EP1785622B1 - Pompe hydraulique - Google Patents

Pompe hydraulique Download PDF

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Publication number
EP1785622B1
EP1785622B1 EP06023728A EP06023728A EP1785622B1 EP 1785622 B1 EP1785622 B1 EP 1785622B1 EP 06023728 A EP06023728 A EP 06023728A EP 06023728 A EP06023728 A EP 06023728A EP 1785622 B1 EP1785622 B1 EP 1785622B1
Authority
EP
European Patent Office
Prior art keywords
control
rotor
pump according
tank
pintle
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.)
Not-in-force
Application number
EP06023728A
Other languages
German (de)
English (en)
Other versions
EP1785622A1 (fr
Inventor
Marcus Fischer
Robert Saric
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.)
Weber Hydraulik GmbH Germany
Original Assignee
Weber Hydraulik GmbH Germany
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
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Publication of EP1785622A1 publication Critical patent/EP1785622A1/fr
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Publication of EP1785622B1 publication Critical patent/EP1785622B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04B1/047—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the outer ends of the cylinders
    • 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
    • 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
    • F04B1/1072—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 with cylinder blocks and actuating cams rotating together
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/02—Pumping installations or systems having reservoirs
    • F04B23/025—Pumping installations or systems having reservoirs the pump being located directly adjacent the reservoir
    • F04B23/026—Pumping installations or systems having reservoirs the pump being located directly adjacent the reservoir a pump-side forming a wall of the reservoir

Definitions

  • the invention relates to a generic pump according to the preamble of the main claim.
  • Reversible pumps for various small volume flow applications e.g., 0.5 l / min
  • high pressures e.g., up to 400 bar
  • well-defined lifetimes e.g. 150 hours
  • Pumps for applications in the mobile hydraulics such. Pumps for cab tilting systems.
  • Today's gear pumps are inexpensive, but do not reach the required pressure level and are not reversible at low flow rates.
  • valve-controlled single-piston pumps are also not reversible and ruled out due to the cost of the reversal by means of a solenoid valve and because of the high pulsation caused by the high noise level. In addition, they have a much higher than required by the market life and are therefore too expensive.
  • Known slot-controlled radial piston pumps have a rotor with radial pumping pistons and a fixed control pin with two radial control slots.
  • the rotor is rotatably mounted on the control pin.
  • the bearing point must ensure - besides the interception of the pumping forces - at the connection point between the rotor and the control plug oil-tightness.
  • a leakage is inevitable due to the design, which has a negative effect on the efficiency.
  • the rotor will jam on the control pin in the event of severe temperature fluctuations. Constant wear in the course of operation can increase the leakage, which has a negative effect on the efficiency and is highly undesirable.
  • the invention has the object of providing a generic pump easier to manufacture and assembly and thus cheaper so that it remains leaking in operation despite wear.
  • the annular channels are configured such that by the hydraulically effective, the end face of the rotor facing and next adjacent, formed by the control pin front annular surface with decreasing radius and the housing itself formed by the rear annular surface upon pressurization of the annular channel in the direction of the rotor acting resulting force results.
  • the inventive principle thus lies in the axial arrangement of the control pin on the end face of the rotor and the pressing of these two parts dependent on the operating pressure in the hydraulic system.
  • the connection point of these parts is not only relatively tight in operation and thus low in leakage; even with wear (abrasion) of the end face of the rotor, the required adjustment takes place automatically and automatically.
  • the invention provides a simpler in the production and assembly and thus more cost-effective pump, which is extremely low leakage even during operation despite wear.
  • the front face of the rotor adjacent the front annular channel and the end face of the rotor remote rear ring channel are connected via a respective transverse bore with the associated line connection of Saugrücktschventile, resulting in a particularly simple production.
  • this has a circular cylindrical shell and is the rear and front annular channel of two circumferential seals adjacent.
  • the pump unit formed by the actual hydraulic reversible pump 1, 2, 12 and the electric motor 9 flanged to it on one side thereof and driving the latter has, as shown in FIG. 1, a housing 12 on the other side of which a tank 11 for the Hydraulic fluid is attached, which is preferably formed of oil.
  • the pump is provided with two ports 13,14, of which in one direction of rotation one serves as a pressure for the supply line and the other as a line connection for the return line and -in the opposite direction of rotation - vice versa, and with a connected to the tank 11 filling port 17 provided.
  • a rotor 1 is rotatably mounted, which has three radially movable, with its outer ends on an eccentric 4 supporting the pump piston 3.
  • This eccentric bearing 4 is executed in the embodiment shown as a rolling bearing.
  • the arranged in the axial direction next to the control pin 2 rotor 1 is pressed against this in a pressureless state with the force of a spring 8.
  • On its side facing away from the end face of the rotor 1 is rotatably supported by means of two deep groove ball bearings 10 about the housing-fixed axis of rotation.
  • each piston chamber has an axially extending and in the control pin 2 facing end side of the rotor 1 opening bore 3a.
  • the control pin 2 is provided with a hardened control plate 2a with two control surfaces (FIG. 2A) formed as control rods 2b, 2c or alternatively with two bores 2b, 2c (FIG. 2B) which abut against the end face of the rotor 1 in such a way that they act during the control Rotation of the rotor 1 with the opening into the end face of the rotor 1 Holes 3a are temporarily aligned.
  • the control pin 2 are also two with their tank facing tank port 5c, 6c with a tank 11 and with its tank 11 remote line connection 5d, 6d with one of the control surfaces 2b, 2c and one of the two ports 13,14 connected Saug Kohltschventile 5.6 provided.
  • the line connection 5d of the one-rear suction check valve 5 is connected to a provided between the housing 12 and the jacket of the control pin 2 disposed therein, circumferential, rear annular channel 5a via an associated transverse bore 5b.
  • the line connection 6d of the -vorderen- Saugrücktschventils 6 is connected to a provided between the housing 12 and the jacket of the control pin 2 disposed therein, circumferential, front annular channel 6a via an associated transverse bore 6b.
  • FIG. 6 shows another embodiment of the suction check valve 5, 6, whose two valve balls on each valve seat seal the through-channel, which extends between the two valve seats and open into the tank via a branch channel which is not described in more detail.
  • the two valve balls are controlled by a valve stem 19 so that when closing the one Saug Wegtschventils 5, i. with resting on the valve seat valve ball, the valve ball of the other suction check valve 6 is lifted by the valve stem 19 from its seat and thus opened, so either only one or the other suction check valve open and the other is closed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (16)

  1. Pompe hydraulique, de préférence entraînée par un moteur électrique (9) comportant deux raccords (13, 14), parmi lesquels, dans un sens de rotation, l'un desdits raccords fait office de raccord de pression et l'autre fait office de raccord d'aspiration et, dans le sens de rotation opposé, on obtient la situation inverse, laquelle pompe comporte un tourillon de commande (2) résistant à la rotation par rapport à un boîtier (12) et un rotor (1) pouvant tourner autour d'un axe de rotation fixe par rapport au boîtier, présentant plusieurs, de préférence trois, pistons de pompe (3) mobiles radialement, reposant avec leurs extrémités externes sur un palier excentrique (4), dont les extrémités internes obturent chacun respectivement un espace de piston - présentant un volume variable -, moyennant quoi le tourillon de commande (2) présente deux surfaces de commande (2b, 2c), jouxte le rotor (1) dans la direction axiale et est adjacent, avec les deux surfaces de commande (2b, 2c), à l'une des faces frontales du rotor, moyennant quoi il est respectivement prévu un alésage (3a) relié à chaque espace de piston, s'étendant axialement - parallèlement à l'axe de rotation -, et débouchant au niveau de la face frontale du rotor (1), caractérisée en ce que:
    - dans le boîtier est disposé un réservoir (11),
    - dans le tourillon de commande (2) est prévu un premier clapet antiretour d'aspiration (5), pouvant être relié, au niveau de son premier raccord de réservoir (5c), orienté vers le réservoir, avec le réservoir (11) et, au niveau de son premier raccord de conduite (5d), opposé au réservoir (11), aussi bien avec l'une des surfaces de commande (2b, 2c) qu'avec l'un des deux raccords (13, 14), ainsi qu'un deuxième clapet antiretour d'aspiration pouvant être relié, au niveau de son deuxième raccord de réservoir (6c) orienté vers le réservoir, avec le réservoir (11) et, au niveau de son deuxième raccord de conduite (6d) opposé au réservoir (11), aussi bien avec l'autre des surfaces de commande (2b, 2c) qu'avec l'autre des deux raccords (13, 14),
    - et en ce que chacun, à savoir le premier et le deuxième raccord de conduite (5d, 6d) de chaque clapet antiretour d'aspiration (5, 6), à savoir le premier et deuxième clapet antiretour d'aspiration, est raccordé respectivement à un canal annulaire avant (6a) ou arrière (5a) périphérique, prévu entre le boîtier (12) et l'enveloppe du tourillon de commande (2) disposé à l'intérieur, dont la surface annulaire avant (15), délimitant le canal annulaire au niveau de sa face la plus proche de la surface frontale du rotor (1), est formée par une zone du tourillon de commande (2) ayant un rayon décroissant, et dont la surface annulaire arrière (16), délimitant le canal annulaire au niveau de sa face éloignée de la surface frontale du rotor (1), est formée une zone du boîtier (12).
  2. Pompe selon la revendication 1, caractérisée en ce que le canal annulaire avant (6a), le plus proche de la surface frontale du rotor (1), ainsi que le canal annulaire arrière (5a), éloigné de la surface frontale du rotor (1), sont reliés respectivement par l'intermédiaire d'un alésage transversal (5b, 6b) avec le raccord de conduite (5d, 6d) associé des clapets antiretour d'aspiration (5, 6).
  3. Pompe selon la revendication 1 ou 2, caractérisée en ce que le tourillon de commande (2) présente une enveloppe en forme de cylindre circulaire, et le canal annulaire arrière et avant (5a, 6a) est entouré, de chaque côté, par un joint d'étanchéité périphérique (9a, 9b, 9c).
  4. Pompe selon l'une quelconque des revendications 1 à 3, caractérisée en ce que le tourillon de commande présente, en tant que surfaces de commande (2b, 2c), deux nodules de commande.
  5. Pompe selon l'une quelconque des revendications 1 à 3, caractérisée en ce que le tourillon de commande présente, en tant que surfaces de commande (2b, 2c), deux alésages de commande.
  6. Pompe selon l'une quelconque des revendications 1 à 5, caractérisée en ce que le tourillon de commande (2) présente une plaque porte-clapet (2a) et en ce que les surfaces de commande (2b, 2c) du tourillon de commande (2) sont disposées à l'intérieur de la plaque porte-clapet (2a).
  7. Pompe selon la revendication 6, caractérisée en ce que le rotor (1) présente une plaque porte-clapet, et celle-ci présente une rigidité différente de celle de la plaque porte-clapet (2a) du tourillon de commande (2).
  8. Pompe selon l'une quelconque des revendications 1 à 7, caractérisée en ce que, à l'état exempt de pression, le rotor (1) disposé à côté du tourillon de commande (2) dans la direction axiale et le tourillon de commande (2) sont appuyés l'un contre l'autre sous la force d'un ressort (8).
  9. Pompe selon l'une quelconque des revendications 1 à 8, caractérisée en ce que le palier excentrique (4) est configuré sous la forme d'un palier lisse ou d'un palier à roulement.
  10. Pompe selon l'une quelconque des revendications 1 à 9, caractérisée en ce que le rotor (1) est disposé de manière à pouvoir tourner sur sa face opposée à la face frontale à l'aide d'au moins un palier axial (10).
  11. Pompe selon l'une quelconque des revendications 1 à 9, caractérisée en ce que le rotor (1) est disposé de manière à pouvoir tourner, sur sa face opposée à la face frontale, à l'aide d'au moins un palier radial (10).
  12. Pompe selon la revendication 10 ou 11, caractérisée en ce que le palier axial et/ou le palier radial est configuré sous la forme d'un roulement à billes rainuré (10).
  13. Pompe selon la revendication 1, caractérisée en ce qu'elle est configurée sous la forme d'une pompe à mouvement de va-et-vient.
  14. Pompe selon la revendication 1, caractérisée en ce que le réservoir (11) est adjacent au tourillon de commande (2) au niveau de sa face opposée au rotor (1).
  15. Pompe selon la revendication 1, caractérisée en ce que les deux clapets antiretour (5, 6) disposés dans le tourillon de commande (2) présentent chacun une bille de clapet disposée sur un siège de clapet, qui étanchéifie le canal de passage respectif s'étendant entre les deux sièges de clapet et débouchant dans le réservoir, et en ce que les deux billes de clapet sont commandées par un poussoir de clapet (19) de telle sorte que, lors de la fermeture de l'un des clapets antiretour d'aspiration (5) avec la bille de clapet reposant sur le siège de clapet, chaque bille de clapet de l'autre clapet antiretour d'aspiration (6) est amenée à se soulever de son siège par le poussoir de clapet (19), et s'ouvre donc.
  16. Pompe selon la revendication 15, caractérisée en ce que le canal de passage s'étendant entre les deux sièges de clapet débouche dans le réservoir (11) par l'intermédiaire d'un canal de liaison.
EP06023728A 2005-11-15 2006-11-15 Pompe hydraulique Not-in-force EP1785622B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005054873A DE102005054873B4 (de) 2005-11-15 2005-11-15 Hydraulische Pumpe

Publications (2)

Publication Number Publication Date
EP1785622A1 EP1785622A1 (fr) 2007-05-16
EP1785622B1 true EP1785622B1 (fr) 2008-01-23

Family

ID=37700912

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06023728A Not-in-force EP1785622B1 (fr) 2005-11-15 2006-11-15 Pompe hydraulique

Country Status (4)

Country Link
EP (1) EP1785622B1 (fr)
AT (1) ATE384870T1 (fr)
BR (1) BRPI0603632A (fr)
DE (2) DE102005054873B4 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011013108A1 (de) 2011-03-04 2012-09-06 Weber-Hydraulik Gmbh Pumpe sowie deren Verwendung
DE102011109268C5 (de) * 2011-08-03 2016-08-25 Hoerbiger Automotive Komfortsysteme Gmbh Hydraulik-Kleinaggregat geringer Förderleistung
DE102012010616A1 (de) 2012-05-30 2013-12-05 Weber-Hydraulik Gmbh Pumpe sowie deren Verwendung
TWM533845U (en) * 2016-06-06 2016-12-11 Cooler Master Technology Inc Pressurized infusion device and liquid cooling system
CN107762844A (zh) * 2017-11-29 2018-03-06 徐州科源液压股份有限公司 带前置轴承式齿轮油泵

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3028814A (en) * 1957-10-17 1962-04-10 Houdaille Industries Inc High speed variable displacement pump
GB2086991A (en) * 1980-08-26 1982-05-19 Staffa Products Ltd Improvements in and relating to hydraulic motors
DE3701857A1 (de) * 1987-01-23 1988-08-04 Teves Gmbh Alfred Radialkolbenpumpe
DE4004932C2 (de) * 1990-02-16 1995-04-13 Rexroth Mannesmann Gmbh Radialkolbenmaschine
DE4037455C1 (fr) * 1990-11-24 1992-02-06 Mannesmann Rexroth Gmbh, 8770 Lohr, De
DE19514749A1 (de) * 1995-04-21 1996-10-24 Bosch Gmbh Robert Hydrostatische Radialkolbenpumpe
DE19730499B4 (de) * 1997-07-16 2005-03-17 Weber-Hydraulik Gmbh Hydraulische Kippvorrichtung

Also Published As

Publication number Publication date
DE102005054873A1 (de) 2007-05-16
EP1785622A1 (fr) 2007-05-16
DE502006000315D1 (de) 2008-03-13
ATE384870T1 (de) 2008-02-15
BRPI0603632A (pt) 2007-08-14
DE102005054873B4 (de) 2007-08-09

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