EP0384974B1 - Hydrostatic machine - Google Patents

Hydrostatic machine Download PDF

Info

Publication number
EP0384974B1
EP0384974B1 EP89123243A EP89123243A EP0384974B1 EP 0384974 B1 EP0384974 B1 EP 0384974B1 EP 89123243 A EP89123243 A EP 89123243A EP 89123243 A EP89123243 A EP 89123243A EP 0384974 B1 EP0384974 B1 EP 0384974B1
Authority
EP
European Patent Office
Prior art keywords
rotor
shaft
disc
pistons
holes
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.)
Expired - Lifetime
Application number
EP89123243A
Other languages
German (de)
French (fr)
Other versions
EP0384974A1 (en
Inventor
Dieter Dipl.-Ing. Weigle
Dieter Dipl.-Ing. Fetting
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 EP0384974A1 publication Critical patent/EP0384974A1/en
Application granted granted Critical
Publication of EP0384974B1 publication Critical patent/EP0384974B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04B1/10—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 category of one of claims 1 or 4.
  • the thrust force acting on the rotor is absorbed by the fact that it is acted upon by pressurized pistons which are mounted in bores arranged in the housing cover. d. H. the thrust must be absorbed by the housing cover. This is not very cheap, since the housing cover must be made stronger to take up the forces and especially the pistons. This makes the machine more expensive (DE-OS 27 48 455).
  • a hydrostatic machine according to the invention with the characterizing features of one of the independent claims 1 or 4 in contrast, has the advantage that the thrust force 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. In the interior, a cam ring 13 is mounted, 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.
  • each slot 26 opens axially, which can be connected to two approximately kidney-shaped openings 28A, 29A of 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.
  • 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 fixed 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 60 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 sliding arrangement of the cobs 39 allows adjustment.
  • 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.

Landscapes

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

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer hydrostatischen Maschine nach der Gattung eines der Ansprüche 1 oder 4. 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 category of one of claims 1 or 4. In such a known hydrostatic machine, the thrust force acting on the rotor is absorbed by the fact that it is acted upon by pressurized pistons which are mounted in bores arranged in the housing cover. d. H. the thrust must be absorbed by the housing cover. This is not very cheap, since the housing cover must be made stronger to take up the forces and especially the pistons. This makes the machine more expensive (DE-OS 27 48 455).

Vorteile der ErfindungAdvantages of the invention

Eine erfindungsgemäße hydrostatische Maschine mit den kennzeichnenden Merkmalen eines der unabhängigen Ansprüche 1 oder 4, 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.A hydrostatic machine according to the invention with the characterizing features of one of the independent claims 1 or 4, in contrast, has the advantage that the thrust force 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. In the interior, a cam ring 13 is mounted, 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. In each of the bores 17 receiving the pistons 16, at least one slot 26 opens axially, which can be connected to two approximately kidney-shaped openings 28A, 29A of 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 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 Ausnehmungen 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 39A 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 fixed 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 recesses therein 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 39A 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 60 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 60 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 exemplary 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.It applies to all the exemplary embodiments that the sliding arrangement of the cobs 39 allows adjustment. 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.

Claims (7)

  1. Hydrostatic machine having a rotor (18, 50, 150) which is arranged on a shaft (19, 51) and has pistons (16) arranged in radially extending holes (17), the ends of which pistons protruding from the holes slide - possibly by means of sliding shoes (15) - on a lift cam (14), the holes being in connection via control slots (26) with passages (28, 29) (high pressure/low pressure) for the purpose of controlling the pressure medium and opening laterally at the rotor, and having a multi-part casing (10, 12, 37) for accommodating the rotor (18, 50, 150) and the passages (28, 29) and having a device (31, 52) for balancing the axial thrust exerted by the pressure medium on the rotor (18, 50, 150), which device has small pistons (39, 39A) subjected to pressure medium and a disc (32, 53), arranged on the shaft (19, 51), the small pistons (39, 39A) being in contact with the disc (32, 53), characterised in that the small pistons (39) are in contact with the side, facing towards the rotor (18), of the disc (32) firmly attached to the shaft (19) and are guided in holes (40) in the casing part (10) accommodating the rotor (18), and in that the shaft (19) and the rotor (18) are firmly connected together.
  2. Hydrostatic machine according to Claim 1, characterised in that the holes (40) accommodating the small pistons (39a) are arranged so that they are located at regular distances apart on a circle.
  3. Hydrostatic machine according to Claim 1 and/or 2, characterised in that the small pistons (39) consist of a metallic material with good sliding properties.
  4. Hydrostatic machine having a rotor (18, 50, 150) which is arranged on a shaft (19, 51) and has pistons (16) arranged in radially extending holes (17), the ends of which pistons protruding from the holes slide - possibly by mean of sliding shoes (15) - on a lift cam (14), the holes being in connection via control slots (26) with passages (28, 29) (high pressure/low pressure) for the purpose of controlling the pressure medium and opening laterally at the rotor, and having a multi-part casing (10, 12, 37) for accommodating the rotor (18, 50, 150) and the passages (28, 29) and having a device (31, 52) for balancing the axial thrust exerted by the pressure medium on the rotor (18, 50, 150), which device has small pistons (39, 39a) subjected to pressure medium and a disc (32, 53), arranged on the shaft (19, 51), the small pistons (39, 39a) being in contact with the disc (32, 53), characterised in that the small pistons (39a) are in contact with the side, facing towards the rotor (50, 150), of the disc (53) firmly attached to the shaft (51) and are guided in recesses (55) of the rotor (50, 150), and in that a second disc (57) is firmly connected to the rotor (50, 150), which second disc (57) forms an axial bearing and is supported on the casing part (10) accommodating the rotor (50, 150).
  5. Hydrostatic machine according to Claim 4, characterised in that the disc (60) in effective connection with the small pistons (39A) has a cylindrical continuation (65A) by means of which it is shrunk onto the shaft (50) (Fig. 3).
  6. Hydrostatic machine according to one of Claims 4 and/or 5, characterised in that the disc (65) in effective connection with the small pistons (39A) is used for driving the rotor (150) (Fig. 4).
  7. Hydrostatic machine according to one of Claims 4 to 6, characterised in that the small pistons (39A) consist of plastic and are guided in recesses (55) which are arranged at regular distances apart on the end 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

Publications (2)

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

Family

ID=6374947

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89123243A Expired - Lifetime EP0384974B1 (en) 1989-02-25 1989-12-15 Hydrostatic machine

Country Status (3)

Country Link
US (1) US5201260A (en)
EP (1) EP0384974B1 (en)
DE (2) DE3905936A1 (en)

Families Citing this family (8)

* 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
DE4123675A1 (en) * 1991-07-17 1993-01-21 Bosch Gmbh Robert HYDROSTATIC PISTON MACHINE
DE4221705A1 (en) * 1992-07-02 1994-01-05 Voith Gmbh J M Hydrostatic machine with axial thrust compensation
DE4337508A1 (en) * 1993-11-03 1995-05-04 Rexroth Mannesmann Gmbh Radial piston motor as a plug-in motor
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)
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
CN102644575B (en) * 2012-05-07 2015-01-21 吕慧彬 Connecting rod sliding shoe type flow distribution radial plunger pump

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE877982C (en) * 1940-02-25 1953-05-28 Auto Union A G Pressure chamber sealing on injection pumps, especially for low-viscosity fuels
US2470220A (en) * 1943-09-11 1949-05-17 Int Harvester Co Pump
US2608933A (en) * 1945-09-24 1952-09-02 Oilgear Co Hydrodynamic machine
US2620733A (en) * 1946-06-19 1952-12-09 John W Overbeke Hydraulic fluid mechanism
US2972961A (en) * 1957-09-18 1961-02-28 Albert P Clark Hydrostatic lubricating apparatus
US3056357A (en) * 1958-12-01 1962-10-02 Gen Motors Corp Radial ball piston pump
CH604002A5 (en) * 1974-11-02 1978-08-31 Danfoss As
US3913454A (en) * 1974-11-18 1975-10-21 Deere & Co Hydraulic motor
DE2529473C3 (en) * 1975-07-02 1980-11-20 Danfoss A/S, Nordborg (Daenemark) Slide shoe arrangement, especially for axial and radial piston machines
AU1819076A (en) * 1977-01-13 1978-04-06 Power Train Inc Stored energy power system
US4411190A (en) * 1981-05-07 1983-10-25 Kilmer John B Energy translation device having individually compensated sliding valves and counterbalancing mechanism

Also Published As

Publication number Publication date
US5201260A (en) 1993-04-13
EP0384974A1 (en) 1990-09-05
DE3905936A1 (en) 1990-09-06
DE58905473D1 (en) 1993-10-07

Similar Documents

Publication Publication Date Title
DE1958225C3 (en) External mesh gear pump
DE2744947C3 (en) Infinitely adjustable conical pulley belt drive
DE3340333C1 (en) Swash plate axial piston pump
EP0620358A1 (en) Hydraulic motor
EP0384974B1 (en) Hydrostatic machine
DE2448594B2 (en) Axial piston machine
DE3909910C2 (en)
DE1453701A1 (en) Inclined drum axial piston motor
DE4414400C2 (en) Engine brake for a multi-cylinder internal combustion engine
EP0405161A1 (en) Screw rotor pump
DE2909248C2 (en) Working piston for a hydrostatic piston machine
DE2134026A1 (en) AXIAL PISTON MACHINE
DE2815476A1 (en) AXIAL PISTON MACHINE
DE2418164C3 (en) Radial piston machine with internal flow
EP0523384B1 (en) Hydrostatic piston machine
DE1553035C3 (en) Internal rotor gear pump with radially movable filler piece
DE2248316C2 (en) Radial piston machine
DE2914282C2 (en) Support body for the adjustable race of hydraulic pumps
DE3725156C2 (en)
CH623894A5 (en) Hydraulic screw machine
DE4134582A1 (en) RADIAL PISTON MACHINE
DE3800905A1 (en) Pump, in particular axial-piston pump
DE19544359C2 (en) Radial piston machine
DE3733625A1 (en) Axial piston machine
DE3123420A1 (en) Variable-output vane pump

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: 19901217

RAP3 Party data changed (applicant data changed or rights of an application transferred)

Owner name: ROBERT BOSCH GMBH

17Q First examination report despatched

Effective date: 19920414

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

ET Fr: translation filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19930827

REF Corresponds to:

Ref document number: 58905473

Country of ref document: DE

Date of ref document: 19931007

ITF It: translation for a ep patent filed

Owner name: STUDIO JAUMANN

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19931215

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19931215

26N No opposition filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19940831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19940901

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20051215