EP0384974A1 - Machine hydrostatique - Google Patents

Machine hydrostatique 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
Authority
EP
European Patent Office
Prior art keywords
rotor
shaft
pistons
bores
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.)
Granted
Application number
EP19890123243
Other languages
German (de)
English (en)
Other versions
EP0384974B1 (fr
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/fr
Application granted granted Critical
Publication of EP0384974B1 publication Critical patent/EP0384974B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
EP89123243A 1989-02-25 1989-12-15 Machine hydrostatique Expired - Lifetime EP0384974B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3905936A DE3905936A1 (de) 1989-02-25 1989-02-25 Hydrostatische maschine
DE3905936 1989-02-25

Publications (2)

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

Family

ID=6374947

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89123243A Expired - Lifetime EP0384974B1 (fr) 1989-02-25 1989-12-15 Machine hydrostatique

Country Status (3)

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

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 (zh) * 2011-06-16 2012-08-01 兰州理工大学 七星单作用活塞缸偏置式径向柱塞马达
CN102644575A (zh) * 2012-05-07 2012-08-22 吕慧彬 连杆滑靴式配流径向柱塞泵

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4123675A1 (de) * 1991-07-17 1993-01-21 Bosch Gmbh Robert Hydrostatische kolbenmaschine
DE4123674C2 (de) * 1991-07-17 2002-07-11 Bosch Gmbh Robert Hydrostatische Kolbenmaschine
DE4221705A1 (de) * 1992-07-02 1994-01-05 Voith Gmbh J M Hydrostatische Maschine mit axialem Schubausgleich
GB9525028D0 (en) * 1995-12-06 1996-02-07 Unipat Ag Hydrostatic piston machine
DE19959020A1 (de) * 1999-12-08 2001-06-13 Bosch Gmbh Robert Hydroaggregat mit zumindest einer Verdrängermaschine, insbsondere mit einer Radialkolbenmaschine (Pumpen oder Motor)
SK288973B6 (sk) * 2020-08-13 2022-06-30 Up-Steel, S.R.O. Radiálny piestový rotačný stroj

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE877982C (de) * 1940-02-25 1953-05-28 Auto Union A G Druckraumabdichtung an Einspritzpumpen, insbesondere fuer niederviskose Kraftstoffe
FR2289771A1 (fr) * 1974-11-02 1976-05-28 Danfoss As Pompe a pistons radiaux
DE2748455A1 (de) * 1977-01-13 1978-07-20 Power Train Inc Hydro-rotationsmaschine

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
US3913454A (en) * 1974-11-18 1975-10-21 Deere & Co Hydraulic motor
DE2529473C3 (de) * 1975-07-02 1980-11-20 Danfoss A/S, Nordborg (Daenemark) Gleitschuhanordnung, insbesondere für Axial- und Radialkolbenmaschinen
US4411190A (en) * 1981-05-07 1983-10-25 Kilmer John B Energy translation device having individually compensated sliding valves and counterbalancing mechanism

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE877982C (de) * 1940-02-25 1953-05-28 Auto Union A G Druckraumabdichtung an Einspritzpumpen, insbesondere fuer niederviskose Kraftstoffe
FR2289771A1 (fr) * 1974-11-02 1976-05-28 Danfoss As Pompe a pistons radiaux
DE2748455A1 (de) * 1977-01-13 1978-07-20 Power Train Inc Hydro-rotationsmaschine

Cited By (5)

* 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 (zh) * 2011-06-16 2012-08-01 兰州理工大学 七星单作用活塞缸偏置式径向柱塞马达
CN102619675B (zh) * 2011-06-16 2014-07-23 兰州理工大学 七星单作用活塞缸偏置式径向柱塞马达
CN102644575A (zh) * 2012-05-07 2012-08-22 吕慧彬 连杆滑靴式配流径向柱塞泵
CN102644575B (zh) * 2012-05-07 2015-01-21 吕慧彬 连杆滑靴式配流径向柱塞泵

Also Published As

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

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