EP0231429B1 - Pompe à engrenages - Google Patents

Pompe à engrenages Download PDF

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Publication number
EP0231429B1
EP0231429B1 EP86111453A EP86111453A EP0231429B1 EP 0231429 B1 EP0231429 B1 EP 0231429B1 EP 86111453 A EP86111453 A EP 86111453A EP 86111453 A EP86111453 A EP 86111453A EP 0231429 B1 EP0231429 B1 EP 0231429B1
Authority
EP
European Patent Office
Prior art keywords
eccentric ring
pressure
gear pump
pump according
spring
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
Application number
EP86111453A
Other languages
German (de)
English (en)
Other versions
EP0231429A3 (en
EP0231429A2 (fr
Inventor
Kurt Sickinger
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.)
Schwaebische Huettenwerke Automotive GmbH
Original Assignee
Schwaebische Huettenwerke Automotive 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 Schwaebische Huettenwerke Automotive GmbH filed Critical Schwaebische Huettenwerke Automotive GmbH
Publication of EP0231429A2 publication Critical patent/EP0231429A2/fr
Publication of EP0231429A3 publication Critical patent/EP0231429A3/de
Application granted granted Critical
Publication of EP0231429B1 publication Critical patent/EP0231429B1/fr
Expired 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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/04—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for reversible machines or pumps

Definitions

  • the invention relates to a gear pump according to the preamble of claim 1.
  • Gear pumps of this type have an externally toothed inner rotor, which rotates within an externally eccentrically rotatable internally toothed outer rotor, which in turn is mounted in an eccentric ring.
  • the eccentric ring which determines the position of the external rotor, must be swiveled by 180 °. The easiest way to do this is to always maintain a certain frictional connection between the outer surface of the outer rotor and the inner surface of the eccentric ring, whereby the eccentric ring is always pressed against an end stop corresponding to the direction of rotation when the outer rotor is rotating.
  • the piston mentioned delimits an expansion chamber which is connected to the pressure connection of the pump via a pressure line.
  • the fluid pressure transmitted from the pressure connection to the expansion chamber acts on the piston, counteracts the spring loading it, and lifts the friction body out of the frictional engagement with the external rotor.
  • the pump briefly comes to a standstill when the direction of rotation is reversed, then the delivery pressure and thus the pressure in the expansion chamber drop, the friction body creates the frictional engagement between the eccentric ring and the outer rotor, and when starting in the opposite direction, the outer rotor takes the eccentric ring in its second End position with, in which the eccentric ring is held by a stop.
  • the build-up of the delivery pressure then acts again on the piston in the expansion chamber, so that the frictional engagement remains canceled while the pump is operating.
  • the generic pump has the disadvantage that the arrangement of a cylinder-like expansion chamber, piston, spring and friction body is relatively complicated and difficult to assemble. In addition, due to its small dimensions, the friction body is subject to increased wear. Problems also arise when, for example in trucks, viscous oil has to be pumped.
  • the piston-cylinder arrangement has a considerable radial height, as a result of which the outside diameter of the eccentric ring and thus also of the pump is enlarged. And finally, the eccentric ring is limited in its minimum thickness by the piston diameter and the required wall thickness.
  • the object of the invention is to further develop the generic pump in such a way that it is structurally simplified, the outer circumference required for the eccentric ring is reduced and the resistance to wear is increased.
  • the inner surface of the eccentric ring is again formed as a counter surface, as was the case before the generic document, so that the eccentric ring can be brought into frictional engagement with the outer rotor.
  • the eccentric ring according to the invention is provided with at least one radial slot or, in the case of a plurality of radial slots, is composed of segments so that it can be contracted and expanded radially.
  • the eccentric ring is pulled together by spring force, while the expansion takes place through the action of the expansion chamber and through hydrodynamic forging pressures, so that when the pump is working and releases pressure fluid through the pressure connection, this pressure in the expansion chamber and the pressure generated by rotation Hydrodynamic pressure is then used to expand the eccentric ring so that the frictional engagement between it and the outer surface of the outer rotor is canceled.
  • the eccentric ring is in that of its end positions which is assigned to the currently prevailing direction of rotation.
  • the eccentric ring is slotted only once or has only one continuous slot
  • the eccentric ring itself preferably consists of resilient material, such as steel, sintered material, aluminum but also plastic.
  • the spring which is intended to compress the eccentric ring is formed by the latter itself, so that the spring as a separate component can be dispensed with entirely.
  • the eccentric ring is composed of at least two segments or arc sections, according to a preferred embodiment of the invention, these arc sections are compressed by an annular spring that surrounds them from the outside.
  • This ring spring which can be inserted into a circumferential groove of the eccentric ring, forms a separate component and is itself easy to assemble.
  • a hydraulic piston can be specified as the expansion element, which bends the ends of the slotted eccentric ring apart.
  • a separate component is not absolutely necessary to achieve the expansion: for example, it is possible to form grooves in at least one of the friction surfaces, which are connected to the pressure line. If these grooves are pressurized, the eccentric ring is initially widened a little. As a result, pressure fluid can get into the annular gap that forms between the eccentric ring and the outer rotor, which then bends the eccentric ring apart.
  • the expansion chamber is delimited by the walls of the radial slot.
  • the expansion chamber is thus effective at the point at which the eccentric ring can be expanded with the least amount of force.
  • An eccentric ring can thus be used, which tightly encloses the outer rotor when it is not loaded by the expansion chamber, as a result of which a quick response to a change of direction and an error-free switching process are achieved, even with viscous fluids.
  • the two surfaces delimiting the expansion chamber are preferably used as stops in order to avoid an excessive, harmful contraction of the eccentric ring in the non-installed state.
  • these surfaces which are seated on one another are slightly inclined to one another so that the hydraulic fluid can penetrate between them.
  • these grooves or grooves are initially filled with fluid when pressure is applied, which initiates the lifting of the surfaces.
  • the space between the raised surfaces then fills with fluid so that its pressure acts on the full surface of the diaphragm walls.
  • the inner surface of the eccentric ring is left out.
  • the resulting recess is connected to the slot and is in the end positions of the eccentric ring opposite the mouth of the pressure line, so that the pocket-like recess forms part of the expansion chamber. If pressure is applied to this pressure pocket when the expansion ring is contracted, then this acts radially in the areas next to the slot on the eccentric ring and tries to expand it radially.
  • the slot opens and immediately fills with fluid, the full pressure of which can then act on the walls of the slot.
  • the expansion of the eccentric ring achieved in this way is supported by the radially acting pressure component and the hydrodynamic pressure.
  • the arrangement of a pressure pocket is also advantageous if it is not directly connected to the pressure line, but is only subjected to pressure through the gap between the diaphragm walls, since fluid passes through the pressure pocket into the increasing annular gap between the outer rotor and the eccentric ring , which helps to spread the eccentric ring away from the outer rotor and thus to abort the operating state with frictional engagement as quickly as possible when it is no longer required.
  • mouths of the pressure line are arranged at the two end positions of the eccentric ring, it is proposed according to a further embodiment of the invention to leave out a second pressure pocket opposite the first on the inner surface of the eccentric ring.
  • the second pressure pocket lies in front of the mouth of the pressure line assigned to the other end position, so that the pressurization of the annular space between the eccentric ring and the external rotor takes place from two places.
  • FIG. 1 shows an exemplary embodiment of the gear pump according to the invention in radial section and has a housing 1 with a cylindrical chamber in which an eccentric ring 2 is suitably inserted.
  • This eccentric ring 2 the cylindrical outer surface of which is centered on the axis A, has an essentially circular-cylindrical inner bore, the central axis B of which is offset from the central axis A.
  • An outer rotor 6 is accommodated in the eccentric bore of the eccentric ring 2 and has a circular cylindrical outer surface which is essentially complementary to the inner surface of the eccentric ring 2.
  • the outer rotor 6 has an inner toothing which engages in the outer toothing of an inner rotor 7, which has one tooth less than the outer rotor 6 and is centered on the axis A.
  • the eccentric ring 2 has a circumferential groove 3 which extends over a little more than 180 °, in
  • the eccentric ring 2 is separated by a radial slot 5. Adjacent to the slot 5, the inner surface of the eccentric ring 2 is recessed to form a pressure pocket 8. At this point of the pressure pocket 8 opposite the center B of the inner surface of the eccentric ring 2, this is also trough-like to form a second pressure pocket 9.
  • a pressure line 10 is recessed in the housing 1 through bores, which opens into the bottom of the receiving bore for the arrangement formed from parts 2, 6 and 7, in each case at a point which corresponds to the pressure pocket 8 or 9 faces.
  • the pressure line 10 is connected to the pressure connection of the pump.
  • the eccentric ring 2 is made of resilient material and is biased by its own spring action so that it seeks to lie closely around the outer rotor 6.
  • the walls of the slot 5 can sit one on top of the other as a force limitation, but it is equally advantageous that the walls also maintain a mutual distance in this state, so that pressure can build up quickly in the slot 5.
  • the outer surface of the outer rotor 6 and the inner surface of the eccentric ring 2 form a friction pairing, which must transmit a frictional force which is sufficient to rotate the eccentric ring 2 by 180 °.
  • the two engagement surfaces are smooth and clean.
  • it is necessary to take additional measures to increase the frictional engagement such as the arrangement of a friction lining, a suitable material pairing or a suitable honing surface treatment frictional surfaces.
  • the mode of operation of the gear pump shown is as follows: In the state shown in FIG. 1, the pump rotates in the direction of the arrow and conveys fluid.
  • the pressure line 10 and thus also the slot 5 and the pressure pockets 8 and 9 are under fluid pressure, which is effective in such a direction that the eccentric ring 2 is expanded.
  • the wedge-shaped pockets seen in the direction of rotation build up a hydrodynamic, very high oil pressure that is dependent on the speed of rotation, which supports the expansion of the eccentric ring.
  • the bearing play is automatically adjusted to a favorable level.
  • the bore in the housing 1 must be dimensioned accordingly.
  • the pump If the pump is brought to a standstill, then the pressure in the pressure outlet of the pump and thus also in the pressure line 10, the slot 5 and in the pressure pockets 8 and 9 decreases, so that those pressure forces which had previously spread the eccentric ring 2 apart, omitted.
  • the eccentric ring 2 thus lies tightly around the outer rotor 6 and engages with its outer surface in close frictional engagement.
  • the inner rotor 7 rotates the outer rotor 6 with which it is engaged, which in turn rotates the eccentric ring 2 until a stop between the end wall of the groove 3 and the pin 4 takes place.
  • the pump that continues to run begins to build up a pressure in its pressure connection, which acts via line 10 in the manner mentioned above and lifts the eccentric ring 2 again from the external rotor 6, so that smooth running and the switching process take place in a simple and robust manner can be achieved.
  • the embodiment of FIG. 3 differs from that of FIG. 2 in that the eccentric ring 2 is not designed as a one-piece, open ring, but is composed of two curved pieces, each of which forms a slot 5 at their mutual abutment points.
  • the two arc pieces forming the eccentric ring 2 have an external circumferential groove, into which an annular spring 11 is inserted, which tries to press the arc pieces in the same way against the outer surface of the outer rotor 6, as is the case in the embodiment of FIGS. 1 and 2 due to the self-suspension of the eccentric ring shown there was reached.
  • the mode of operation of the exemplary embodiment of FIGS. 3 and 4 is the same as that of the exemplary embodiments of FIGS. 1 and 2. Otherwise, the pressure line 10 is omitted in the illustration in FIG. 4 for the sake of clarity.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (8)

1. Pompe à engrenages avec direction de refoulement constante pour des sens d'entraînement variables, comprenant
a) un carter (1) avec un raccord d'aspiration et de refoulement (10) pour le fluide à pomper,
b) une roue mobile interne (7) à denture extérieure,
c) une roue mobile externe (6) à denture intérieure entourant la roue mobile interne,
d) un anneau excentrique (2) recevant la roue mobile externe pouvant être tourné de 180° et logé à son tour dans le carter,
e) un dispositif d'accouplement utilisant un effet de ressort pour la réalisation d'un entraînement par friction entre la face extérieure de la roue mobile externe (6) et une surface conjugée rattachée à l'anneau excentrique (2), et
f) un dispositif (5) communiquant avec le raccord de refoulement par l'intermédiaire d'une conduite forcée (10) et servant à débloquer le dispositif d'accouplement dès que la pression de refoulement a dépassé une valeur déterminée, caractérisée en ce que
g) l'anneau excentrique (2) soumis à une tension de ressort
g1) présente au moins une fente radiale (5),
g2) peut être poussé radialement vers l'intérieur, contre la face extérieure de la roue mobile externe (6) pour réaliser l'entraînement par friction par la tension du ressort, et
g3) peut être dégagé de la roue mobile externe (6), avec élargissement de la fente radiale (5), pour la suppréssion de l'entraînement par friction par le fluide.
2. Pompe à engrenages selon la revendication 1, caractérisée en ce que l'anneau excentrique (2) constitué d'un matériau élastique est conformé en ressort.
3. Pompe à engrenages selon la revendication 2, caractérisée en ce que l'anneau excentrique (2) est réalisé à partird'un métal, en particulierd'aluminium, d'acier nitruré, de matériau fritté ou d'une matière plastique.
4. Pompe à engrenages selon la revendication 1, caractérisée en ce que l'anneau excentrique (2) est enserré par un annueau-ressort (11).
5. Pompe à engrenages selon la revendication 4, caractérisée en ce que l'anneau excentrique (2) se compose d'au moins deux segments d'anneau et que l'anneau-ressort (11) est logé dans des rainures aménagées dans la périphérie extérieure de l'anneau excentrique (2).
6. Pompe à engrenages selon l'une des revendications 1 à 5, caractérisée en ce que dans la face interne de l'anneau excentrique (2) est conformée, dans la région de la fente radiale (5), une poche de pression (8), qui, dans les positions extrêmes de l'anneau excentrique (2), se trouve respectivement en face d'une sortie de la conduite forcée (10) évidée dans le carter (1).
7. Pompe à engrenages selon la revendication 6, caractérisée en ce que, pour un anneau excentrique (2) formé d'une seule pièce, il est prévu, en face de la poche de pression (8) dans la région de la fente radiale (5), au moins une seconde poche de pression (9) qui est respectivement ouverte en direction d'une sortie de la conduite forcée (10).
8. Pompe à engrenages selon l'une des revendications 6 ou 1, caractérisée en ce que la caractéristique de flexibilité de l'anneau excentrique (2) etrespecti- vement de l'anneau-ressort (11) est adaptée à la vitesse de rotation de telle façon que le jeu du palier hydrodynamique entre l'anneau excentrique (2) et la roue mobile externe (6) est réglé automatiquement sur une valeur favorable par la pression du fluide s'établissant dans la poche de pression (8, 9).
EP86111453A 1985-12-09 1986-08-19 Pompe à engrenages Expired EP0231429B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853543488 DE3543488A1 (de) 1985-12-09 1985-12-09 Zahnradpumpe
DE3543488 1985-12-09

Publications (3)

Publication Number Publication Date
EP0231429A2 EP0231429A2 (fr) 1987-08-12
EP0231429A3 EP0231429A3 (en) 1987-11-19
EP0231429B1 true EP0231429B1 (fr) 1988-12-28

Family

ID=6288025

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86111453A Expired EP0231429B1 (fr) 1985-12-09 1986-08-19 Pompe à engrenages

Country Status (4)

Country Link
US (1) US4743180A (fr)
EP (1) EP0231429B1 (fr)
JP (1) JPS62142881A (fr)
DE (1) DE3543488A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015112664A1 (de) * 2015-07-31 2017-02-02 Ebm-Papst St. Georgen Gmbh & Co. Kg Zahnringpumpe

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2214987B (en) * 1988-02-05 1992-09-30 Petter Refrigeration Ltd Reversible unidirectional flow gear pump.
US5085187A (en) * 1991-03-11 1992-02-04 Chrysler Corporation Integral engine oil pump and pressure regulator
HU217275B (hu) * 1994-02-24 1999-12-28 Rába Rt. Irányváltós, excentrikus zárótolattyús szivattyú, főként hajtóművek kenőanyagának áramoltatására
US5655983A (en) * 1995-04-28 1997-08-12 Dana Corporation Hydromechanical system for limiting differential speed between differentially rotating members
US5702319A (en) * 1995-10-13 1997-12-30 Dana Corporation Hydromechanical system for limiting differential speed between differentially rotating members
US5711408A (en) * 1996-05-09 1998-01-27 Dana Corporation Reversible gerotor pump
GB2342396B (en) * 1998-08-15 2002-04-24 Lucas Ind Plc Pumps
US6702703B2 (en) 2001-01-18 2004-03-09 Dana Corporation Lubrication pump for inter-axle differential
DE102014115548A1 (de) 2014-10-27 2016-04-28 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Innenzahnradpumpe und Pumpverfahren
DE102016121240A1 (de) * 2016-11-07 2018-05-09 Nidec Gpm Gmbh Elektrische Gerotorpumpe und Herstellungsverfahren für dieselbe
CN110578685A (zh) * 2019-10-21 2019-12-17 中车戚墅堰机车车辆工艺研究所有限公司 输送泵、齿轮箱、车辆及船

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3118387A (en) * 1964-01-21 Reveksible gear pump
DE1553281A1 (de) * 1963-04-30 1969-09-25 Zahnradfabrik Friedrichshafen Kapselwerk,insbesondere Raederkapselwerk
US3583839A (en) * 1969-08-20 1971-06-08 Emerson Electric Co Automatic distortion control for gear type pumps and motors
DE2742821C2 (de) * 1977-09-23 1982-11-25 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Zahnradpumpe mit bei wechselnder Antriebsrichtung gleichbleibender Förderrichtung
US4193746A (en) * 1978-02-16 1980-03-18 Westinghouse Electric Corp. Reversible gerotor pump
US4171192A (en) * 1978-05-05 1979-10-16 Thermo King Corporation Eccentric positioning means for a reversible pump
DE2936066A1 (de) * 1978-09-12 1980-03-20 Concentric Pumps Ltd Pumpe
US4222719A (en) * 1979-01-02 1980-09-16 Thermo King Corporation Reversible unidirectional fluid flow pump
US4492539A (en) * 1981-04-02 1985-01-08 Specht Victor J Variable displacement gerotor pump

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015112664A1 (de) * 2015-07-31 2017-02-02 Ebm-Papst St. Georgen Gmbh & Co. Kg Zahnringpumpe
DE102015112664C5 (de) 2015-07-31 2022-11-17 Ebm-Papst St. Georgen Gmbh & Co. Kg Zahnringpumpe

Also Published As

Publication number Publication date
DE3543488C2 (fr) 1989-04-13
US4743180A (en) 1988-05-10
JPS62142881A (ja) 1987-06-26
EP0231429A3 (en) 1987-11-19
DE3543488A1 (de) 1987-06-11
EP0231429A2 (fr) 1987-08-12

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