EP0808421B1 - Pompe hydrostatique ajustable - Google Patents

Pompe hydrostatique ajustable Download PDF

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Publication number
EP0808421B1
EP0808421B1 EP96900534A EP96900534A EP0808421B1 EP 0808421 B1 EP0808421 B1 EP 0808421B1 EP 96900534 A EP96900534 A EP 96900534A EP 96900534 A EP96900534 A EP 96900534A EP 0808421 B1 EP0808421 B1 EP 0808421B1
Authority
EP
European Patent Office
Prior art keywords
control
pump
rotor
adjustable
piston
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
EP96900534A
Other languages
German (de)
English (en)
Other versions
EP0808421A1 (fr
Inventor
Walter Robeller
Volkmar Leutner
Dieter Bertsch
Michael 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 EP0808421A1 publication Critical patent/EP0808421A1/fr
Application granted granted Critical
Publication of EP0808421B1 publication Critical patent/EP0808421B1/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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • 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
    • F04B1/06—Control
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
    • F04B49/128—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the cylinders, e.g. by moving a cylinder block

Definitions

  • the invention is based on an adjustable hydrostatic pump according to the genus of the main claim.
  • a pump is in one Training as a radial piston pump known as Adjusting member a cam ring is provided, the Eccentricity as the decisive factor for the Pump adjustment or the pump swivel viewed becomes.
  • the cam ring is here of two different sizes, hydraulic adjusting piston held in position, the larger adjusting piston being part of a hydromechanical adjustment device.
  • the Noise development in such a piston pump is very much from the rigidity of the hydraulic clamping of the adjusting element, the cam ring, depending.
  • the Noise development decreases with decreasing stiffness hydraulic clamping of the cam ring and is by the portions of the Engine forces caused.
  • a radial piston machine is known from DE 37 00 573 A1 known in which an additional pressure chamber in the control pin via a throttled connection from the high pressure side is rechargeable.
  • an additional pressure chamber in the control pin via a throttled connection from the high pressure side is rechargeable.
  • JP-A 22 38 179 is an adjustable one hydrostatic pump in one design as an axial piston pump known, also with a noise reduction is sought.
  • the pump has a first Adjustment device for adjusting the stroke of the pump second adjustment device for noise reduction is used and the actuating cylinder via a electrohydraulic control valve is controllable.
  • This Pump builds with two adjustment devices and electrohydraulic control elements that depend on Angle of rotation of the pump can be controlled, relatively expensive.
  • the adjustable hydrostatic pump according to the invention has the characteristic features of the main claim on the other hand the advantage that the noise of the Pump is significantly reduced by the influence of the acting on the hydraulic clamping of the adjusting element Share of engine power is reduced, this is counteracted.
  • the control piston with an additional control device additional pressure signal from the angle of rotation of the pump is dependent on the engine Oscillations and thus the operating noise are favorable influenced. This influence or reduction goes far beyond a measure that is related to the constructive design of the adjusting member or the adjusting piston and the Adjustment device would be possible.
  • the Additional control device for active noise reduction deal with purely hydromechanical functional elements realize, making a relatively simple, space-saving and inexpensive construction is possible.
  • FIG. 1 shows a section through a clockwise rotating radial piston pump
  • Figure 2 shows a longitudinal section by the radial piston pump according to FIG. 1
  • FIG. 3 Diagram showing the Engine power in the direction of adjustment depending on Represents angle of rotation
  • Figure 4 is part of a Cross-section according to IV-IV in Figure 2.
  • FIG. 1 shows one in conjunction with FIG Radial piston pump 10, the housing 11 on one side is closed by a lid 12.
  • the housing 11 In the housing 11 is a central, continuous longitudinal bore 13 is formed as well an adjoining cylindrical recess 14.
  • a control pin 15 In the longitudinal bore 13 a control pin 15 is attached, which protrudes into the housing recess 14.
  • a rotor 16 On this part of the control pin 15, a rotor 16 is slidably mounted in which a plurality of radially extending cylinder bores 17th are formed in which working pistons 18 slide.
  • This Working pistons 18 are articulated with sliding shoes 19 connected with their shoe soles on the Support the inner surface 21 of a cylindrical cam ring 22, which is adjustably arranged in the housing recess 14 is. Due to the eccentric position of the as an adjusting element serving lifting ring 22, as can be seen in Figure 1, 18 strokes are given to the working pistons.
  • the slide shoes 19 are tied to the lifting ring 22 Retaining rings 23, 24 are provided.
  • control pin 15 In the control pin 15 are in the plane of the piston bores 17th two control slots 25, 26 formed, which also over formed in the control pin 15 longitudinal channels 27, 28 and Breakthroughs, of which only the top in Figure 2 Breakthrough 29 is shown with radial in the housing 11 running, outwardly penetrating channels are connected, which are designed here as suction channel 31 and pressure channel 32 are. On the control pin 15 are between the Control slots 25, 26 webs with 33, 34 denotes at which the dead center for the Rotary motion.
  • the radial piston pump 10 is hydraulic Hubring adjustment trained that a pure Has hydromechanical adjustment device 35.
  • Adjusting piston arranged on the outer circumference of the cam ring 22nd in two diametrically opposite positions act. The is in a manner known per se smaller actuating piston 36 via a channel 38 always from the High pressure side 32 acted upon.
  • the larger control piston 37 delimits a pressure chamber 39 which is connected to the housing 11 flanged pressure regulator 41 from its regulating slide 42 shut off, connected to the high pressure side 32 or for Low pressure side 31 is relieved, as in itself Radial piston pumps with hydraulic cam ring adjustment is known.
  • the rotor 16 designed here as a cylindrical star is over a universal joint coupling 43 from a drive shaft 44 driven, which in the cover 12 in a double ball bearing 45 is stored.
  • the throttle bore 53 is outside the Angular range of the control grooves 55 through the inner wall 54 of the Cylinder star 16 completed. According to the im Cylinder star 16 are present, seven working pistons 18 thus a total of fourteen control grooves 55 in the inner wall 54 arranged.
  • the mode of operation of the adjustable radial piston pump 10 is explained as follows, its basic function with the adjustment of the lifting ring 22 by the hydromechanical adjustment device 35 being assumed to be known per se.
  • the stroke ring 22 is raised to the left via the adjusting device 35.
  • the cam ring 22 is supported on the large actuating piston 37 due to the centering engine forces. Every time one of the working pistons 18 dips into or emerges from the high-pressure side at the control slot 26, the supporting force F s on the large actuating piston 37 experiences a jump in the amount of a piston force downward. This can be illustrated with the aid of FIG.
  • a pressure change in the large actuating piston 37 is now brought about in synchronism with the force jumps by opening and closing control cross sections with the aid of the additional control device 47, this additional control device 47 being connected in parallel with the actual pressure regulator 41.
  • the additional control device 47 is integrated with the help of the throttle bore 53 in the control pin 15 and the control grooves 55 in the rotor 16, because in this way the required relative movement and synchronization are already provided.
  • the additional control device 47 when the working piston 18 "emerges from the high-pressure side 26, the additional control device 47 also opens a control cross section for the return and the pressure in the actuating cylinder 39 is reduced, in order to reduce the effect of the force jump 59
  • the operation of the additional control device 47 is adapted to the hydraulic stroke adjustment in such a way that, despite the delays caused by the hydromechanical adjustment device, a temporal collision of the force jump from the engine and Counteraction on the actuating piston 37 is ensured.

Claims (10)

  1. Pompe hydrostatique réglable, en particulier pompe à piston ou pompe à cellules semi-rotative, comprenant un carter dans lequel est disposé un rotor qui coopère avec un arbre d'entraínement, rotor qui présente des évidements, dans lesquels sont guidés de façon glissante des éléments de pompe qui prennent appui par leurs extrémités faisant saillie hors du rotor sur un organe de réglage qui produit un soulèvement, organe de réglage sur lequel agit pour effecteur le réglage au moins un piston de réglage qui délimite une chambre de pression, d'un dispositif hydraulique de réglage et comprenant un corps de commande dans lequel sont constituées des fentes de commande séparées les unes des autres, associées au côté haute pression et au côté basse pression,
    caractérisée en ce qu'
    on prévoit un dispositif de commande additionnel (47) hydromécanique qui commande en parallèle au dispositif de réglage (35) dans la chambre de pression (39) associée au piston de réglage (37) une variation de la pression d'une manière synchrone par rapport aux sauts de force (58, 59) qui se produisent sur le piston de réglage (37).
  2. Pompe réglable selon la revendication 1,
    caractérisée en ce que
    le dispositif de commande additionnel (47) est formé par le rotor (16) et le corps de commande correspondant (15) qui sont mobiles l'un par rapport à l'autre.
  3. Pompe réglable selon la revendication 1 ou 2,
    caractérisée en ce que
    le dispositif de commande additionnel (47) est monté dans une liaison de commande (48) qui va de la chambre de pression (39) au circuit de retour.
  4. Pompe réglable selon la revendication 1 à 3,
    caractérisée en ce que
    le dispositif de commande additionnel (47) présente des rainures de commande (55) disposées dans le rotor (16), au moins une rainure de commande (55) qui est déchargée vers le circuit de retour, étant associée à chaque élément de pompe (18) lesquelles rainures de commande (55) coopérant avec au moins un évidement de commande (53) qui est solidaire du carter, dans le corps de commande (15) qui est en liaison avec la chambre de pression (39) et
    des rainures de commande (55) et l'évidement de commande (53) sont ajustés l'un à l'autre quant à leur position angulaire, vu dans le sens de rotation, de telle sorte que lors de chaque immersion et de chaque émersion d'un élément de pompe (18) dans le côté haute pression (26) une section transversale de commande (55, 53) soit commandée dans le dispositif de commande additionnel (47).
  5. Pompe réglable selon la revendication 1 à 4,
    caractérisée en ce qu'
    elle est constituée comme une pompe à pistons radiaux (10) avec une bague de soulèvement (22) comme organe de réglage, dans lequel des pistons de travail (18) sont respectivement disposés comme éléments de pompe dans des alésages radiaux (17) du rotor (16), éléments de pompe qui prennent appui par l'intermédiaire de patins (19) sur le pourtour intérieur de la bague de soulèvement (22) et dans lequel le rotor (16) est monté sur un tourillon de commande (15) qui sert de corps de commande, tourillon dans lequel les fentes de commande (25, 26) se trouvent en liaison avec un canal d'aspiration (31) ou un canal sous pression (32), et avec deux pistons de réglage (36, 37) de diamètres différents qui agissent en des endroits diamétralement opposés sur le pourtour extérieur de la bague de soulèvement (22), pistons de réglage (36, 37) dont le plus petit, le piston (36) est alimenté en permanence par le côté haute pression (26) de la pompe et dont le plus grand, le piston (37) peut être relié par l'intermédiaire d'un dispositif de réglage hydromécanique (41) au côté haute pression (26) ou au côté basse pression (25).
  6. Pompe réglable selon la revendication 5,
    caractérisée en ce que
    les rainures de commande (55) du dispositif de commande additionnel (47) se trouvent réparties dans la paroi intérieure du rotor (16) le long du pourtour et sont ouvertes en direction de l'une de ses faces frontales et
    dans la surface enveloppe du tourillon de commande (15) on dispose en tant qu'évidement de commande au moins un alésage radial d'étranglement (53) qui est en liaison par l'intermédiaire d'un canal solidaire du carter (51, 49) avec la chambre de pression (39) sur le grand piston de réglage (37).
  7. Pompe réglable selon la revendication 6,
    caractérisée en ce que
    dans un rotor (16) à sept pistons (18) on dispose quatorze rainures de commande (55) correspondantes.
  8. Pompe réglable selon l'une des revendication 5 à 7,
    caractérisée en ce que
    le dispositif de commande additionnel (47) commande en synchronisme avec les sauts de force une chute de la pression dans la chambre de pression (39).
  9. Pompe réglable selon l'une des revendication 1 à 4,
    caractérisée en ce qu'
    elle est constituée sous la forme d'une pompe à pistons axiaux selon le mode de construction à disques de nutation, mode de construction dans lequel le rotor est constitué sous la forme d'un tambour cylindrique, l'organe de réglage sous la forme d'un disque de nutation réglable et le corps de commande sous la forme d'un disque de commande, le dispositif de commande additionnel étant intégré dans le tambour cylindrique et dans le disque de commande.
  10. Pompe réglable selon l'une des revendications 1 à 4,
    caractérisée en ce qu'
    elle est constituée sous la forme d'une pompe à cellules semi-rotative et
    le dispositif de commande additionnel est intégré dans un rotor et dans une plaque de commande située du côté frontal.
EP96900534A 1995-02-09 1996-01-20 Pompe hydrostatique ajustable Expired - Lifetime EP0808421B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19504220 1995-02-09
DE19504220A DE19504220A1 (de) 1995-02-09 1995-02-09 Verstellbare hydrostatische Pumpe
PCT/DE1996/000081 WO1996024766A1 (fr) 1995-02-09 1996-01-20 Pompe hydrostatique ajustable

Publications (2)

Publication Number Publication Date
EP0808421A1 EP0808421A1 (fr) 1997-11-26
EP0808421B1 true EP0808421B1 (fr) 1999-05-19

Family

ID=7753516

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96900534A Expired - Lifetime EP0808421B1 (fr) 1995-02-09 1996-01-20 Pompe hydrostatique ajustable

Country Status (7)

Country Link
US (1) US5980215A (fr)
EP (1) EP0808421B1 (fr)
JP (1) JPH10513525A (fr)
KR (1) KR100382129B1 (fr)
CN (1) CN1077958C (fr)
DE (2) DE19504220A1 (fr)
WO (1) WO1996024766A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110630461A (zh) * 2019-09-24 2019-12-31 邵玉强 一种变量径向柱塞泵
DE102019110762A1 (de) * 2019-04-25 2020-10-29 Hoerbiger Automotive Komfortsysteme Gmbh Schlitzgesteuerte Radialkolbenpumpe

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DE19818396C2 (de) * 1998-04-24 2001-08-16 Bosch Gmbh Robert Radialkolbenpumpe mit asymmetrischen Gleitsteinen
US6343250B1 (en) 2000-05-19 2002-01-29 Caterpillar Inc. Method and apparatus for smoothing the output of a hydrostatic transmission near zero speed
US6817438B2 (en) * 2001-04-03 2004-11-16 Visteon Global Technologies, Inc. Apparatus and a method for adjusting fluid movement in a variable displacement pump
US6470992B2 (en) * 2001-04-03 2002-10-29 Visteon Global Technologies, Inc. Auxiliary solenoid controlled variable displacement power steering pump
US6916158B2 (en) * 2003-04-30 2005-07-12 Actuant Corporation Radial piston pump
CA2581120C (fr) * 2004-09-20 2013-10-15 Magna Powertrain Inc. Procede et mecanisme de regulation de vitesse d'une pompe
DE502006002760D1 (de) 2005-10-06 2009-03-19 Joma Hydromechanic Gmbh Flügelzellenpumpe
DE102005048602B4 (de) * 2005-10-06 2011-01-13 Joma-Polytec Kunststofftechnik Gmbh Flügelzellenmaschine, insbesondere Flügelzellenpumpe
EP1931879B1 (fr) 2005-10-06 2009-11-04 Joma-Polytec Kunststofftechnik GmbH Pompe a palettes coulissantes
DE502006004164D1 (de) 2005-10-06 2009-08-20 Joma Hydromechanic Gmbh Flügelzellenpumpe
DE502006008468D1 (de) 2006-10-10 2011-01-20 Joma Polytec Gmbh Flügelzellenmaschine, insbesondere flügelzellenpumpe
DE102010034896B3 (de) 2010-08-16 2011-07-28 Alke, Knut, 37520 Hydraulikpumpe, Getriebe daraus und Fahrzeug mit dem Getriebe
JP5620882B2 (ja) * 2011-05-23 2014-11-05 日立オートモティブシステムズ株式会社 可変容量形ポンプ
CN102606438A (zh) * 2012-03-29 2012-07-25 北京市三一重机有限公司 一种水泵
CN104196720B (zh) * 2014-07-07 2016-04-13 西安交通大学 一种变量叶片泵排量调节用交流伺服电机驱动装置
CN104153958B (zh) * 2014-07-07 2016-06-29 西安交通大学 一种径向柱塞泵的排量调节用交流伺服电机驱动装置
CN106194637B (zh) * 2016-07-27 2018-04-17 西安交通大学 一种伺服电机直接驱动变量的浮杯式径向柱塞泵
CN106224191B (zh) * 2016-07-27 2018-04-17 西安交通大学 一种浮杯式滑靴结构的径向柱塞变量泵
CN106246488B (zh) * 2016-07-27 2018-04-17 西安交通大学 一种双列柱塞的伺服电机驱动变量的浮杯式径向柱塞泵
CN108590995A (zh) * 2018-04-11 2018-09-28 王长健 变量泵及液压系统
DE102019215830A1 (de) * 2019-10-15 2021-04-15 Robert Bosch Gmbh Verdrängerpumpe und Verfahren zum Betreiben einer Verdrängerpumpe

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DE2720306C2 (de) * 1977-05-06 1986-02-27 Robert Bosch Gmbh, 7000 Stuttgart Verdrängermaschine
JPS6131675A (ja) * 1984-07-24 1986-02-14 Nippon Denso Co Ltd 可変容量ポンプ
JPS6155386A (ja) * 1984-08-24 1986-03-19 Nissan Motor Co Ltd 可変容量ポンプのライン圧制御システム
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DE3700573A1 (de) * 1987-01-10 1988-07-21 Bosch Gmbh Robert Kolbenmaschine, insbesondere axial- oder radialkolbenmaschine
JPH02238179A (ja) * 1988-11-17 1990-09-20 Daikin Ind Ltd 可変容量形ポンプ
DE4135904A1 (de) * 1990-11-06 1992-05-21 Teves Gmbh Alfred Kolbenpumpe, insbesondere radialkolbenpumpe
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019110762A1 (de) * 2019-04-25 2020-10-29 Hoerbiger Automotive Komfortsysteme Gmbh Schlitzgesteuerte Radialkolbenpumpe
CN110630461A (zh) * 2019-09-24 2019-12-31 邵玉强 一种变量径向柱塞泵

Also Published As

Publication number Publication date
CN1077958C (zh) 2002-01-16
JPH10513525A (ja) 1998-12-22
WO1996024766A1 (fr) 1996-08-15
DE59601946D1 (de) 1999-06-24
CN1173912A (zh) 1998-02-18
EP0808421A1 (fr) 1997-11-26
KR19980702023A (ko) 1998-07-15
DE19504220A1 (de) 1996-08-14
KR100382129B1 (ko) 2003-08-21
US5980215A (en) 1999-11-09

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