EP0211723A1 - Purely hydraulic action device for the hydrostatic compensation of hydraulic gear pumps and motors - Google Patents

Purely hydraulic action device for the hydrostatic compensation of hydraulic gear pumps and motors Download PDF

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Publication number
EP0211723A1
EP0211723A1 EP86401502A EP86401502A EP0211723A1 EP 0211723 A1 EP0211723 A1 EP 0211723A1 EP 86401502 A EP86401502 A EP 86401502A EP 86401502 A EP86401502 A EP 86401502A EP 0211723 A1 EP0211723 A1 EP 0211723A1
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EP
European Patent Office
Prior art keywords
seal
pump
groove
compensation
pressure
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EP86401502A
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German (de)
French (fr)
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EP0211723B1 (en
Inventor
Roger Laumont
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Hydroperfect International Inc
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Hydroperfect International Inc
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Priority to AT86401502T priority Critical patent/ATE46017T1/en
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    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

  • the present invention relates to gear pumps or motors whose pinions carried by shafts are arranged between two bearings which are applied under pressure against the lateral faces of the pinions.
  • compensation chambers are delimited by partitions placed in grooves, these partitions forming, so to speak, joints between the pads and the covers. It is the same in French patent 1,598,392 which uses seals arranged in grooves of the pump or motor body, these joints delimiting chambers of complex shape in which liquid is brought to a pressure which corresponds to that which is exerted on the opposite face of the bearing, that is to say that facing the pinions.
  • the invention solves this problem by making it possible to exert compensation pressures over the entire useful surface of the bearings of a pump or of a motor and this whatever the direction of rotation of the pinions, this pressure also being exerted on the entire surface of the seal delimiting the balancing pressure zones.
  • the hydrostatic compensation device for a pump or hydraulic gear motor in which at least one pinion support bearing is slidably mounted in the pump body and delimits with a cover of the pump body of the compensation chambers bordered by at least one seal and in which a pressure is developed to maintain the bearing applied against the lateral face of the gears is characterized in that the seal has a U-section to delimit a groove placed in communication with a high pressure prevailing in the pump or the motor.
  • the following description refers to a hydraulic gear pump which is designed to operate in either of the two possible directions of rotation.
  • the pump comprises a body 1 delimiting a cavity 2 of ovoid shape.
  • the body 1 is closed on each of its two sides by covers 3, 4 which are connected to it by centering pins 5.
  • the cavity 2 contains bearings or bearings 6, 7 which can slide with gentle friction.
  • the bearings 6, 7 support driving shafts 8 and driven 9 on which pinions 8a and 9a are fixed.
  • the shaft 8 constituting the driving shaft projects from the cover 3 while the shaft 9 is completely included inside the pump.
  • the bearings or bearings 6, 7 respectively called front bearing and rear bearing have an 8-shaped groove 10 with radial extensions 11, 11 a , 11 b , 11 c , 11 d , 11 e delimiting balancing zones 12, 13, 14, 15, 16 and 17.
  • conduits or grooves 18, 19, 20 21 pass through the bearings to bring the gates of the pinions into communication with the very thin space separating the other face of the pads from the covers.
  • the inlet 24 and outlet 25 conduits are also placed in communication respectively with the space 12 and 13 comprised between each pad and each cover.
  • a seal 26 of U-shaped section which is fitted into the groove 10 as illustrated in FIG. 4 and which forms a continuous groove 27.
  • conduits 22 and 23 passing through the bearings put the pressurized fluid located between the gears of the pinions in communication with the inside of the U-shaped part of the seal 26.
  • zones 16 and 17 are also subjected to the high pressure due to the communication of the conduits 20 and 21.
  • the pressure is also high in the zones 14 and 15 due to the communication produced by the conduits 18 and 19.
  • Zone 12 is subject to low pressure or inlet pressure.
  • the high pressure prevailing in the groove 27 of the U-shaped seal 26 presses said seal through its anti-extrusion seal 28 on the front 3 or rear 4 cover of the pump, causing a self-sealing between the zones 13, 16 and 17 and 14, 15 and 12, the pressure prevailing in the groove 27 always being equal to or greater than the pressure prevailing in the above areas.
  • the anti-extrusion lining extends as shown in FIG. 4 over the entire bearing surface of the seal bearing against the cover 11 and the seal provides a slight clearance with the bottom of the groove 10.
  • the seal between the balancing zones is therefore achieved by means of an elastic seal subjected only to the effects of the prevailing pressure. in the high pressure area of the pump or motor and in no case by the compression of this seal.
  • Balancing is thus completely achieved by hydraulic thrusts independent of mechanical compression of a mechanical seal.
  • the balancing and bearing forces of the bearings 6, 7 on the pinions 10, 11 are therefore produced by the product of the pressure prevailing in the conduits 24 and 25 on the one hand and on the other hand in the conduits 18, 19 and 20, 21 by the corresponding sections of zones 12, 13, 14, 15, 16 and 17 increased by the balancing force caused by the pressure in the conduits 22 and 23 by the surface of the seal 26.
  • the high pressure in the groove 27 also tends to apply the ends of the radial extensions 11, 11 a , 11 b , 11 c , 11 d and 11 e against the internal wall of the pump body 1, thereby preventing any leaks.

Abstract

1. Hydrostatic compensation device for gear hydraulic pumps or motors in which support bearings of the pinions are slidably mounted in the pump body (1) and define, with covers (3, 4) of the pump body, compensation chambers bordered by at least a gasket and in which a pressure is developed for keeping the bearings applied against the side face of the gears, characterized in that the gasket (26) has a U-shaped section the bottom part of which is facing a cover for defining a groove (27) set into communication with a high pressure prevailing in the pump or motor and is provided with an anti-extrusion fitting (28) applied against the cover, subjected to the pressure on its entire surface and extending on the whole support surface, the gasket (26) forming moreover a slight clearance with the bottom portion of the groove (10).

Description

La présente invention concerne les pompes ou moteurs à engrenages dont les pignons portés par des arbres sont disposés entre deux coussinets qui sont appliqués sous pression contre les faces latérales des pignons.The present invention relates to gear pumps or motors whose pinions carried by shafts are arranged between two bearings which are applied under pressure against the lateral faces of the pinions.

La technique antérieure a enseigné de nombreux moyens pour appliquer sur les coussinets des forces dites de compensation et le plus souvent la technique antérieure prévoit de délimiter des chambres de compensation entre les coussinets et des couvercles fermant le corps de pompe ou de moteur sur ses côtés latéraux.The prior art has taught numerous means for applying so-called compensating forces to the bearings, and most often the prior art provides for delimiting compensation chambers between the bearings and covers closing the pump or motor body on its lateral sides. .

Dans certaines publications, par exemple, dans le brevet USA 3 473 476, des chambres de compensation sont délimi­tées par des cloisons mises en place dans des rainures, ces cloisons formant en quelque sorte joints entre les coussinets et les couvercles. Il en est de même dans le brevet français 1 598 392 qui met en oeuvre des joints disposés dans des rainures du corps de pompe ou de moteur, ces joints délimitant des chambres de forme complexe dans lesquelles du liquide est amené à une pression qui cor­respond à celle qui s'exerce sur la face opposée du cous­sinet, c'est-à-dire celle tournée vers les pignons.In certain publications, for example, in US Pat. No. 3,473,476, compensation chambers are delimited by partitions placed in grooves, these partitions forming, so to speak, joints between the pads and the covers. It is the same in French patent 1,598,392 which uses seals arranged in grooves of the pump or motor body, these joints delimiting chambers of complex shape in which liquid is brought to a pressure which corresponds to that which is exerted on the opposite face of the bearing, that is to say that facing the pinions.

D'autres publications montrent encore des joints et cham­bres analogues. C'est le cas en particulier des brevets USA 3 482 524 et 3 142 260.Other publications also show similar seals and chambers. This is particularly the case for the US patents 3,482,524 and 3,142,260.

La Demanderesse a elle-même enseigné, en particulier dans son brevet français 73 02257, und disposition analogue dans laquelle un joint est prévu, soit dans des coussinets, soit dans le couvercle pour délimiter des chambres de com­pensation.The Applicant has itself taught, in particular in its French patent 73 02257, a similar arrangement in which a seal is provided, either in bearings or in the cover to delimit compensation chambers.

Les dispositions ci-dessus donnent généralement satisfac­tion mais se sont révélées imparfaites pour des pompes ou moteurs hydrauliques travaillant sous très haute pres­sion. En effet, les joints et les cloisons pour les main­tenir constituent des ensembles généralement fragiles. De plus, lorsque des cloisons sont prévues, cela limite la surface sur laquelle peut s'exercer la pression de compensation.The above arrangements are generally satisfactory but have proved to be imperfect for hydraulic pumps or motors working under very high pressure. Indeed, the seals and the partitions to maintain them constitute generally fragile assemblies. In addition, when partitions are provided, this limits the surface on which the compensation pressure can be exerted.

L'invention résout ce problème en permettant d'exercer des pressions de compensation sur toute la surface utile des coussinets d'une pompe ou d'un moteur et cela quel que soit le sens de rotation des pignons, cette pression s'exerçant également sur toute la surface du joint d'é­tanchéïté délimitant les zones de pression d'équilibrage.The invention solves this problem by making it possible to exert compensation pressures over the entire useful surface of the bearings of a pump or of a motor and this whatever the direction of rotation of the pinions, this pressure also being exerted on the entire surface of the seal delimiting the balancing pressure zones.

Conformément à l'invention, le dispositif de compensation hydrostatique pour pompe ou moteur hydraulique à engrena­ge dans lequel au moins un coussinet de support des pignons est monté coulissant dans le corps de pompe et délimite avec un couvercle du corps de pompe des chambres de com­pensation bordées par au moins un joint et dans lesquel­les une pression est développée pour maintenir le coussi­net appliqué contre la face latérale des engrenages est caractérisé en ce que le joint présente une section en U pour délimiter une rainure mise en communication avec une haute pression régnant dans la pompe ou le moteur.According to the invention, the hydrostatic compensation device for a pump or hydraulic gear motor in which at least one pinion support bearing is slidably mounted in the pump body and delimits with a cover of the pump body of the compensation chambers bordered by at least one seal and in which a pressure is developed to maintain the bearing applied against the lateral face of the gears is characterized in that the seal has a U-section to delimit a groove placed in communication with a high pressure prevailing in the pump or the motor.

Diverses autres caractéristiques de l'invention ressortent d'ailleurs du dessin détaillé qui suit;Various other characteristics of the invention will also emerge from the detailed drawing which follows;

Une forme de réalisation de l'objet de l'invention est représentée, à titre d'exemple non limitatif, au dessin annexé.

  • La fig. 1 est une coupe transversale d'une pompe ou d'un moteur à engrenage d'un type faisant l'objet de l'inven­tion.
  • La fig. 2 est une coupe vue sensiblement suivant la ligne II-II de la fig. 1.
  • La fig. 3 est une coupe partielle, en partie schématique, vue sensiblement suivant la ligne III-III de la fig. 2.
  • La fig. 4 est une coupe très agrandie du détail A de la fig. 3
An embodiment of the object of the invention is shown, by way of nonlimiting example, in the accompanying drawing.
  • Fig. 1 is a cross section of a pump or a gear motor of a type forming the subject of the invention.
  • Fig. 2 is a section seen substantially along line II-II of FIG. 1.
  • Fig. 3 is a partial section, partly schematic, seen substantially along line III-III of FIG. 2.
  • Fig. 4 is a very enlarged section of detail A in FIG. 3

La description qui suit se réfère à une pompe hydraulique à engrenage qui est constituée pour pouvoir fonctionner dans l'un et l'autre des deux sens de rotation possibles.The following description refers to a hydraulic gear pump which is designed to operate in either of the two possible directions of rotation.

Tout ce qui suit s'applique de la même façon à un moteur hydraulique et, le cas échéant, à une pompe ou à un moteur hydraulique destiné à fonctionner seulement dans un seul sens de rotation. La différence essentielle existant avec la pompe décrite résiderait dans la conformation diffé­rente que présenteraient alors les chambres ou espaces dits de compensation.The following applies equally to a hydraulic motor and, where applicable, to a pump or hydraulic motor intended to operate only in one sense of rotation. The essential difference existing with the pump described would reside in the different conformation that the so-called compensation chambers or spaces would then have.

La pompe comporte un corps 1 délimitant une cavité 2 de forme ovoïde.The pump comprises a body 1 delimiting a cavity 2 of ovoid shape.

Le corps 1 est fermé sur chacun de ses deux côtés par des couvercles 3, 4 qui y sont reliés par des pions de centrage 5. La cavité 2 contient des coussinets ou paliers 6, 7 pouvant coulisser à frottement doux. Les coussinets 6, 7 supportent des arbres menant 8 et mené 9 sur lesquels sont calés des pignons 8a et 9a.The body 1 is closed on each of its two sides by covers 3, 4 which are connected to it by centering pins 5. The cavity 2 contains bearings or bearings 6, 7 which can slide with gentle friction. The bearings 6, 7 support driving shafts 8 and driven 9 on which pinions 8a and 9a are fixed.

Dans l'exemple décrit, l'arbre 8 constituant l'arbre me­nant fait saillie du couvercle 3 tandis que l'arbre 9 est complètement inclus à l'intérieur de la pompe.In the example described, the shaft 8 constituting the driving shaft projects from the cover 3 while the shaft 9 is completely included inside the pump.

Les coussinets ou paliers 6, 7 respectivement appelés pa­lier avant et palier arrière présentent une rainure 10 en forme de 8 avec des prolongements radiaux 11, 11a, 11b, 11c, 11d, 11e délimitant des zones d'équilibrage 12, 13, 14, 15, 16 et 17.The bearings or bearings 6, 7 respectively called front bearing and rear bearing have an 8-shaped groove 10 with radial extensions 11, 11 a , 11 b , 11 c , 11 d , 11 e delimiting balancing zones 12, 13, 14, 15, 16 and 17.

Pour que les coussinets 6, 7 soient toujours maintenus appliqués contre les faces latérales des pignons de la pompe ou du moteur, des conduits ou rainures 18, 19, 20 21 traversent les coussinets pour mettre en communication les entre-dents des pignons avec l'espace de très faible épaisseur qui sépare l'autre face des coussinets des cou­vercles.So that the bearings 6, 7 are always kept applied against the lateral faces of the pinions of the pump or of the motor, conduits or grooves 18, 19, 20 21 pass through the bearings to bring the gates of the pinions into communication with the very thin space separating the other face of the pads from the covers.

De même, si l'on considère le sens de circulation du li­quide de travail illustré par les flèches f₁ et f₂ de la de la fig. 2, les conduits d'admission 24 et de refou­lement 25, sont également mis en communication respecti­vement avec l' space 12 et 13 compris entre chaque coussinet et chaque couvercle.Similarly, if we consider the direction of circulation of the working liquid illustrated by the arrows f₁ and f₂ of the of fig. 2, the inlet 24 and outlet 25 conduits, are also placed in communication respectively with the space 12 and 13 comprised between each pad and each cover.

Les zones d'équilibrage sur lesquelles viennent s'appli­quer les pressions régnant dans la pompe ou le moteur sont délimitées et rendues étanches par un joint 26 de sec­tion en forme de U et qui est emboîté dans la rainure 10 comme illustré par la fig. 4 et qui forme une rainure continue 27.The balancing zones on which the pressures prevailing in the pump or the motor are applied are delimited and sealed by a seal 26 of U-shaped section which is fitted into the groove 10 as illustrated in FIG. 4 and which forms a continuous groove 27.

Les conduits 22 et 23 traversant les coussinets, mettent en communication le fluide sous pression se trouvant en­tre les entre-dents des pignons avec l'intérieur de la partie en forme de U du joint 26.The conduits 22 and 23 passing through the bearings put the pressurized fluid located between the gears of the pinions in communication with the inside of the U-shaped part of the seal 26.

Le dessin montre que les conduits 22 et 23 sont diamétra­lement opposés.The drawing shows that the conduits 22 and 23 are diametrically opposed.

La réalisation décrite et représentée fait apparaître que le joint 26 en forme de U, qui délimite les zones de pression d'équilibrage 12 à 17, est lui-même soumis in­térieurement à une pression hydraulique provenant des conduits 22 et 23 qui sont symétriques aux pignons menant et mené.The embodiment described and shown shows that the U-shaped seal 26, which delimits the balancing pressure zones 12 to 17, is itself internally subjected to hydraulic pressure coming from the conduits 22 and 23 which are symmetrical with the pinions leading and leading.

Ce qui précède montre que la pression régnant dans les conduits 22 et 23 est toujours la même, quel que soit le sens de rotation de la pompe ou du moteur, l'expérience faisant apparaître que cette pression correspond sensible­ment à la plus forte pression régnant dans la pompe ou le moteur.The above shows that the pressure prevailing in the conduits 22 and 23 is always the same, regardless of the direction of rotation of the pump or the motor, experience showing that this pressure corresponds substantially to the highest pressure prevailing in pump or motor.

A titre d'exemple pour un fonctionnement en pompe, si l'on considère la fig. 2 et le sens de rotation de l'arbre menant suivant la flèche f₁, la haute pression est établie dans le conduit de sortie 25 et la basse pression dans le conduit 24; la zone d'équilibrage 13 est aussi soumise à la haute pression.As an example for pump operation, if one consider fig. 2 and the direction of rotation of the driving shaft along arrow f₁, the high pressure is established in the outlet conduit 25 and the low pressure in the conduit 24; the balancing zone 13 is also subjected to high pressure.

Par suite des jeux fonctionnels les zones 16 et 17 sont également soumises à la haute pression du fait de la communication des conduits 20 et 21. La pression est également élevée dans les zones 14 et 15 du fait de la communication réalisée par les conduits 18 et 19. La zone 12 est soumise à la basse pression ou à la pression d'admission.As a result of the functional clearances, the zones 16 and 17 are also subjected to the high pressure due to the communication of the conduits 20 and 21. The pressure is also high in the zones 14 and 15 due to the communication produced by the conduits 18 and 19. Zone 12 is subject to low pressure or inlet pressure.

Parallèlement, le joint 26 alimenté par les conduits 22 et 23 est soumis à la haute pression sur toute son étendue.In parallel, the seal 26 supplied by the conduits 22 and 23 is subjected to high pressure over its entire extent.

La haute pression régnant dans la rainure 27 du joint d'étanchéité 26 en U appuie ledit joint par l'inter­médiaire de sa garniture anti-extrusion 28 sur le cou­vercle avant 3 ou arrière 4 de la pompe en provoquant une auto-étanchéité entre les zones 13, 16 et 17 et 14, 15 et 12, la pression régnant dans la rainure 27 étant toujours égale ou supérieure à la pression régnant dans les zones ci-dessus.The high pressure prevailing in the groove 27 of the U-shaped seal 26 presses said seal through its anti-extrusion seal 28 on the front 3 or rear 4 cover of the pump, causing a self-sealing between the zones 13, 16 and 17 and 14, 15 and 12, the pressure prevailing in the groove 27 always being equal to or greater than the pressure prevailing in the above areas.

De préférence, la garniture anti-extrusion s'étend comme représenté à la fig. 4 sur toute la surface d'appui du joint portant contre le couvercle 11 et le joint ména­ge un léger jeu avec le fond de la rainure 10.Preferably, the anti-extrusion lining extends as shown in FIG. 4 over the entire bearing surface of the seal bearing against the cover 11 and the seal provides a slight clearance with the bottom of the groove 10.

Selon l'invention, l'étanchéité entre les zones d'équi­librage est donc réalisée par l'intermédiaire d'un joint élastique soumis aux seuls effets de la pression régnant dans la zone haute pression de la pompe ou du moteur et en aucun cas par la compression de ce joint.According to the invention, the seal between the balancing zones is therefore achieved by means of an elastic seal subjected only to the effects of the prevailing pressure. in the high pressure area of the pump or motor and in no case by the compression of this seal.

L'équilibrage est donc ainsi complètement réalisé par des poussées hydrauliques indépendantes d'une compres­sion mécanique d'un joint mécanique.Balancing is thus completely achieved by hydraulic thrusts independent of mechanical compression of a mechanical seal.

Les forces d'équilibrage et d'appui des coussinets 6, 7 sur les pignons 10, 11 sont donc réalisées par le pro­duit de la pression régnant dans les conduits 24 et 25 d'une part et d'autre part dans les conduits 18, 19 et 20, 21 par les sections correspondantes des zones 12, 13, 14, 15, 16 et 17 augmenté de la force d'équilibrage provoquée par la pression dans les conduits 22 et 23 par la surface du joint 26.The balancing and bearing forces of the bearings 6, 7 on the pinions 10, 11 are therefore produced by the product of the pressure prevailing in the conduits 24 and 25 on the one hand and on the other hand in the conduits 18, 19 and 20, 21 by the corresponding sections of zones 12, 13, 14, 15, 16 and 17 increased by the balancing force caused by the pressure in the conduits 22 and 23 by the surface of the seal 26.

Du fait de la symétrie du joint 26 par rapport à l'axe x - x de la pompe ou du moteur un fonctionnement alter­natif dans l'un et l'autre sens de rotation est possible indépendamment des pressions d'entrée et de sortie, les conduits 22 et 23 de communication alimentant la rainure 27 du joint 26 toujours à la valeur de la haute pression.Due to the symmetry of the seal 26 with respect to the axis x - x of the pump or of the motor, alternating operation in either direction of rotation is possible independently of the inlet and outlet pressures, the communication conduits 22 and 23 supplying the groove 27 of the seal 26 always at the value of the high pressure.

Cette haute pression régnant sur le joint 26 et indépen­dante du sens de rotation, applique celui-ci sur le pour­tour de la rainure 10 et des couvercles en assurant par­faitement l'étanchéité entre les zones d'équilibrage et les zones basse pression régnant dans les alésages des arbres menant et mené. La haute pression dans la rainu­re 27 tend aussi à appliquer les extrémités des prolon­gements radiaux 11, 11a,11b, 11c, 11d et 11e contre la paroi interne du corps de pompe 1 en empêchant ainsi toutes fuites.This high pressure prevailing on the seal 26 and independent of the direction of rotation, applies it on the periphery of the groove 10 and the covers, ensuring perfect sealing between the balancing zones and the low pressure zones prevailing in the bores leading and led trees. The high pressure in the groove 27 also tends to apply the ends of the radial extensions 11, 11 a , 11 b , 11 c , 11 d and 11 e against the internal wall of the pump body 1, thereby preventing any leaks.

L'invention n'est par limitée à l'exemple de réalisation représenté et décrit en détail, car diverses modifica­tions peuvent y être apportées sans sortir de son cadre.The invention is not limited to the embodiment shown and described in detail, because various modifications can be made without departing from its scope.

Claims (9)

1 - Dispositif de compensation hydrostatique pour pompe ou moteur hydraulique à engrenage dans lequel au moins un coussinet de support des pignons est monté coulissant dans le corps de pompe (1) et délimite avec un couvercle (3 ou 4) du corps de pompe des chambres de compensation bordées par au moins un joint et dans lesquelles une pression est développée pour maintenir le coussinet ap­pliqué contre la face latérale des engrenages, caracté­risé en ce que le joint (26) présente une section en U pour délimiter une rainure (27) mise en communication avec une haute pression régnant dans la pompe ou le moteur.1 - Hydrostatic compensation device for pump or hydraulic gear motor in which at least one pinion support bearing is slidably mounted in the pump body (1) and delimits with a cover (3 or 4) from the pump body of the chambers compensation bordered by at least one seal and in which a pressure is developed to maintain the bearing applied against the lateral face of the gears, characterized in that the seal (26) has a U-section to define a groove (27) communication with high pressure prevailing in the pump or motor. 2 - Dispositif suivant la revendication 1, caractérisé en ce que le joint (26) est muni d'une garniture anti-extrusion (28) et est soumis aux pressions sur toute sa surface.2 - Device according to claim 1, characterized in that the seal (26) is provided with an anti-extrusion packing (28) and is subjected to pressures over its entire surface. 3 - Dispositif suivant l'une des revendications 1 et 2, caractérisé en ce que la garniture anti-extrusion s'étend sur toute la surface d'appui.3 - Device according to one of claims 1 and 2, characterized in that the anti-extrusion lining extends over the entire bearing surface. 4 - Dispositif suivant l'une des revendications 1 à 3, caractérisé en ce que le joint (26) présente sensiblement la forme du chiffre 8 à partir duquel font saillie des prolongements radiaux (11 à 11e) dont les extrémités por­tent contre l'intérieur du corps de pompe.4 - Device according to one of claims 1 to 3, characterized in that the seal (26) has substantially the shape of the figure 8 from which protrude radial extensions (11 to 11e) whose ends bear against the interior of the pump body. 5 - Dispositif suivant l'une des revendications 1 à 4, caractérisé en ce que la haute pression est amenée dans la rainure (27) du joint par des conduits (22, 23) diamé­tralement opposés.5 - Device according to one of claims 1 to 4, characterized in that the high pressure is brought into the groove (27) of the joint by conduits (22, 23) diametrically opposite. 6 - Dispositif suivant l'une des revendications 1 à 5, caractérisé en ce que la haute pression est amenée dans la rainure (27) du joint (26) par des rainures (22, 23) prévues à la périphérie de chaque coussinet.6 - Device according to one of claims 1 to 5, characterized in that the high pressure is brought in the groove (27) of the seal (26) by grooves (22, 23) provided at the periphery of each bearing. 7 - Dispositif suivant l'une des revendications 1 à 6, caractérisé par des conduits supplémentaires (18, 19, 20, 21) pour faire communiquer les entre-dents des engrenages avec les chambres de compensation (14, 15, 16, 17) délimi­tées par les prolongements radiaux (11 à 11e) du joint (26).7 - Device according to one of claims 1 to 6, characterized by additional conduits (18, 19, 20, 21) for communicating the inter-teeth of the gears with the compensation chambers (14, 15, 16, 17) delimited by the radial extensions (11 to 11 e ) of the seal (26). 8 - Dispositif suivant l'une des revendications 1 à 7, caractérisé en ce que les conduits supplémentaires sont formés par des rainures pratiquées à la périphérie des coussinets ( 6, 7).8 - Device according to one of claims 1 to 7, characterized in that the additional conduits are formed by grooves formed at the periphery of the pads (6, 7). 9 - Dispositif suivant l'une des revendications 1 à 8, caractérisé en ce que le joint (26) et ses prolongements radiaux sont disposés dans une rainure (10) du côté de chaque coussinet faisant face à un couvercle (3 ou 4) qui forme surface d'appui pour la garniture anti-extrusion (28).9 - Device according to one of claims 1 to 8, characterized in that the seal (26) and its radial extensions are arranged in a groove (10) on the side of each pad facing a cover (3 or 4) which form support surface for the anti-extrusion lining (28).
EP86401502A 1985-07-16 1986-07-04 Purely hydraulic action device for the hydrostatic compensation of hydraulic gear pumps and motors Expired EP0211723B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86401502T ATE46017T1 (en) 1985-07-16 1986-07-04 PURELY HYDRAULIC DEVICE FOR HYDROSTATIC BALANCING OF HYDRAULIC GEAR PUMPS AND MOTORS.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8510887 1985-07-16
FR8510887A FR2585083B1 (en) 1985-07-16 1985-07-16 PURE HYDRAULIC ACTION DEVICE FOR HYDROSTATIC COMPENSATION OF GEAR TYPE HYDRAULIC PUMPS AND MOTORS

Publications (2)

Publication Number Publication Date
EP0211723A1 true EP0211723A1 (en) 1987-02-25
EP0211723B1 EP0211723B1 (en) 1989-08-30

Family

ID=9321351

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86401502A Expired EP0211723B1 (en) 1985-07-16 1986-07-04 Purely hydraulic action device for the hydrostatic compensation of hydraulic gear pumps and motors

Country Status (5)

Country Link
EP (1) EP0211723B1 (en)
JP (2) JPS6248978A (en)
AT (1) ATE46017T1 (en)
DE (2) DE3665351D1 (en)
FR (1) FR2585083B1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0287698A1 (en) * 1987-04-24 1988-10-26 JOHN S. BARNES GmbH Fluid gear pump or motor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4322240C2 (en) * 1993-07-03 1997-01-09 Eckerle Rexroth Gmbh Co Kg Hydraulic internal gear machine (pump or motor)

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Publication number Priority date Publication date Assignee Title
FR1343908A (en) * 1962-11-22 1963-11-22 Clark Equipment Co Pump or motor
FR1546355A (en) * 1966-12-05 1968-11-15 Borg Warner Pressure-loaded pump mechanism or motor, including reversible gear pump or motor
FR1598392A (en) * 1968-04-13 1970-07-06
DE1940106A1 (en) * 1969-08-07 1971-03-11 Westinghouse Bremsen Und Appba Seal for sealing pressure fields
FR2193455A5 (en) * 1972-07-14 1974-02-15 Trw Inc
DE2403319A1 (en) * 1974-01-24 1975-07-31 Bosch Gmbh Robert GEAR MACHINE
DE2646727A1 (en) * 1975-10-17 1977-04-28 Kayaba Industry Co Ltd GEAR PUMP
FR2353728A1 (en) * 1976-06-04 1977-12-30 Bosch Gmbh Robert Engaging gear wheel pump or motor - has hydraulically pressurised bearing sleeves ensuring sealing under critical conditions
GB2028925A (en) * 1978-08-24 1980-03-12 Commercial Shearing Rotary positiv-displacement fluidmachines
GB2033478A (en) * 1978-11-03 1980-05-21 Bosch Gmbh Robert Rotary positive-displacement fluidmachines
EP0093917A1 (en) * 1982-05-12 1983-11-16 Robert Bosch Gmbh Reversible gear machine (motor or pump)

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JPS5234763A (en) * 1975-09-12 1977-03-16 Oki Electric Ind Co Ltd Process for the fabrication of a compound type device for transmitting and re ceiving waves
JPS5838392A (en) * 1981-08-31 1983-03-05 Shimadzu Corp Gear pump or gear motor

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Publication number Priority date Publication date Assignee Title
FR1343908A (en) * 1962-11-22 1963-11-22 Clark Equipment Co Pump or motor
FR1546355A (en) * 1966-12-05 1968-11-15 Borg Warner Pressure-loaded pump mechanism or motor, including reversible gear pump or motor
FR1598392A (en) * 1968-04-13 1970-07-06
DE1940106A1 (en) * 1969-08-07 1971-03-11 Westinghouse Bremsen Und Appba Seal for sealing pressure fields
FR2193455A5 (en) * 1972-07-14 1974-02-15 Trw Inc
DE2403319A1 (en) * 1974-01-24 1975-07-31 Bosch Gmbh Robert GEAR MACHINE
DE2646727A1 (en) * 1975-10-17 1977-04-28 Kayaba Industry Co Ltd GEAR PUMP
FR2353728A1 (en) * 1976-06-04 1977-12-30 Bosch Gmbh Robert Engaging gear wheel pump or motor - has hydraulically pressurised bearing sleeves ensuring sealing under critical conditions
GB2028925A (en) * 1978-08-24 1980-03-12 Commercial Shearing Rotary positiv-displacement fluidmachines
GB2033478A (en) * 1978-11-03 1980-05-21 Bosch Gmbh Robert Rotary positive-displacement fluidmachines
EP0093917A1 (en) * 1982-05-12 1983-11-16 Robert Bosch Gmbh Reversible gear machine (motor or pump)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0287698A1 (en) * 1987-04-24 1988-10-26 JOHN S. BARNES GmbH Fluid gear pump or motor
US4830592A (en) * 1987-04-24 1989-05-16 Vickers Systems Gmbh Rotary gear pump or motor for fluids

Also Published As

Publication number Publication date
JPH0680885U (en) 1994-11-15
DE211723T1 (en) 1987-07-02
JP2572016Y2 (en) 1998-05-20
FR2585083B1 (en) 1989-09-01
EP0211723B1 (en) 1989-08-30
JPS6248978A (en) 1987-03-03
ATE46017T1 (en) 1989-09-15
DE3665351D1 (en) 1989-10-05
FR2585083A1 (en) 1987-01-23

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