It consists of an elastic material and also has the shape of a right-angled triangle in cross section, the oblique side abutting that of the compensating piston 41.
  • the spring 42 presses the sealing ring 43 against the compensating plate 39 via the compensating piston 41. This seals the normally existing gap S between the rotor 18 and the housing 10 or control mirror 32.
  • the compensating pistons arranged in each bore 26 or the extensions 40 are system-pressurized in the direction of the spring force if they are currently on the pressure side.
  • This force resulting from the product of the annular surface of a compensating piston, the system pressure and the number of compensating pistons which are just pressurized, causes the control mirror 32 and the compensating plate 39 to be pressed against one another and the axial gap S to be closed.
  • the compensating piston 41 together with the sealing rings 43 thus have the function of pressing the compensating plate 39 and the control mirror 32 so that - as stated above - the gap S is closed.
  • the compensating pistons 41 exert both an axial and a radial force on the sealing rings 43, so that these are pressed against the outer wall of the extensions 40.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)

Abstract

The axial-piston machine has a rotor (18) in which, in bores (17) running approximately radially, pistons (16) are arranged which slide via cross-head shoes (15) on the inside of a cam ring disposed in the casing (10) of the machine. Adjoining the ends of the bores (17) in the rotor (18) there are bores (26) running axially which communicate, via a bedding area (32) which is disposed between the rotor and the casing and has inlet and outlet ducts (28, 29). So as to provide a gapless seal between the bedding area (32) and the rotor, a sealing device is provided which comprises a compensator plate (39), a sealing ring (43) and a piston (41) acting on which there is a spring element (42) disposed in the bores (26). Said spring element presses the sealing ring (43), via the compensator piston (41), tightly against the compensator plate which bears on the bedding area without leaving a gap. <IMAGE>

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Radialkolbenmaschine nach der Gattung des Hauptanspruchs. Bei derartigen Maschinen ergibt sich die Schwierigkeit, daß die hierbei zwangsläufig auftretenden Axialkräfte auf die Bauteile Steuerspiegel und Rotor abhebend wirken. Diesen Axialkräften entgegen wirkt ein Axiallager. Jedoch entsteht zwischen Steuerspiegel und Rotor aufgrund von Fertigungstoleranzen, Bauteilverformungen und Verschleiß während des Betriebs ein Spalt, über den Leckagen fließen können. Dieser Spalt ändert infolge Belastungsänderungen und Verschleiß laufend seine Größe.The invention is based on a radial piston machine according to the preamble of the main claim. With such machines there is the difficulty that the inevitable axial forces acting on the components of the control mirror and rotor have a lifting effect. An axial bearing counteracts these axial forces. However, due to manufacturing tolerances, component deformations and wear during operation, a gap develops between the control mirror and the rotor, through which leakages can flow. This gap constantly changes in size due to changes in load and wear.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Axialkolbenmaschine mit dem kennzeichnenden Merkmal hat demgegenüber den Vorteil, daß die Leckagen an den obengenannten Teilen durch eine spaltverschließende Einrichtung wesentlich verringert werden. Diese durch den Ausgleichskolben erzielte Maßnahme wird unter anderem dadurch unterstützt, daß die Ausgleichskolben nicht nur durch ein Federelement belastet sind, sondern daß sie im Betrieb druckmittelbeaufschlagt sind, da sie sich auf der Druckseite befinden.The axial piston machine according to the invention with the characteristic feature has the advantage that the leaks in the above-mentioned parts are significantly reduced by a gap-closing device. This measure achieved by the compensating piston is supported, inter alia, by the fact that the compensating pistons are not only loaded by a spring element, but that they are pressurized during operation, since they are on the pressure side.

Ein Ausführungsbeispiel der Erfindung ist in der nachfolgenden Beschreibung und Zeichnung näher erläutert. Diese zeigt in Figur 1 einen Längsschnitt durch eine Radialkolbenmaschine, in Figur 2 eine Einzelheit, die in Figur 1 nicht im Detail dargestellt und mit A bezeichnet ist.An embodiment of the invention is explained in more detail in the following description and drawing. 1 shows a longitudinal section through a radial piston machine, in FIG. 2 a detail which is not shown in detail in FIG. 1 and is designated by A.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In Figur 1 ist mit 10 das Gehäuse einer Radialkolbenpumpe bezeichnet, das einen zylindrischen Innenraum 11 aufweist, welcher durch einen Deckel 12 verschlossen ist. Im Innenraum 11 ist ein Hubring 13 angeordnet, dessen Innenseite 14 ballig ausgebildet ist. An der Innenseite 14 liegen Gleitschuhe 15 an, auf denen sich Kolben 16 abstützen, die in etwa radial verlaufenden Bohrungen 17 eines Rotors 18 gleiten. Dieser ist drehfest auf einer Antriebswelle 19 befestigt, welche einerseits in einem Gleitlager 20 des Gehäuses 10, andererseits in einem Gleitlager 21 des Deckels 12 gelagert ist. Angetrieben wird die Welle 19 über eine Klauenkupplung 22, und zwar über eine Antriebswelle 23, die in einem Doppelkugellager 24 des Deckels 12 gelagert ist.In Figure 1, 10 denotes the housing of a radial piston pump, which has a cylindrical interior 11, which is closed by a cover 12. In the interior 11, a cam ring 13 is arranged, the inside 14 of which is spherical. Sliding shoes 15 rest on the inside 14, on which pistons 16 are supported, which slide in approximately radially running bores 17 of a rotor 18. This is fixed in a rotationally fixed manner on a drive shaft 19 which is mounted on the one hand in a slide bearing 20 of the housing 10 and on the other hand in a slide bearing 21 of the cover 12. The shaft 19 is driven via a dog clutch 22, specifically via a drive shaft 23 which is mounted in a double ball bearing 24 of the cover 12.

In die die Kolben 16 aufnehmenden Bohrungen 17 dringen von der dem Deckel 12 abgewandten Seite her axial im Rotor 18 ausgebildete Bohrungen 26 ein. Im Gehäuse 10 sind zwei einander gegenüberliegende Ein- und Auslaßkanäle 28 bzw. 29 ausgebildet. Diese haben zuerst einen radialen Verlauf und gehen in der Nähe des Gleitlagers 20 in einen axialen Verlauf über. Die Mündungen 30 bzw. 31 dieser Kanäle sind in bekannter Weise bogenförmig ausgebildet; die Bohrungen 26 im Rotor 18 korrespondieren mit diesen Kanalmündungen. Zwischen diesen und dem Rotor 18 ist jedoch noch ein Steuerspiegel 32 angeordnet, der ebenfalls zwei bogenförmige Schlitze 33, 34 aufweist. An dem dem Deckel 12 gegenüberliegenden Ende der Welle 19 ist eine Einrichtung 32 zur Aufnahme des Axialschubausgleichs angeordnet. Sie ist nicht weiter beschrieben, da nicht erfindungswesentlich. Sie liegt in einer zylindrischen Ausnehmung 36 am Ende des Gehäuses 10, welche durch einen Deckel 37 verschlossen ist.Bores 26 formed axially in the rotor 18 penetrate into the bores 17 receiving the pistons 16 from the side facing away from the cover 12. In the housing 10, two opposite inlet and outlet channels 28 and 29 are formed. These initially have a radial course and merge into an axial course in the vicinity of the slide bearing 20. The mouths 30 and 31 of these channels are arcuate in a known manner; the bores 26 in the rotor 18 correspond to these channel openings. Between these and the rotor 18, however, a control mirror 32 is also arranged, which also has two arcuate slots 33, 34. At the end of the shaft 19 opposite the cover 12 there is a device 32 arranged to accommodate the axial thrust compensation. It is not further described because it is not essential to the invention. It lies in a cylindrical recess 36 at the end of the housing 10, which is closed by a cover 37.

In Figur 1 ist die Partie um den Steuerspiegel 32 vereinfacht dargestellt. Sie ist mit A gekennzeichnet und in Figur 2 näher erläutert.In Figure 1, the lot around the control mirror 32 is shown in simplified form. It is marked with A and explained in more detail in FIG. 2.

Bei derartigen bekannten Maschinen ergibt sich die Schwierigkeit, daß sich zwischen Rotor und Steuerspiegel ein Spalt bildet, welcher zu Leckverlusten führt, was den Wirkungsgrad der Maschine negativ beeinflußt. Durch die im folgenden beschriebene Einrichtung wird diese Leckage weitestgehend verhindert. Diese Einrichtung weist eine neben dem Steuerspiegel 32 liegende und dem Rotor 18 zugewandte Ausgleichsplatte 39 auf, welche ähnlich wie der Steuerspiegel 32 ausgebildet ist. Vor der Mündung jeder Bohrung 26 an der Stirnseite des Rotors befindet sich eine zylindrische Erweiterung 40, in der ein ringförmiger Ausgleichskolben 41 angeordnet ist, welcher im Querschnitt die Form eines rechtwinkligen Dreiecks aufweist, wobei die schräge Seite der Ausgleichsplatte 39 zugewandt ist. Der Ausgleichskolben besteht aus einem verhältnismäßig festen Material, auf ihn wirkt eine in der Erweiterung 40 angeordnete Druckfeder 42 ein, die ihn mit seiner schrägen Seite gegen die schräge Seite eines Dichtrings 43 drückt, welcher ebenfalls in der Erweiterung 40 angeordnet ist. Er besteht aus einem elastischen Werkstoff, hat im Querschnitt ebenfalls die Form eines rechtwinkligen Dreiecks, wobei die schräge Seite an derjenigen des Ausgleichskolbens 41 anliegt. Die Feder 42 drückt über den Ausgleichskolben 41 den Dichtring 43 an die Ausgleichsplatte 39. Damit wird der normalerweise bestehende Spalt S zwischen Rotor 18 und Gehäuse 10 bzw. Steuerspiegel 32 abgedichtet.In such known machines there is the difficulty that a gap is formed between the rotor and the control mirror, which leads to leakage losses, which has a negative effect on the efficiency of the machine. This leakage is largely prevented by the device described below. This device has a compensation plate 39, which is located next to the control mirror 32 and faces the rotor 18 and is designed similarly to the control mirror 32. Before the opening of each bore 26 on the end face of the rotor there is a cylindrical extension 40 in which an annular compensating piston 41 is arranged, which has the shape of a right-angled triangle in cross section, the oblique side facing the compensating plate 39. The compensating piston consists of a relatively solid material, a compression spring 42 arranged in the extension 40 acts on it, which presses it with its oblique side against the oblique side of a sealing ring 43, which is also arranged in the extension 40. It consists of an elastic material and also has the shape of a right-angled triangle in cross section, the oblique side abutting that of the compensating piston 41. The spring 42 presses the sealing ring 43 against the compensating plate 39 via the compensating piston 41. This seals the normally existing gap S between the rotor 18 and the housing 10 or control mirror 32.

Die in jeder Bohrung 26 bzw. den Erweiterungen 40 angeordneten Ausgleichskolben werden, wenn sie sich im Betrieb gerade auf der Druckseite befinden, in Richtung der Federkraft systemdruckbeaufschlagt. Diese Kraft, resultierend aus dem Produkt aus Ringfläche eines Ausgleichskolbens, Systemdruck und Anzahl der gerade druckbeaufschlagten Ausgleichskolben bewirkt, daß Steuerspiegel 32 und Ausgleichsplatte 39 aufeinandergepreßt werden und der axiale Spalt S verschlossen wird. Die Ausgleichskolben 41 samt den Dichtringen 43 haben somit die Funktion zu erfüllen, Ausgleichsplatte 39 und Steuerspiegel 32 so aufeinanderzupressen, daß - wie oben ausgeführt - der Spalt S verschlossen wird. Die Ausgleichskolben 41 üben auf die Dichtringe 43 sowohl eine axiale wie auch eine radiale Kraft aus, so daß diese an die Außenwand der Erweiterungen 40 angedrückt werden. Die so gefundene Lösung ist, wenn man die Leckverluste betrachtet, trotzdem kostengünstig.The compensating pistons arranged in each bore 26 or the extensions 40 are system-pressurized in the direction of the spring force if they are currently on the pressure side. This force, resulting from the product of the annular surface of a compensating piston, the system pressure and the number of compensating pistons which are just pressurized, causes the control mirror 32 and the compensating plate 39 to be pressed against one another and the axial gap S to be closed. The compensating piston 41 together with the sealing rings 43 thus have the function of pressing the compensating plate 39 and the control mirror 32 so that - as stated above - the gap S is closed. The compensating pistons 41 exert both an axial and a radial force on the sealing rings 43, so that these are pressed against the outer wall of the extensions 40. The solution found in this way is nevertheless inexpensive if one considers the leakage losses.

Claims (5)

Radialkolbenmaschine mit einem von einer Antriebswelle (19, 23) angetriebenen Rotor (18), der in etwa radial verlaufenden Bohrungen (17) Kolben (16) aufnimmt, die mit ihren aus den Bohrungen ragenden Enden - gegebenenfalls über sogenannte Gleitschuhe (15) - an die Innenseite eines Hubrings (13) gedrückt werden, wobei die etwa radial verlaufenden Bohrungen (17) über im Rotor etwa axial verlaufende Bohrungen (26) und einem zwischen Rotor und Gehäuse (10) der Maschine angeordneten Steuerspiegel (32) mit zwei im Gehäuse (10) ausgebildeten bogenförmigen Mündungen (30, 31) von zwei in diesem Gehäuse ausgebildeten Kanälen (28, 29) in Verbindung stehen, die die Niederdruck- bzw. Hochdruckseite der Maschine bilden und der Steuerspiegel (32) unmittelbar an den Mündungen (30, 31) der Stirnseite des Gehäuses (10) anliegt, dadurch gekennzeichnet, daß sich zwischen Steuerspiegel (32) und Rotor (18) eine am Steuerspiegel anliegende Ausgleichsplatte (39) befindet, an der ein Dichtring (43) aus elastischem Werkstoff anliegt, welcher in der axial verlaufenden Bohrung (26) angeordnet ist und an welchen sich wiederum ein ebenfalls in dieser Bohrung angeordneter, ringförmiger Ausgleichskolben (41) unter Flüssigkeitsdurck und der Kraft einer Feder (42) anlegt.Radial piston machine with a rotor (18) driven by a drive shaft (19, 23), which receives pistons (16) in approximately radially extending bores (17), the ends of which protrude from the bores - possibly via so-called sliding shoes (15) the inside of a cam ring (13) is pressed, the approximately radially running bores (17) via bores (26) running approximately axially in the rotor and a control mirror (32) arranged between the rotor and the housing (10) of the machine with two in the housing ( 10) formed arcuate mouths (30, 31) of two channels (28, 29) formed in this housing, which form the low-pressure or high-pressure side of the machine and the control mirror (32) directly on the mouths (30, 31 ) of the end face of the housing (10), characterized in that between the control mirror (32) and the rotor (18) there is a compensating plate (39) lying against the control mirror, on which a sealing ring (43) rests of elastic material, which is arranged in the axially extending bore (26) and against which in turn an annular compensating piston (41), also arranged in this bore, bears under pressure of liquid and the force of a spring (42). Maschine nach Anspruch 1, dadurch gekennzeichnet, daß sich sowohl der Dichtring (43) wie auch der Ausgleichskolben (41) in einer zylindrischen Erweiterung (40) an den Mündungen der Bohrungen (26) befinden.Machine according to claim 1, characterized in that both the sealing ring (43) and the compensating piston (41) are located in a cylindrical extension (40) at the mouths of the bores (26). Maschine nach Anspruch 1 und/oder 2, dadurch gekennzeichnet, daß die Querschnitte von Dichtring (43) und Ausgleichskolben (41) im Querschnitt die Form eines rechtwinkligen Dreiecks aufweisen, wobei die schrägen Seiten aneinanderliegen.Machine according to claim 1 and / or 2, characterized in that the cross-sections of the sealing ring (43) and compensating piston (41) have the shape of a right-angled triangle in cross-section, the oblique sides abutting one another. Maschine nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Ausgleichskolben aus einem härteren Material bestehen als die Dichtringe (43).Machine according to one of claims 1 to 3, characterized in that the compensating pistons consist of a harder material than the sealing rings (43). Maschine nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß das Federelement eine Wellfeder oder ein Elastomer ist.Machine according to one of claims 1 to 4, characterized in that the spring element is a corrugated spring or an elastomer.
EP92116323A 1991-10-19 1992-09-24 Radial-piston machine Withdrawn EP0538637A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19914134582 DE4134582A1 (en) 1991-10-19 1991-10-19 RADIAL PISTON MACHINE
DE4134582 1991-10-19

Publications (1)

Publication Number Publication Date
EP0538637A1 true EP0538637A1 (en) 1993-04-28

Family

ID=6442995

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92116323A Withdrawn EP0538637A1 (en) 1991-10-19 1992-09-24 Radial-piston machine

Country Status (2)

Country Link
EP (1) EP0538637A1 (en)
DE (1) DE4134582A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6120035A (en) * 1998-08-26 2000-09-19 Welker Engineering Company Mating ring seal members with beveled mitered interface
WO2006003689A1 (en) * 2004-06-30 2006-01-12 S.A.I. Societa' Apparecchiature Idrauliche Spa Fluid machine with radial cylinders

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19633169A1 (en) 1996-08-17 1998-02-19 Teves Gmbh Alfred Electric motor / pump unit
DE19650275A1 (en) * 1996-12-04 1998-06-10 Teves Gmbh Alfred Piston pump driven by electric motor especially for radial piston pumps

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB661652A (en) * 1942-01-14 1951-11-28 Oilgear Co Improvements in or relating to hydraulic pumps or motors
US2716944A (en) * 1954-05-24 1955-09-06 Oilgear Co Mechanism for pumping a liquid and a lubricant simultaneously
US2901975A (en) * 1954-12-30 1959-09-01 Oilgear Co Pumping unit
CH348322A (en) * 1954-11-24 1960-08-15 Reiners Walter Dr Ing Multi-cylinder device representing an oil pump or an oil motor
FR2426801A1 (en) * 1978-05-22 1979-12-21 Poclain Hydraulics Sa Radial piston hydraulic motor for auxiliary trailer drive - has valve plate disengaged from cylinder block when idling
WO1986004961A1 (en) * 1985-02-15 1986-08-28 Hydro-Mec S.R.L. Radial piston rotary machine capable of forming a pump or an engine
EP0263218A1 (en) * 1986-10-08 1988-04-13 POCLAIN HYDRAULICS Société Anonyme de droit français Hydraulic mechanism with fluid distribution disk and counter disk

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB661652A (en) * 1942-01-14 1951-11-28 Oilgear Co Improvements in or relating to hydraulic pumps or motors
US2716944A (en) * 1954-05-24 1955-09-06 Oilgear Co Mechanism for pumping a liquid and a lubricant simultaneously
CH348322A (en) * 1954-11-24 1960-08-15 Reiners Walter Dr Ing Multi-cylinder device representing an oil pump or an oil motor
US2901975A (en) * 1954-12-30 1959-09-01 Oilgear Co Pumping unit
FR2426801A1 (en) * 1978-05-22 1979-12-21 Poclain Hydraulics Sa Radial piston hydraulic motor for auxiliary trailer drive - has valve plate disengaged from cylinder block when idling
WO1986004961A1 (en) * 1985-02-15 1986-08-28 Hydro-Mec S.R.L. Radial piston rotary machine capable of forming a pump or an engine
EP0263218A1 (en) * 1986-10-08 1988-04-13 POCLAIN HYDRAULICS Société Anonyme de droit français Hydraulic mechanism with fluid distribution disk and counter disk

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6120035A (en) * 1998-08-26 2000-09-19 Welker Engineering Company Mating ring seal members with beveled mitered interface
WO2006003689A1 (en) * 2004-06-30 2006-01-12 S.A.I. Societa' Apparecchiature Idrauliche Spa Fluid machine with radial cylinders
US8382449B2 (en) 2004-06-30 2013-02-26 S.A.I. Societa' Apparecchiature Idrauliche Spa Fluid machine with radial cylinders

Also Published As

Publication number Publication date
DE4134582A1 (en) 1993-04-22

Similar Documents

Publication Publication Date Title
DE3340333C1 (en) Swash plate axial piston pump
DE4037455C1 (en)
DE1703594B2 (en) Axial piston pump
DE1804529A1 (en) Liquid motor or pump
DE3233579A1 (en) AXIAL PISTON MACHINE
DE3700573A1 (en) Piston machine, in particular axial or radial piston machine
DE1728421A1 (en) Axial piston machine
EP0538637A1 (en) Radial-piston machine
DE2134026A1 (en) AXIAL PISTON MACHINE
DE3444774A1 (en) HYDRAULIC ENGINE
DE2248316C2 (en) Radial piston machine
DE2540879B1 (en) Multicylinder hydraulic piston pump - has segment-shaped recesses in leaf spring valve seat face between pressure ducts in housing
DE3725156C2 (en)
DE2165781C2 (en) Hydraulic radial piston motor or pump
DE2159418A1 (en) Axial piston machine
DE19653591C1 (en) Fluid distributor for hydraulic, radial piston-type pump or motor
EP0329208B1 (en) Hydraulically driven high-pressure cleaner
DE2263837A1 (en) RADIAL PISTON PUMP
DE2236125A1 (en) RADIAL PISTON MACHINE
DE1239570B (en) Device for pressing the control plate disk of a pressure fluid axial piston machine against the face of the cylinder drum
DE1015689B (en) Radial piston machine
DE2254751B2 (en) Radial piston machine
DE2841083A1 (en) PRESSURE REGULATING VALVE FOR A DISPLACEMENT PUMP WITH VARIABLE FLOW RATE
DE2123429A1 (en) Sealing for flowable media under high pressure
AT205860B (en) Hydraulic machine with a rotating cylinder body

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 19930922

17Q First examination report despatched

Effective date: 19940628

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 19950314