EP0384974A1 - Hydrostatic machine - Google Patents

Hydrostatic machine Download PDF

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Publication number
EP0384974A1
EP0384974A1 EP19890123243 EP89123243A EP0384974A1 EP 0384974 A1 EP0384974 A1 EP 0384974A1 EP 19890123243 EP19890123243 EP 19890123243 EP 89123243 A EP89123243 A EP 89123243A EP 0384974 A1 EP0384974 A1 EP 0384974A1
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EP
European Patent Office
Prior art keywords
rotor
shaft
pistons
bores
machine
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Granted
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EP19890123243
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German (de)
French (fr)
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EP0384974B1 (en
Inventor
Dieter Dipl.-Ing. Weigle
Dieter Dipl.-Ing. Fetting
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0384974A1 publication Critical patent/EP0384974A1/en
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    • 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
    • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • F04B1/107—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders
    • F04B1/1071—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary with actuating or actuated elements at the outer ends of the cylinders with rotary cylinder blocks

Definitions

  • the invention is based on a hydrostatic machine according to the preamble of the main claim.
  • the thrust force acting on the rotor is absorbed by the fact that this is acted upon by pressurized pistons which are mounted in bores arranged in the housing cover, i. H. the thrust must be absorbed by the housing cover.
  • This is not very cheap, since the housing cover must be made stronger so that the forces and especially the pistons increase. This makes the machine more expensive (DE-OS 27 48 455).
  • the hydrostatic machine according to the invention with the characterizing features of the main claim has the advantage that the thrust is short-circuited via the shaft of the machine and transmitted to the housing, which is strength, noise and space favorable. Further advantageous embodiments of the invention result from the remaining claims.
  • the radial piston machine has a housing 10 which has a cylindrical interior 11 and is closed by a cover 12.
  • a cam ring 13 is mounted in the interior, on the curved inside of which 14 sliding shoes 15 of pistons 16 slide, which are arranged in radial bores 17 of a rotor 18.
  • the rotor is connected in one piece to a shaft 19 which is mounted in a through bore 20 of the housing 10 or 21 of the cover 12.
  • the shaft 19 is driven via a coupling device 22, specifically via a drive connection 23, which is mounted in a double roller bearing 24 arranged in the cover 12.
  • At least one slot 26 opens axially into each of the bores 17 receiving the pistons 16, which can be connected to two approximately kidney-shaped openings 28A, 29A by inlet and outlet channels 28, 29 formed in the housing 10.
  • four such cubs are provided. They consist of a metallic material with good sliding properties, e.g. B. brass.
  • springs 41 are also provided in the bore, which press on the cobs 39. These are from the high pressure side through suitable holes and channels, eg. B. channel 42, pressurized with high pressure. In this way, an axial force is exerted on the disk 32 and thus on the shaft 19 and the rotor 18, which counteracts the hydraulic force mentioned above. By measuring the cobs, this counterforce can be measured in such a way that a slight excess force is generated on the shaft in the direction of the cover 37.
  • both the radial piston machine and the thrust compensation are designed differently.
  • the overall structure has remained essentially the same, but now the rotor - designated by 50 - is a separate part on the shaft 51. It is connected to the shaft 51 in a rotationally fixed manner by means of a spline toothing.
  • the device for thrust compensation is now designated 52 and in turn has a disk 53, which is fixedly arranged on the shaft 51 between the rotor 50 and the cover 12. It is supported there on a shaft shoulder 54.
  • the fluid pressure prevailing in the machine in turn generates a thrust on the rotor 50, which is absorbed on the disk 53.
  • This force is transmitted via the shaft to the disk 57, which is supported on the housing via the disk 61.
  • the short-circuited force curve is again characterized by a thick solid line.
  • FIG. 3 differs from that of Figure 2 in that a flange sleeve 65 is now shrunk onto the shaft 50 with its extension 65A, which takes over the function of the disk 53 according to the embodiment of Figure 2.
  • the rotor 50 is not seated on the shaft 51 in a rotationally fixed manner, but is set in rotation by a bolt 66 which is fastened in the flange sleeve 60.
  • the power flow for the thrust compensation is again the same as in the previous embodiment.
  • FIG. 4 again largely corresponds to that according to FIG. 3, but with the difference that a slot 63 is now formed on the flange sleeve 65, in which an extension 64 engages on the rotor 150.
  • the fact that the sliding arrangement of the cobs 39 allows a readjustment is possible.
  • the possibility of expansion is restricted by the power line via the shaft and the housing (not via the cover). This has the advantage that the amount of material required for the pump to function safely can be reduced.

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

Abstract

The hydrostatic machine is designed as a radial piston machine, the pistons (16) of which slide in radial bores (17) in a rotor (18) and are supported by means of sliding shoes (15) on a lifting ring (13). The bores (17) have a lateral admission via slots (26) in the rotor which are joined to corresponding ducts (28, 29) in the housing (10) of the machine (so-called lateral admission radial piston machine). The axial thrust produced thereby on the rotor (18) and/or the shaft (19) is absorbed by a device (31) which comprises a disc (32) firmly located on the shaft (19), in contact with which disc are small pistons (39) which are arranged in bores (40) in the housing and acted on by the high pressure. In this way a short-circuited thrust equalisation is obtained from the rotor via the shaft and the disc (32) back to the rotor. This method of thrust equalisation makes it possible to reduce the dimensions of the machine. In addition this also results in improved noise characteristics. <IMAGE>

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer hydrostatischen Maschine nach der Gattung des Hauptanspruchs. Bei einer derartigen bekannten hydro­statischen Maschine wird die auf den Rotor wirkende Schubkraft dadurch aufgenommen, daß auf diesen druckbeaufschlagte Kolben einwirken, welche in im Gehäusedeckel angeordneten Bohrungen gelagert sind, d. h. die Schubkraft muß vom Gehäusedeckel auf­genommen werden. Das ist nicht sehr günstig, da der Gehäusedeckel entsprechend stärker ausgebildet werden muß, um die Kräfte und vor allem die Kolben auf zunehmen. Dadurch verteuert sich die Maschine (DE-OS 27 48 455).The invention is based on a hydrostatic machine according to the preamble of the main claim. In such a known hydrostatic machine, the thrust force acting on the rotor is absorbed by the fact that this is acted upon by pressurized pistons which are mounted in bores arranged in the housing cover, i. H. the thrust must be absorbed by the housing cover. This is not very cheap, since the housing cover must be made stronger so that the forces and especially the pistons increase. This makes the machine more expensive (DE-OS 27 48 455).

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße hydrostatische Maschine mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß die Schubkraft über die Welle der Maschine kurzgeschlossen und auf das Gehäuse übertragen wird, was festigkeitsmäßig, geräuschlich und räumlich günstiger ist. Weitere vorteilhafte Ausgestaltungen der Erfindung ergeben sich aus den übrigen Ansprüchen.The hydrostatic machine according to the invention with the characterizing features of the main claim has the advantage that the thrust is short-circuited via the shaft of the machine and transmitted to the housing, which is strength, noise and space favorable. Further advantageous embodiments of the invention result from the remaining claims.

Zeichnungdrawing

Ausführungsbeispiele der Erfindung sind in der nachfolgenden Beschreibung und Zeichnung näher erläutert. Letztere zeigt in den Figuren 1 bis 4 Längsschnitte durch Radialkolbenmaschinen.Embodiments of the invention are explained in more detail in the following description and drawing. The latter shows longitudinal sections through radial piston machines in FIGS. 1 to 4.

Beschreibung der ErfindungsbeispieleDescription of the invention examples

Die Radialkolbenmaschine weist ein Gehäuse 10 auf, das einen zylindrischen Innenraum 11 hat und durch einen Deckel 12 verschlossen ist. Im Innenraum ist ein Hubring 13 gelagert, an dessen gewölbter Innenseite 14 Gleitschuhe 15 von Kolben 16 gleiten, welche in radialen Bohrungen 17 eines Rotors 18 angeordnet sind. Der Rotor ist einstückig mit einer Welle 19 verbunden, welche in einer durchgehenden Bohrung 20 des Gehäuses 10 bzw. 21 des Deckels 12 gelagert ist. Die Welle 19 wird über eine Kupplungseinrichtung 22 angetrieben, und zwar über einen Antriebstutzen 23, welcher in einem im Deckel 12 angeordneten Doppelrollenlager 24 gelagert ist. In jede die Kolben 16 aufnehmenden Bohrungen 17 mündet axial mindestens ein Schlitz 26, welche mit zwei etwa nierenförmigen Mündungen 28A, 29A von im Gehäuse 10 ausgebildeten Einlaß- bzw. Auslaßkanälen 28, 29 in Verbindung bringbar sind. Der bisher beschriebene Aufbau der Radialkolbenmaschine ist bekannt und deshalb ebenfalls nur kurz beschrieben.The radial piston machine has a housing 10 which has a cylindrical interior 11 and is closed by a cover 12. A cam ring 13 is mounted in the interior, on the curved inside of which 14 sliding shoes 15 of pistons 16 slide, which are arranged in radial bores 17 of a rotor 18. The rotor is connected in one piece to a shaft 19 which is mounted in a through bore 20 of the housing 10 or 21 of the cover 12. The shaft 19 is driven via a coupling device 22, specifically via a drive connection 23, which is mounted in a double roller bearing 24 arranged in the cover 12. At least one slot 26 opens axially into each of the bores 17 receiving the pistons 16, which can be connected to two approximately kidney-shaped openings 28A, 29A by inlet and outlet channels 28, 29 formed in the housing 10. The structure of the radial piston machine described so far is known and is therefore only described briefly.

Durch das im Auslaßkanal 29 unter Hochdruck stehende Druckmittel wird über den Schlitz 26 ein Axialschub auf den Rotor 18 samt Welle 19 ausgeübt, und zwar in Richtung zum Antriebszapfen 23. Dieser Axialschub ist hoch und wird durch eine hydrostatische Einrichtung 31 zum Schubausgleich aufgenommen. Diese Einrichtung weist eine Scheibe 32 auf, welche über einen Stift 33 drehfest mit der Welle 19 verbunden ist und sich dort an eine Wellenschulter 34 anlegt. Sie wird festgespannt durch eine auf die Welle aufgeschraubte Mutter 35. Die dort im Gehäuse 10 vorhandene Öffnung 36 ist durch einen Deckel 37 verschlossen. An die dem Rotor 18 zugewandte Seite der Scheibe 32 legen sich mehrere Kölbchen 39 an, die abgedichtet in regelmäßig auf einem Kreisumfang verteilten Bohrungen 40 im Gehäuse 10 angeordnet sind. Im Ausführungsbeispiel sind vier solcher Kölbchen vorgesehen. Sie bestehen hier aus aus einem metallischen Werkstoff mit guten Gleiteigenschaften, z. B. Messing. Zusätzlich sind in der Bohrung noch Federn 41 vorgesehen, welche auf die Kölbchen 39 drücken. Diese werden von der Hochdruckseite her über geeignete Bohrungen und Kanäle, z. B. Kanal 42, mit Hochdruck beaufschlagt. Auf diese Weise wird eine axiale Kraft auf die Scheibe 32 und damit auf die Welle 19 und den Rotor 18 ausgeübt, welche der weiter oben genannten hydraulischen Kraft entgegenwirkt. Durch Bemessung der Kölbchen kann diese Gegenkraft so bemessen werden, daß eine geringe Überschußkraft an der Welle in Richtung zum Deckel 37 hin entsteht. Dadurch wird der Spalt zwischen dem Rotor 18 und dem Gehäuse, welcher durch eine Metallscheibe 43 überbrückt ist, auf alle Fälle dicht gehalten. Der Kräfteverlauf (Kraftschluß) zwischen Rotor 18, Welle 19 und Einrich­tung 31 zum Schubausgleich ist durch eine stark ausgezogene Linie mit Pfeilen gekennzeichnet. Daraus ist zu erkennen, daß dieser Kraftausgleich kurzgeschlossen ist, was eine besonders zweckmäßige Konstruktion ergibt.Due to the pressure medium in the outlet channel 29 under high pressure, an axial thrust is exerted on the rotor 18 together with the shaft 19 via the slot 26, namely in the direction of the drive pin 23. This axial thrust is high and is absorbed by a hydrostatic device 31 for thrust compensation. This device has a disk 32, which is connected in a rotationally fixed manner to the shaft 19 by means of a pin 33 and lies there against a shaft shoulder 34. It is clamped by a nut 35 screwed onto the shaft. The opening 36 in the housing 10 there is closed by a cover 37. On the side of the disk 32 facing the rotor 18 create several cubs 39, which are arranged sealed in bores 40 in the housing 10 which are regularly distributed over a circumference. In the exemplary embodiment, four such cubs are provided. They consist of a metallic material with good sliding properties, e.g. B. brass. In addition, springs 41 are also provided in the bore, which press on the cobs 39. These are from the high pressure side through suitable holes and channels, eg. B. channel 42, pressurized with high pressure. In this way, an axial force is exerted on the disk 32 and thus on the shaft 19 and the rotor 18, which counteracts the hydraulic force mentioned above. By measuring the cobs, this counterforce can be measured in such a way that a slight excess force is generated on the shaft in the direction of the cover 37. As a result, the gap between the rotor 18 and the housing, which is bridged by a metal disk 43, is kept tight in all cases. The course of forces (frictional connection) between the rotor 18, shaft 19 and device 31 for thrust compensation is indicated by a solid line with arrows. From this it can be seen that this force balance is short-circuited, which results in a particularly useful construction.

Beim Ausführungsbeispiel nach Figur 2 sind sowohl die Radialkolben­maschine wie auch der Schubausgleich anders gestaltet. Gleichge­blieben ist im wesentlichen der Gesamtaufbau, jedoch ist nunmehr der Rotor - bezeichnet mit 50 - ein separates Teil auf der Welle 51. Er ist über eine Vielkeilverzahnung mit der Welle 51 drehfest ver­bunden. Die Einrichtung zum Schubausgleich ist nun mit 52 bezeichnet und weist wiederum eine Scheibe 53 auf, welche fest auf der Welle 51 zwischen dem Rotor 50 und dem Deckel 12 angeordnet ist. Sie stützt sich dort an einer Wellenschulter 54 ab. An der der Scheibe 53 zugewandten Seite des Rotors 50 sind in diesem zylindrische Aus­ nehmungen 55 ausgebildet, in welchen Kölbchen 39 dicht angeordnet sind und sich mit ihren Böden an die Scheibe 53 unter Flüssigkeits­druck anlegen, welcher wiederum von der Hochdruckseite stammt. Da der Rotor 50 nur drehfest mit der Welle verbunden ist, ist eine zusätzliche Einrichtung notwendig, welche eine Scheibe 57 aufweist, die wiederum am Ende der Welle 51 drehfest und axial unverschiebbar befestigt ist, und zwar durch eine Mutter 58, welche die Scheibe gegen eine Wellenschulter 59 drückt. Zwischen der Scheibe 57 und einer ihr zugewandten Fläche 60 am Gehäuse befindet sich eine Gleit­scheibe 61, welche durch einen Stift 62 gegen Verdrehen gesichert ist. Es ist noch zu bemerken, daß die Welle 51 nunmehr unmittelbar angetrieben wird. Die Kölbchen 39 bestehen in diesem Fall aus Kunst­stoff, da sie nicht an der Scheibe 53 gleiten.In the exemplary embodiment according to FIG. 2, both the radial piston machine and the thrust compensation are designed differently. The overall structure has remained essentially the same, but now the rotor - designated by 50 - is a separate part on the shaft 51. It is connected to the shaft 51 in a rotationally fixed manner by means of a spline toothing. The device for thrust compensation is now designated 52 and in turn has a disk 53, which is fixedly arranged on the shaft 51 between the rotor 50 and the cover 12. It is supported there on a shaft shoulder 54. On the side of the rotor 50 facing the disk 53 there are cylindrical outlets in it Recesses 55 formed in which Cologne 39 are arranged densely and with their bottoms against the disc 53 under liquid pressure, which in turn comes from the high pressure side. Since the rotor 50 is only non-rotatably connected to the shaft, an additional device is necessary, which has a disk 57, which in turn is non-rotatably and axially non-displaceably fastened at the end of the shaft 51, namely by a nut 58 which holds the disk against one Shaft shoulder 59 presses. Between the disk 57 and a surface 60 facing it on the housing there is a sliding disk 61 which is secured against rotation by a pin 62. It should also be noted that the shaft 51 is now driven directly. The Kölbchen 39 are made of plastic in this case, since they do not slide on the disc 53.

Der in der Maschine herrschende Flüssigkeitsdruck erzeugt wiederum eine Schubkraft am Rotor 50, die an der Scheibe 53 aufgenommen wird. Diese Kraft wird über die Welle weitergeleitet auf die Scheibe 57, die sich über die Scheibe 61 am Gehäuse abstützt. Der kurzge­schlossene Kraftverlauf ist wiederum durch eine dick ausgezogene Linie gekennzeichnet.The fluid pressure prevailing in the machine in turn generates a thrust on the rotor 50, which is absorbed on the disk 53. This force is transmitted via the shaft to the disk 57, which is supported on the housing via the disk 61. The short-circuited force curve is again characterized by a thick solid line.

Das Ausführungsbeispiel nach Figur 3 unterscheidet sich von dem­jenigen nach Figur 2 dadurch, daß nunmehr auf die Welle 50 mit ihrem Fortsatz 65A eine Flanschhülse 65 aufgeschrumpft ist, welche die Funktion der Scheibe 53 nach dem Ausführungsbeispiel der Figur 2 übernimmt. Bei diesem Ausführungsbeispiel sitzt der Rotor 50 nicht drehfest auf der Welle 51, sondern wird durch einen Bolzen 66 in Rotation versetzt, welcher in der Flanschhülse 60 befestigt ist. Der Kraftfluß für den Schubausgleich ist wiederum derselbe wie beim vorigen Ausführungsbeispiel.The embodiment of Figure 3 differs from that of Figure 2 in that a flange sleeve 65 is now shrunk onto the shaft 50 with its extension 65A, which takes over the function of the disk 53 according to the embodiment of Figure 2. In this embodiment, the rotor 50 is not seated on the shaft 51 in a rotationally fixed manner, but is set in rotation by a bolt 66 which is fastened in the flange sleeve 60. The power flow for the thrust compensation is again the same as in the previous embodiment.

Das Ausführungsbeispiel nach Figur 4 entspricht wiederum weitest­gehend demjenigen nach Figur 3, jedoch mit dem Unterschied, daß nunmehr an der Flanschhülse 65 ein Schlitz 63 ausgebildet ist, in welchen ein Fortsatz 64 am Rotor 150 eingreift.The embodiment according to FIG. 4 again largely corresponds to that according to FIG. 3, but with the difference that a slot 63 is now formed on the flange sleeve 65, in which an extension 64 engages on the rotor 150.

Für alle Ausführungsbeispiele gilt, daß durch die verschiebliche Anordnung der Kölbchen 39 eine Nachstellmöglichkeit gegeben ist. Durch die Kraftleitung über die Welle und das Gehäuse (nicht über den Deckel) wird die Dehnungsmöglichkeit eingeschränkt. Das hat den Vorteil, daß der Materialeinsatz, der zu einer sicheren Funktion der Pumpe nötig ist, verringert werden kann. Außerdem entfällt eine Anregung durch den Lagerdeckel bei Druckschwankungen bei Kolben­wechsel, so daß sich ein günstigeres Geräuschverhalten ergibt.For all of the exemplary embodiments, the fact that the sliding arrangement of the cobs 39 allows a readjustment is possible. The possibility of expansion is restricted by the power line via the shaft and the housing (not via the cover). This has the advantage that the amount of material required for the pump to function safely can be reduced. In addition, there is no excitation by the bearing cover in the event of pressure fluctuations when changing the piston, so that there is more favorable noise behavior.

Claims (7)

1. Hydrostatische Maschine mit einem auf einer Welle (19) drehfest angeordneten Rotor (18) mit in radial verlaufenden Bohrungen (17) angeordneten Kolben (16), die mit ihren aus den Bohrungen ragenden Enden - gegebenenfalls über Gleitschuhe (15) - an einer Hubkurve (14) gleiten, wobei die Bohrungen über Steuerschlitze (26) seitlich am Rotor mündenden Kanälen (28, 29) (Hochdruck/Niederdruck) zwecks Steuerung des Druckmittels in Verbindung stehen, sowie mit einer Einrichtung (31) zum Ausgleich des vom Druckmittel auf den Rotor ausgeübten Axialschubs, welche druckmittelbeaufschlagte Kolben (39) aufweist, dadurch gekennzeichnet, daß die Einrichtung (31) eine fest auf der Welle (19) angeordnete Scheibe (32) aufweist, an der die Kolben (39) anliegen, welche in Bohrungen (40) des Gehäuses (10) angeordnet sind, und daß Welle und Rotor einstückig ausgebildet sind.1. Hydrostatic machine with a rotor (18) arranged in a rotationally fixed manner on a shaft (19) with pistons (16) arranged in radially extending bores (17), with their ends protruding from the bores - optionally via sliding shoes (15) - on one Stroke curve (14) slide, the bores are connected via control slots (26) on the sides of the rotor-opening channels (28, 29) (high pressure / low pressure) for the purpose of controlling the pressure medium, and with a device (31) for compensating for the pressure medium axial thrust exerted on the rotor, which has pistons (39) pressurized by pressure medium, characterized in that the device (31) has a disk (32) which is fixedly arranged on the shaft (19) and against which the pistons (39) which lie in bores ( 40) of the housing (10) are arranged, and that the shaft and rotor are formed in one piece. 2. Maschine nach Anspruch 1, dadurch gekennzeichnet, daß sich die die Kolben aufnehmenden Bohrungen (40) in regelmäßigen, auf einem Kreis liegenden Abständen befinden.2. Machine according to claim 1, characterized in that the piston-receiving bores (40) are at regular intervals lying on a circle. 3. Maschine nach Anspruch 1 und/oder 2, dadurch gekennzeichnet, daß die Kolben aus einem metallischen Werkstoff mit guten Gleiteigen­schaften bestehen.3. Machine according to claim 1 and / or 2, characterized in that the pistons consist of a metallic material with good sliding properties. 4. Hydrostatische Maschine mit einem auf einer Welle (51) drehfest oder lose angeordneten Rotor (50) mit in radial verlaufenden Bohrungen (17) angeordneten Kolben (16), die mit ihren aus den Bohrungen ragenden Enden - gegebenenfalls über Gleitschuhe (15) - an einer Hubkurve (14) gleiten, wobei die Bohrungen über Steuerschlitze (26) mit seitlich am Rotor mündenden Kanälen (28, 29) zwecks Steuerung des Druckmittels in Verbindung stehen, sowie mit einer Einrichtung (52) zum Ausgleich des vom Druckmittel auf den Rotor ausgeübten Axialschubs, welche druckmittelbeaufschlagte Kolben (40A) aufweist, dadurch gekennzeichnet, daß die Einrichtung (52) eine fest auf der Welle (51) angeordnete erste Scheibe (53) aufweist, an der in Ausnehmungen (55) des Rotors (50) angeordnete, druckbeaufschlagte Kolben (39A) anliegen, daß auf der Welle (51) eine ein mechanisches Axiallager bildende zweite Scheibe (57) fest angeordnet ist, die sich an einer am Gehäuse der Maschine ebenfalls drehfest ange­ordneten Gleitscheibe (61) abstützt, und daß der Rotor ein separates Teil bildet (Figur 2).4. Hydrostatic machine with a rotor (50), which is arranged on a shaft (51) in a rotationally fixed or loose manner, with pistons (16) arranged in radially running bores (17), the ends of which protrude from the bores - possibly via sliding shoes (15) - slide on a stroke curve (14), the bores being connected via control slots (26) to channels (28, 29) which open at the side of the rotor for the purpose of controlling the pressure medium, and with a device (52) for compensating for the pressure medium on the rotor Exerted axial thrust, which has pistons (40A) acted upon by pressure medium, characterized in that the device (52) has a first disc (53) fixedly arranged on the shaft (51), on which are arranged in recesses (55) of the rotor (50), pressurized pistons (39A) rest on the shaft (51) a second axial disk (57) forming a mechanical thrust bearing, which is also rotatably attached to a on the housing of the machine dneten sliding disc (61) supports, and that the rotor forms a separate part (Figure 2). 5. Maschine nach Anspruch 4, dadurch gekennzeichnet, daß die mit den Kolben (39A) in Wirkverbindung stehende erste Scheibe (65) einen zylindrischen Fortsatz (65A) aufweist, mit dem sie auf die Welle (50) aufgeschrumpft ist (Figur 3).5. Machine according to claim 4, characterized in that with the pistons (39A) operatively connected first disc (65) has a cylindrical extension (65A) with which it is shrunk onto the shaft (50) (Figure 3). 6. Maschine nach Anspruch 4 und/oder 5, dadurch gekennzeichnet, daß die erste Scheibe (65) zum Antrieb des verdrehbar auf der Welle sitzenden Rotors (150) dient (Figur 4).6. Machine according to claim 4 and / or 5, characterized in that the first disc (65) is used to drive the rotatably seated on the shaft rotor (150) (Figure 4). 7. Maschine nach einem der Ansprüche 4 bis 6, dadurch gekennzeich­net, daß die druckmittelbeaufschlagten Kolben (39A) aus Kunststoff bestehen und in in regelmäßigen Abständen liegenden Ausnehmungen (55) an der Stirnseite des Rotors (50) angeordnet sind.7. Machine according to one of claims 4 to 6, characterized in that the pressurized pistons (39A) consist of plastic and are arranged at regular intervals in recesses (55) on the end face of the rotor (50).
EP89123243A 1989-02-25 1989-12-15 Hydrostatic machine Expired - Lifetime EP0384974B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3905936 1989-02-25
DE3905936A DE3905936A1 (en) 1989-02-25 1989-02-25 HYDROSTATIC MACHINE

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EP0384974A1 true EP0384974A1 (en) 1990-09-05
EP0384974B1 EP0384974B1 (en) 1993-09-01

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2283541A (en) * 1993-11-03 1995-05-10 Rexroth Mannesmann Gmbh Radial piston machine
CN102619675A (en) * 2011-06-16 2012-08-01 兰州理工大学 Seven parts individual effecting piston cylinder polarization type radial plunger motor
CN102644575A (en) * 2012-05-07 2012-08-22 吕慧彬 Connecting rod sliding shoe type flow distribution radial plunger pump

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4123674C2 (en) * 1991-07-17 2002-07-11 Bosch Gmbh Robert Hydrostatic piston machine
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GB9525028D0 (en) * 1995-12-06 1996-02-07 Unipat Ag Hydrostatic piston machine
DE19959020A1 (en) * 1999-12-08 2001-06-13 Bosch Gmbh Robert Hydraulic unit with at least one displacement machine, in particular with a radial piston machine (pumps or motor)

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GB2283541A (en) * 1993-11-03 1995-05-10 Rexroth Mannesmann Gmbh Radial piston machine
CN102619675A (en) * 2011-06-16 2012-08-01 兰州理工大学 Seven parts individual effecting piston cylinder polarization type radial plunger motor
CN102619675B (en) * 2011-06-16 2014-07-23 兰州理工大学 Seven parts individual effecting piston cylinder polarization type radial plunger motor
CN102644575A (en) * 2012-05-07 2012-08-22 吕慧彬 Connecting rod sliding shoe type flow distribution radial plunger pump
CN102644575B (en) * 2012-05-07 2015-01-21 吕慧彬 Connecting rod sliding shoe type flow distribution radial plunger pump

Also Published As

Publication number Publication date
DE58905473D1 (en) 1993-10-07
DE3905936A1 (en) 1990-09-06
EP0384974B1 (en) 1993-09-01
US5201260A (en) 1993-04-13

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