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EP0534836A1 - Hydraulic gear type machine with floating body - Google Patents

Hydraulic gear type machine with floating body Download PDF

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Publication number
EP0534836A1
EP0534836A1 EP92402597A EP92402597A EP0534836A1 EP 0534836 A1 EP0534836 A1 EP 0534836A1 EP 92402597 A EP92402597 A EP 92402597A EP 92402597 A EP92402597 A EP 92402597A EP 0534836 A1 EP0534836 A1 EP 0534836A1
Authority
EP
European Patent Office
Prior art keywords
flanges
machine according
pinions
casing
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP92402597A
Other languages
German (de)
French (fr)
Other versions
EP0534836B1 (en
Inventor
Roger Laumont
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.)
Hydroperfect International Inc
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Hydroperfect International Inc
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Publication date
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Publication of EP0534836A1 publication Critical patent/EP0534836A1/en
Application granted granted Critical
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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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • 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
    • 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
    • F04C15/0007—Radial sealings for working fluid
    • F04C15/0019—Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

  • the present invention relates to hydraulic gear machines intended to be used either as pumps or as motors.
  • devices of the type comprising a set of two cooperating toothed wheels arranged to rotate between two flanges, forming a bearing, mounted movable in translation in corresponding recesses made in a body central and delimited by two opposite covers or housings fixed in leaktight manner to the latter, each flange being substantially balanced in pressure by the arrangement between this flange and the adjacent cover with a suitable seal system.
  • Such devices are known from FR-A-2 215 103 and give satisfaction by making it possible to obtain excellent mechanical and volumetric yields for an acceptable cost price in consideration of the performances obtained.
  • the known devices do not maintain the same efficiency as a function of the working temperature, which is due to the variations in viscosity of the working fluid as well as to the differential expansions existing between the different parts and, more particularly, between the fixed and mobile parts, the pump bodies are often made of aluminum as well as the flanges while the pinions are made of steel.
  • the invention aims to remedy the drawbacks noted by creating a new hydraulic machine, all the moving parts of which can float relative to the fixed parts, regardless of the operating temperature and the speed of rotation of the moving parts, while also making compensation pressures generated, which according to the invention are differential pressures, maintain a constant compensation of the clearances.
  • the hydraulic machine of the gear type comprising at least one set of two cooperating pinions arranged to rotate between two flanges movable in translation in cavities produced in a central casing closed on its two opposite sides by anterior casings and posterior, each flange being substantially balanced in pressure by the arrangement between this flange and the adjacent casing of a suitable seal system, is characterized in that the flanges supporting the pinions are mounted floating inside the median casing and in this that pressure means apply the flanges against the median casing and cause a differential pressure causing the flanges to clamp against the lateral faces of the pinions.
  • Fig. 1 is a longitudinal sectional elevation of an embodiment of the machine according to the invention.
  • Fig. 2 is a sectional view taken along line II-II of FIG. 1.
  • Fig. 3 is a section seen along line III-III of FIG. 1.
  • Fig. 4 is a plan view, partly in section, along the line IV-IV of FIG. 1.
  • Fig. 5 is a section seen along line V-V of FIG. 1 or Va-Va in fig. 4.
  • Fig. 6 is a section taken along line VI-VI of FIG. 1.
  • the illustrated embodiment of the machine is described as a pump for supplying pressurized liquid.
  • the same machine could be used as a motor, its constituent elements being reversible as is usual in the technique of pumps or hydraulic motors of the gear type.
  • the hydraulic machine is described with reference to a machine with a single set of gears but it could, in a similar manner, include several sets of gears, in particular two sets of gears whose teeth would be offset from one game to another.
  • the machine comprises a front casing 1 or cover and a rear casing 2 or cover connected to each other by a median casing 3 inside which is disposed, in accordance in the invention, a floating body 4 constituted by flanges for supporting shafts and pinions described below.
  • the median casing 3 is centered with respect to the anterior 1 and posterior casings 2 by means of pins 5.
  • the anterior 1 and posterior casings 2 are fixed to the median casing 3 by bolts 6.
  • Seals 7, 8 are interposed between the front casing 1 and the central casing 3, and respectively, between the rear casing 2 and the central casing 3 (fig. 1).
  • the front casing 1 has a gasket 9 and a bearing 10 in which is mounted an input shaft 11a connected via a coupling 21 to an input shaft 11 extending within the housing median 3 to a housing 12 of the rear casing 2.
  • the shaft 11 supports and drives a primary pinion 13 disposed between a front flange 14 and a rear flange 15 forming part of the floating body 4.
  • the flanges 14 and 15 also support a secondary shaft 16 on which is fixed a pinion 17 in engagement with the primary pinion 13.
  • Both the shaft 11 and the shaft 16 are supported by the flanges 14 and 15 by means of bearings or bearings 18, 18 a and 19, 19 a whose width is slightly smaller than the thickness of said flanges 14, 15 and in which the shafts 11 and 16 can slide at the same time as they rotate.
  • bearings When the above bearings are constituted by smooth rings, they preferably comprise lubrication grooves 20 advantageously constituted in the manner described and shown in French patent 1,554,858.
  • the coupling 21 causes the part of the shaft 11, which is carried by the bearings 18, 18 a , to undergo the same bending stresses as the shaft 16, which equalizes the working mode of the two trees considered.
  • the pinions 13 and 17 are mounted on the shafts 11 and 16 so that they can slide axially thereon.
  • the flanges 14, 15 each have substantially the shape of the number 8.
  • the interior of the median casing 3 delimits two circular cavities 22, 23 which communicate with each other by a median circular cavity 24.
  • the radius of curvature of the circular cavities 22, 23 is the same as that of the periphery of the teeth of the primary pinions 13 and secondary 17 which are engaged with each other.
  • the middle cavity 24 communicates, on the one hand, with the intake duct 25 for the fluid to be pumped and, on the other hand, with a discharge duct 26 for this same fluid (see FIGS. 2 and 5).
  • the intake duct 25 is of larger section than the discharge duct 26.
  • Each flange 14 and 15 has, at its peripheral part, a lobe 27, respectively 28, of the same radius as the corresponding cavity 22, respectively 23, to bear against the respective wall of each of the two above cavities.
  • the outer wall of the front flanges 14 and rear 15 has low-cut parts 29, 30 respectively, that is to say parts of smaller diameter than the lobes 27, 28 so as to provide spaces 31, 32 communicating as well as this is shown in particular in figs. 2 and 6 with the discharge pipe 26.
  • Pads 33, 34 are arranged in the flanges 14, 15 to project into the spaces 31, 32.
  • the pads 33, 34 are mounted in housings 35 communicating with the spaces 31, 32 so that the pressure prevailing in these spaces is applied on either side of said pads which are also pushed by springs 36, slightly constrained , from so that they exert a push only tending to keep the lobes 27, 28 of the flanges in abutment against the wall of the circular cavities 22, 23.
  • each flange 14 and 15 has a front wall or face 37 facing the pinions 13 and 17 and a rear wall or face 38 facing, for the flange 14, towards the front casing 1 and, for the flange 15, to the rear housing 2.
  • the front wall 37 comprises annular segments 39, 40 (FIGS. 2 and 5) extending from the bore containing the bearing 18 or 18 a to the bottom of the teeth 41 and 42 of the primary gears 13 and secondary 17.
  • the segments 39, 40 constitute bearing surfaces for the solid parts of the pinions 13, 17.
  • the annular segments 39, 40 are connected to plates 43, 44 of substantially trapezoidal shape and, at their other end, they are connected to each other by a partition 45 separating the intake duct 25 from the discharge duct 26.
  • Fig. 5 shows that the partition 45 advantageously has a substantially diamond shape.
  • Fig. 2 shows that the dimension of the partition 45 and also its shape are determined to correspond to the measurement occupied by at least one of the gable ends 13, 17 so that there can never be direct communication between the intake duct 25 and the discharge conduit 26 when the pinions rotate.
  • the part of the front wall 37 which should not bear against the lateral face of the pinions is milled to provide a chamber 46 (fig. 5), respectively 47 (fig. 1), on each side of the primary 13 and secondary 17 pinions.
  • each flange has a groove 48 having substantially the shape of the letter W, and in which is disposed a seal 49 ending at its two ends by retaining shoes 50, 51 (fig. 6).
  • the seal 49 is provided with an anti-extrusion packing 52.
  • the seal 49 has bosses 53 to delimit notches 53a and allow the fluid, being in the circular cavities 22, 23 and coming against the rear wall 38 of each flange, to push the seal against the front casing 1 and, respectively, the rear casing 2, while exerting pressure on the rear face of each flange.
  • the dimension of the groove 48 and of the seal 49, the shoes 50 of which are arranged in the lobes 27, 28, is determined so that the surface on which the pressure of the fluid coming from the discharge conduit 26 is greater to that on which this pressure is exerted on the front face of each flange.
  • the seal 49 located in the rear face of each flange, exerts itself a slight pressure so that the flanges are held in abutment against the lateral faces of the pinions when the pump is is not in action and that the pressure in the discharge duct 26 tends to equalize with the pressure in the intake duct 25.
  • the floating body 4 is independent of stresses due to possible differential expansions, it is made so that the sum of the thicknesses of the flanges 14, 15 and the pinions 13, 17 is slightly less than the width of the median casing 3, the centering of the floating body being provided by the seals 49 and the differential pressure which pushes the flanges 14, 15 towards each other against the lateral faces of the pinions 13 and 17.
  • the lobes 27 and 28 preferably extend over an arc of a circle less than 90 °, the flanges 14 and 15 being prevented from tilting by the studs 33, 34 which hold said lobes 27 and 28 against the wall of the cavities.
  • circular 22, 23, which also makes it possible to compensate for any differential expansions which may occur between the flanges 14, 15 and the median casing 3.
  • Fig. 6 shows that the rear face of the flanges 14 and 15 delimits channels 54, 55 communicating the intake duct 25 through the cavity 24 with one end of the lubrication grooves 20 of the bearings 18, 18 a and 19, 19 a .
  • fig. 5 shows a recess 56 made in the front face of the flanges 14 and 15 between the plates 43, 44 and the partition 45.
  • the recess 56 places the cavity 24 under low pressure in communication with the lubrication grooves 20, so that the hydraulic fluid circulates in said grooves from the recess 56 to the channel 54 or 55, or vice versa, according to the direction of rotation of the shafts 1 and 16.
  • each recess 56 reduces the surface on which the pinions rub.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Gear Transmission (AREA)
  • Lubricants (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Hydraulic Motors (AREA)

Abstract

Gear-type hydraulic machine comprising at least one set of two interacting gears arranged to revolve between two flanges which can move in translation within cavities produced in a middle casing which is closed on its two opposing sides by front and rear casings, each flange being substantially balanced in pressure by arranging a suitable seal system between this flange and the adjacent casing, characterised in that the flanges (14, 15) supporting the gears (13, 17) are mounted to float inside the middle casing (3), and in that pressure means (49) apply the flanges (14, 15) against the middle casing (3) and give rise to a differential pressure causing the flanges (14, 15) to be clamped against the lateral faces of the gears (13, 17). <IMAGE>

Description

La présente invention concerne les machines hydrauliques à engrenages destinées à être utilisées soit comme pompes soit comme moteurs.The present invention relates to hydraulic gear machines intended to be used either as pumps or as motors.

Dans le domaine des appareils hydrauliques à engrenages à haute performance, on a déjà proposé des appareils du type comportant un jeu de deux roues dentées coopérantes agencées pour tourner entre deux flasques, formant palier, montés mobiles en translation dans des évidements correspondants réalisés dans un corps central et délimités par deux couvercles ou carters opposés fixés de façon étanche à ce dernier, chaque flasque étant sensiblement équilibré en pression par la disposition entre ce flasque et le couvercle adjacent d'un système de joint convenable.In the field of hydraulic equipment with high performance gears, devices of the type have already been proposed comprising a set of two cooperating toothed wheels arranged to rotate between two flanges, forming a bearing, mounted movable in translation in corresponding recesses made in a body central and delimited by two opposite covers or housings fixed in leaktight manner to the latter, each flange being substantially balanced in pressure by the arrangement between this flange and the adjacent cover with a suitable seal system.

De tels appareils sont connus par le FR-A-2 215 103 et donnent satisfaction en permettant d'obtenir d'excellents rendements mécaniques et volumétriques pour un prix de revient acceptable en considération des performances obtenues.Such devices are known from FR-A-2 215 103 and give satisfaction by making it possible to obtain excellent mechanical and volumetric yields for an acceptable cost price in consideration of the performances obtained.

Il est apparu cependant que les appareils connus ne conservent pas la même efficacité en fonction de la température de travail, ce qui est dû aux variations de viscosité du fluide de travail ainsi qu'aux dilatations différentielles existant entre les différentes pièces et, plus particulièrement, entre les parties fixes et mobiles, les corps des pompes étant souvent fabriqués en aluminium de même que les flasques tandis que les pignons sont en acier.However, it has become apparent that the known devices do not maintain the same efficiency as a function of the working temperature, which is due to the variations in viscosity of the working fluid as well as to the differential expansions existing between the different parts and, more particularly, between the fixed and mobile parts, the pump bodies are often made of aluminum as well as the flanges while the pinions are made of steel.

L'invention vise à remédier aux inconvénients constatés en créant une nouvelle machine hydraulique dont toutes les parties mobiles peuvent flotter par rapport aux pièces fixes et celà, quelles que soient la température de fonctionnement et la vitesse de rotation des parties mobiles en faisant en outre que des pressions de compensation engendrées, qui selon l'invention sont des pressions différentielles, maintiennent une compensation constante des jeux.The invention aims to remedy the drawbacks noted by creating a new hydraulic machine, all the moving parts of which can float relative to the fixed parts, regardless of the operating temperature and the speed of rotation of the moving parts, while also making compensation pressures generated, which according to the invention are differential pressures, maintain a constant compensation of the clearances.

Conformément à l'invention, la machine hydraulique du type à engrenages comportant au moins un jeu de deux pignons coopérants agencés pour tourner entre deux flasques mobiles en translation dans des cavités réalisées dans un carter médian fermé sur ses deux côtés opposés par des carters antérieur et postérieur, chaque flasque étant sensiblement équilibré en pression par la disposition entre ce flasque et le carter adjacent d'un système de joint convenable, est caractérisée en ce que les flasques supportant les pignons sont montés flottants à l'intérieur du carter médian et en ce que des moyens de pression appliquent les flasques contre le carter médian et provoquent une pression différentielle faisant serrer les flasques contre les faces latérales des pignons.According to the invention, the hydraulic machine of the gear type comprising at least one set of two cooperating pinions arranged to rotate between two flanges movable in translation in cavities produced in a central casing closed on its two opposite sides by anterior casings and posterior, each flange being substantially balanced in pressure by the arrangement between this flange and the adjacent casing of a suitable seal system, is characterized in that the flanges supporting the pinions are mounted floating inside the median casing and in this that pressure means apply the flanges against the median casing and cause a differential pressure causing the flanges to clamp against the lateral faces of the pinions.

Diverses autres caractéristiques de l'invention ressortent d'ailleurs de la description détaillée qui suit.Various other characteristics of the invention will also emerge from the detailed description which follows.

Des formes de réalisation de l'objet de l'invention sont représentées, à titre d'exemples non limitatifs, aux dessins annexés.Embodiments of the object of the invention are shown, by way of nonlimiting examples, in the accompanying drawings.

La fig. 1 est une coupe-élévation longitudinale d'un mode de réalisation de la machine selon l'invention.Fig. 1 is a longitudinal sectional elevation of an embodiment of the machine according to the invention.

La fig. 2 est une coupe vue suivant la ligne II-II de la fig. 1.Fig. 2 is a sectional view taken along line II-II of FIG. 1.

La fig. 3 est une coupe vue suivant la ligne III-III de la fig. 1.Fig. 3 is a section seen along line III-III of FIG. 1.

La fig. 4 est une vue en plan, partie en coupe, suivant la ligne IV-IV de la fig. 1.Fig. 4 is a plan view, partly in section, along the line IV-IV of FIG. 1.

La fig. 5 est une coupe vue suivant la ligne V-V de la fig. 1 ou Va-Va de la fig. 4.Fig. 5 is a section seen along line V-V of FIG. 1 or Va-Va in fig. 4.

La fig. 6 est une coupe vue suivant la ligne VI-VI de la fig. 1.Fig. 6 is a section taken along line VI-VI of FIG. 1.

Dans ce qui suit, l'exemple de réalisation représenté de la machine est décrit en tant que pompe pour fournir un liquide sous pression.In the following, the illustrated embodiment of the machine is described as a pump for supplying pressurized liquid.

La même machine pourrait être utilisée en tant que moteur, ses éléments constitutifs étant réversibles comme celà est usuel dans la technique des pompes ou moteurs hydrauliques du type à engrenages.The same machine could be used as a motor, its constituent elements being reversible as is usual in the technique of pumps or hydraulic motors of the gear type.

De même dans ce qui suit, la machine hydraulique est décrite en référence à une machine à un seul jeu d'engrenages mais elle pourrait, de façon analogue, comporter plusieurs jeux d'engrenages, notamment deux jeux d'engrenages dont les dentures seraient décalées d'un jeu à l'autre.Similarly in what follows, the hydraulic machine is described with reference to a machine with a single set of gears but it could, in a similar manner, include several sets of gears, in particular two sets of gears whose teeth would be offset from one game to another.

D'une façon générale et connue en elle-même, la machine comporte un carter antérieur 1 ou couvercle et un carter postérieur 2 ou couvercle reliés l'un à l'autre par un carter médian 3 à l'intérieur duquel est disposé, conformément à l'invention, un corps flottant 4 constitué par des flasques de support d'arbres et de pignons décrits ci-après.In general and known in itself, the machine comprises a front casing 1 or cover and a rear casing 2 or cover connected to each other by a median casing 3 inside which is disposed, in accordance in the invention, a floating body 4 constituted by flanges for supporting shafts and pinions described below.

Le carter médian 3 est centré par rapport aux carters antérieur 1 et postérieur 2 au moyen de pions 5. De plus, les carters antérieur 1 et postérieur 2 sont fixés au carter médian 3 par des boulons 6.The median casing 3 is centered with respect to the anterior 1 and posterior casings 2 by means of pins 5. In addition, the anterior 1 and posterior casings 2 are fixed to the median casing 3 by bolts 6.

Des joints d'étanchéité 7, 8 sont interposés entre le carter antérieur 1 et le carter médian 3, et respectivement, entre le carter postérieur 2 et le carter médian 3 (fig. 1).Seals 7, 8 are interposed between the front casing 1 and the central casing 3, and respectively, between the rear casing 2 and the central casing 3 (fig. 1).

Dans la réalisation représentée, le carter antérieur 1 contient un joint d'étanchéité 9 et un palier 10 dans lequel est monté un arbre d'entrée 11a relié par un accouplement 21 à un arbre primaire 11 s'étendent à l'intérieur du carter médian 3 jusqu'à un logement 12 du carter postérieur 2.In the illustrated embodiment, the front casing 1 has a gasket 9 and a bearing 10 in which is mounted an input shaft 11a connected via a coupling 21 to an input shaft 11 extending within the housing median 3 to a housing 12 of the rear casing 2.

L'arbre 11 supporte et entraîne un pignon primaire 13 disposé entre un flasque avant 14 et un flasque arrière 15 faisant partie du corps flottant 4.The shaft 11 supports and drives a primary pinion 13 disposed between a front flange 14 and a rear flange 15 forming part of the floating body 4.

Les flasques 14 et 15 supportent également un arbre secondaire 16 sur lequel est fixé un pignon 17 en prise avec le pignon primaire 13.The flanges 14 and 15 also support a secondary shaft 16 on which is fixed a pinion 17 in engagement with the primary pinion 13.

Tant l'arbre 11 que l'arbre 16 sont supportés par les flasques 14 et 15 par l'intermédiaire de coussinets ou paliers 18, 18a et 19, 19a dont la largeur est légèrement plus petite que l'épaisseur desdits flasques 14, 15 et dans lesquels les arbres 11 et 16 peuvent coulisser en même temps qu'ils tournent.Both the shaft 11 and the shaft 16 are supported by the flanges 14 and 15 by means of bearings or bearings 18, 18 a and 19, 19 a whose width is slightly smaller than the thickness of said flanges 14, 15 and in which the shafts 11 and 16 can slide at the same time as they rotate.

Lorsque les paliers ci-dessus sont constitués par des bagues lisses, ils comportent de préférence des rainures de lubrification 20 avantageusement constituées de la façon décrite et représentée dans le brevet français 1 554 858.When the above bearings are constituted by smooth rings, they preferably comprise lubrication grooves 20 advantageously constituted in the manner described and shown in French patent 1,554,858.

L'accouplement 21 fait que la partie de l'arbre 11, qui est portée par les paliers 18, 18a, subit les mêmes contraintes de flexion que l'arbre 16, ce qui égalise le mode de travail des deux arbres considérés.The coupling 21 causes the part of the shaft 11, which is carried by the bearings 18, 18 a , to undergo the same bending stresses as the shaft 16, which equalizes the working mode of the two trees considered.

De même que les flasques 14, 15, les pignons 13 et 17 sont montés sur les arbres 11 et 16 pour pouvoir coulisser axialement sur ceux-ci.Like the flanges 14, 15, the pinions 13 and 17 are mounted on the shafts 11 and 16 so that they can slide axially thereon.

Le dessin montre que les flasques 14, 15 présentent l'un et l'autre sensiblement la forme du chiffre 8. De même, l'intérieur du carter médian 3 délimite deux cavités circulaires 22, 23 qui communiquent entre elles par une cavité circulaire médiane 24.The drawing shows that the flanges 14, 15 each have substantially the shape of the number 8. Likewise, the interior of the median casing 3 delimits two circular cavities 22, 23 which communicate with each other by a median circular cavity 24.

Le rayon de courbure des cavités circulaires 22, 23 est le même que celui de la périphérie des dents des pignons primaires 13 et secondaires 17 qui sont en prise l'un avec l'autre.The radius of curvature of the circular cavities 22, 23 is the same as that of the periphery of the teeth of the primary pinions 13 and secondary 17 which are engaged with each other.

La cavité médiane 24 communique, d'une part, avec le conduit d'admission 25 pour le fluide à pomper et, d'autre part, avec un conduit de refoulement 26 de ce même fluide (voir fig. 2 et 5).The middle cavity 24 communicates, on the one hand, with the intake duct 25 for the fluid to be pumped and, on the other hand, with a discharge duct 26 for this same fluid (see FIGS. 2 and 5).

De préférence, le conduit d'admission 25 est de plus grande section que le conduit de refoulement 26.Preferably, the intake duct 25 is of larger section than the discharge duct 26.

Chaque flasque 14 et 15 présente, à sa partie périphérique, un lobe 27, respectivement 28, de même rayon que la cavité correspondante 22, respectivement 23, pour prendre appui contre la paroi respective de chacune des deux cavités ci-dessus.Each flange 14 and 15 has, at its peripheral part, a lobe 27, respectively 28, of the same radius as the corresponding cavity 22, respectively 23, to bear against the respective wall of each of the two above cavities.

La paroi externe des flasques avant 14 et arrière 15 présente des parties décolletées 29, respectivement 30, c'est-à-dire des parties de plus petit diamètre que les lobes 27, 28 de manière à ménager des espaces 31, 32 communiquant ainsi que le montrent en particulier les fig. 2 et 6 avec le conduit de refoulement 26.The outer wall of the front flanges 14 and rear 15 has low-cut parts 29, 30 respectively, that is to say parts of smaller diameter than the lobes 27, 28 so as to provide spaces 31, 32 communicating as well as this is shown in particular in figs. 2 and 6 with the discharge pipe 26.

On voit par ce qui précède que la pression du fluide se trouvant dans le conduit de refoulement 26 est appliquée dans les espaces 31, 32 se trouvant à la périphérie des flasques 14 et 15, ce qui a pour effet de pousser les lobes 27 et 28 contre la paroi des cavités circulaires 22, 23 lorsque la pression dans le conduit de refoulement 26 est supérieure à la pression dans le conduit d'admission 25, ce qui se produit lorsque la pompe est en fonctionnement.It can be seen from the above that the pressure of the fluid located in the discharge conduit 26 is applied in the spaces 31, 32 located at the periphery of the flanges 14 and 15, which has the effect of pushing the lobes 27 and 28 against the wall of the circular cavities 22, 23 when the pressure in the discharge conduit 26 is greater than the pressure in the intake conduit 25, which occurs when the pump is in operation.

Des plots 33, 34 sont disposés dans les flasques 14, 15 pour faire saillie dans les espaces 31, 32.Pads 33, 34 are arranged in the flanges 14, 15 to project into the spaces 31, 32.

Les plots 33, 34 sont montés dans des logements 35 communiquant avec les espaces 31, 32 de manière que la pression qui règne dans ces espaces soit appliquée de part et d'autre desdits plots qui sont par ailleurs poussés par des ressorts 36, faiblement contraints, de manière qu'ils exercent une poussée tendant seulement à maintenir les lobes 27, 28 des flasques en appui contre la paroi des cavités circulaires 22, 23.The pads 33, 34 are mounted in housings 35 communicating with the spaces 31, 32 so that the pressure prevailing in these spaces is applied on either side of said pads which are also pushed by springs 36, slightly constrained , from so that they exert a push only tending to keep the lobes 27, 28 of the flanges in abutment against the wall of the circular cavities 22, 23.

Etant donné que la pression développée dans les espaces 31, 32 s'applique sur les deux côtés des plots 33, 34, ceux-ci sont constamment en équilibre de sorte que la contrainte qu'ils exercent sur la paroi des cavités du carter médian est celle découlant du tarage des ressorts 33a, 34a.Since the pressure developed in the spaces 31, 32 applies on both sides of the studs 33, 34, these are constantly in equilibrium so that the stress which they exert on the wall of the cavities of the median casing is that resulting from the calibration of the springs 33 a , 34 a .

En se référant à la fig. 1, on constate que chaque flasque 14 et 15 comporte une paroi ou face avant 37 tournée vers les pignons 13 et 17 et une paroi ou face arrière 38 tournée, pour le flasque 14, vers le carter antérieur 1 et, pour le flasque 15, vers le carter postérieur 2.Referring to fig. 1, it can be seen that each flange 14 and 15 has a front wall or face 37 facing the pinions 13 and 17 and a rear wall or face 38 facing, for the flange 14, towards the front casing 1 and, for the flange 15, to the rear housing 2.

Pour simplifier la description qui suit, seule une paroi avant et une paroi arrière sont décrites, les deux flasques étant rigoureusement semblables.To simplify the description which follows, only one front wall and one rear wall are described, the two flanges being strictly similar.

La paroi avant 37 comporte des segments annulaires 39, 40 (fig. 2 et 5) s'étendant depuis l'alésage contenant le palier 18 ou 18a jusqu'au fond de dents 41 et 42 des pignons primaire 13 et secondaire 17. Les segments 39, 40 constituent des portées d'appui pour les parties pleines des pignons 13, 17. A une extrémité, les segments annulaires 39, 40 sont reliés à des plateaux 43, 44 de forme sensiblement trapézoïdale et, à leur autre extrémité, ils sont reliés entre eux par une cloison 45 séparant le conduit d'admission 25 du conduit de refoulement 26.The front wall 37 comprises annular segments 39, 40 (FIGS. 2 and 5) extending from the bore containing the bearing 18 or 18 a to the bottom of the teeth 41 and 42 of the primary gears 13 and secondary 17. The segments 39, 40 constitute bearing surfaces for the solid parts of the pinions 13, 17. At one end, the annular segments 39, 40 are connected to plates 43, 44 of substantially trapezoidal shape and, at their other end, they are connected to each other by a partition 45 separating the intake duct 25 from the discharge duct 26.

La fig. 5 montre que la cloison 45 présente avantageusement une forme sensiblement en losange.Fig. 5 shows that the partition 45 advantageously has a substantially diamond shape.

La fig. 2 fait apparaître que la dimension de la cloison 45 et aussi sa forme sont déterminées pour correspondre à la mesure occupée par au moins un entredent des pignons 13, 17 afin qu'il ne puisse jamais y avoir communication directe entre le conduit d'admission 25 et le conduit de refoulement 26 lorsque les pignons tournent.Fig. 2 shows that the dimension of the partition 45 and also its shape are determined to correspond to the measurement occupied by at least one of the gable ends 13, 17 so that there can never be direct communication between the intake duct 25 and the discharge conduit 26 when the pinions rotate.

Pour le même motif, les segments annulaires 39, 40, les plateaux 43, 44 et la cloison 45 de chaque flasque sont coplanaires pour prendre appui en permanence contre les pignons 13 et 17. Ce qui précède montre que les plateaux 43, 44 séparent les zones haute et basse pressions.For the same reason, the annular segments 39, 40, the plates 43, 44 and the partition 45 of each flange are coplanar to bear permanently against the pinions 13 and 17. The above shows that the plates 43, 44 separate the high and low pressure zones.

La partie de la paroi avant 37 ne devant pas prendre appui contre la face latérale des pignons est fraisée pour ménager une chambre 46 (fig. 5), respectivement 47 (fig. 1), de chaque côté des pignons primaire 13 et secondaire 17.The part of the front wall 37 which should not bear against the lateral face of the pinions is milled to provide a chamber 46 (fig. 5), respectively 47 (fig. 1), on each side of the primary 13 and secondary 17 pinions.

Le dessin montre que les chambres 46 et 47 communiquent avec les cavités circulaires 22, 23 et contiennent, par conséquent, du fluide se trouvant à la même pression que celle qui règne dans le conduit de refoulement 26.The drawing shows that the chambers 46 and 47 communicate with the circular cavities 22, 23 and therefore contain fluid which is at the same pressure as that which prevails in the discharge conduit 26.

Ce qui précède montre que la pression dans les chambres 46 et 47 s'exerce sur toute la surface latérale des flasques avant 14 et arrière 15 laissée libre par les segments circulaires 39, 40, les plateaux 43, 44 et la cloison 45.The above shows that the pressure in the chambers 46 and 47 is exerted on the entire lateral surface of the front flanges 14 and rear 15 left free by the circular segments 39, 40, the plates 43, 44 and the partition 45.

Cette pression tend par conséquent à écarter les flasques 14, 15 des parois latérales des pignons 13, 17.This pressure therefore tends to separate the flanges 14, 15 from the side walls of the pinions 13, 17.

La paroi arrière 38 de chaque flasque est représentée par la fig. 6 qui montre que cette paroi présente une saignée 48 présentant sensiblement la forme de la lettre W, et dans laquelle est disposé un joint d'étanchéité 49 se terminant à ses deux extrémités par des sabots de retenue 50, 51 (fig. 6). De façon connue, le joint d'étanchéité 49 est muni d'une garniture anti-extrusion 52.The rear wall 38 of each flange is shown in FIG. 6 which shows that this wall has a groove 48 having substantially the shape of the letter W, and in which is disposed a seal 49 ending at its two ends by retaining shoes 50, 51 (fig. 6). In known manner, the seal 49 is provided with an anti-extrusion packing 52.

Le joint 49 présente des bossettes 53 pour délimiter des encoches 53a et permettre au fluide, se trouvant dans les cavités circulaires 22, 23 et venant contre la paroi arrière 38 de chaque flasque, de pousser le joint contre le carter antérieur 1 et, respectivement le carter postérieur 2, tout en exerçant sur la face arrière de chaque flasque une pression.The seal 49 has bosses 53 to delimit notches 53a and allow the fluid, being in the circular cavities 22, 23 and coming against the rear wall 38 of each flange, to push the seal against the front casing 1 and, respectively, the rear casing 2, while exerting pressure on the rear face of each flange.

La dimension de la saignée 48 et du joint d'étanchéité 49, dont les sabots 50 sont disposés dans les lobes 27, 28, est déterminée pour que la surface sur laquelle s'applique la pression du fluide provenant du conduit de refoulement 26 soit supérieure à celle sur laquelle s'exerce cette pression sur la face avant de chaque flasque.The dimension of the groove 48 and of the seal 49, the shoes 50 of which are arranged in the lobes 27, 28, is determined so that the surface on which the pressure of the fluid coming from the discharge conduit 26 is greater to that on which this pressure is exerted on the front face of each flange.

On fait ainsi en sorte qu'une pression différentielle est appliquée sur les flasques, cette pression différentielle s'exerçant toujours dans le sens pour lequel lesdits flasques sont poussés contre les pignons circulaires.This ensures that a differential pressure is applied to the flanges, this differential pressure always being exerted in the direction for which said flanges are pushed against the circular pinions.

En outre, il est avantageux que le joint d'étanchéité 49, se trouvant dans la face arrière de chaque flasque, exerce lui-même une légère pression pour que les flasques soient maintenus en appui contre les faces latérales des pignons lorsque la pompe n'est pas en action et que la pression dans le conduit de refoulement 26 tende à s'égaliser avec la pression dans le conduit d'admission 25.In addition, it is advantageous that the seal 49, located in the rear face of each flange, exerts itself a slight pressure so that the flanges are held in abutment against the lateral faces of the pinions when the pump is is not in action and that the pressure in the discharge duct 26 tends to equalize with the pressure in the intake duct 25.

Pour que le corps flottant 4 soit indépendant de contraintes dues à des dilatations différentielles éventuelles, on fait en sorte que la somme des épaisseurs des flasques 14, 15 et des pignons 13, 17 soit légèrement inférieure à la largeur du carter médian 3, le centrage du corps flottant étant assuré par les joints d'étanchéité 49 et la pression différentielle qui pousse les flasques 14, 15 l'un vers l'autre contre les faces latérales des pignons 13 et 17.So that the floating body 4 is independent of stresses due to possible differential expansions, it is made so that the sum of the thicknesses of the flanges 14, 15 and the pinions 13, 17 is slightly less than the width of the median casing 3, the centering of the floating body being provided by the seals 49 and the differential pressure which pushes the flanges 14, 15 towards each other against the lateral faces of the pinions 13 and 17.

Par ailleurs, les lobes 27 et 28 s'étendent de préférence sur un arc de cercle inférieur à 90°, les flasques 14 et 15 étant empêchés de basculer par les plots 33, 34 qui maintiennent lesdits lobes 27 et 28 contre la paroi des cavités circulaires 22, 23, ce qui permet également de compenser d'éventuelles dilatations différentielles pouvant se produire entre les flasques 14, 15 et le carter médian 3.Furthermore, the lobes 27 and 28 preferably extend over an arc of a circle less than 90 °, the flanges 14 and 15 being prevented from tilting by the studs 33, 34 which hold said lobes 27 and 28 against the wall of the cavities. circular 22, 23, which also makes it possible to compensate for any differential expansions which may occur between the flanges 14, 15 and the median casing 3.

La fig. 6 montre que la face arrière des flasques 14 et 15 délimite des canaux 54, 55 faisant communiquer le conduit d'admission 25 par la cavité 24 avec une extrémité des rainures de lubrification 20 des coussinets 18, 18a et 19, 19a. Par ailleurs, la fig. 5 montre un évidement 56 pratiqué dans la face avant des flasques 14 et 15 entre les plateaux 43, 44 et la cloison 45. L'évidement 56 met la cavité 24 sous basse pression en communication avec les rainures de lubrification 20, de sorte que le fluide hydraulique circule dans lesdites rainures depuis l'évidement 56 jusqu'au canal 54 ou 55, ou inversement, selon le sens de rotation des arbres 1 et 16. En outre, chaque évidement 56 réduit la surface sur laquelle frottent les pignons.Fig. 6 shows that the rear face of the flanges 14 and 15 delimits channels 54, 55 communicating the intake duct 25 through the cavity 24 with one end of the lubrication grooves 20 of the bearings 18, 18 a and 19, 19 a . Furthermore, fig. 5 shows a recess 56 made in the front face of the flanges 14 and 15 between the plates 43, 44 and the partition 45. The recess 56 places the cavity 24 under low pressure in communication with the lubrication grooves 20, so that the hydraulic fluid circulates in said grooves from the recess 56 to the channel 54 or 55, or vice versa, according to the direction of rotation of the shafts 1 and 16. In addition, each recess 56 reduces the surface on which the pinions rub.

De cette manière, du fluide sous basse pression est amené dans les coussinets et au-delà de ceux-ci dans les espaces laissés libres par les arbres 11 et 16 à l'intérieur des carters 1, 2 et 3, c'est-à-dire que tous les espaces intérieurs de la pompe sont remplis de fluide sous basse pression à l'exception de ceux de ces espaces qui sont décrits dans ce qui précède et qui sont en communication avec le conduit de refoulement 26 qui fait régner la haute pression lorsque la pompe est en fonctionnement.In this way, fluid under low pressure is brought into the bearings and beyond these in the spaces left free by the shafts 11 and 16 inside the casings 1, 2 and 3, that is to say say that all the interior spaces of the pump are filled with fluid under low pressure with the exception of those of these spaces which are described in the foregoing and which are in communication with the discharge conduit 26 which makes the high pressure prevail when the pump is running.

Le fait que les espaces laissés libres par les arbres 11 et 16 à l'intérieur des carters 1, 2 et 3 soient remplis de fluide sous basse pression évite que les joints d'étanchéité 7, 8 et 9, qui isolent l'intérieur de la pompe de l'atmosphère, soient soumis à des pressions élevées qui pourraient provoquer des fuites.The fact that the spaces left free by the shafts 11 and 16 inside the casings 1, 2 and 3 are filled with fluid under low pressure prevents the seals 7, 8 and 9, which isolate the interior of the atmosphere pump, be subjected to high pressures which could cause leakage.

Dans ce qui précède, il a été précisé que la surface des faces arrière des flasques sur lesquels s'exerce la pression du conduit de refoulement 26 était supérieure à la surface de la face avant de ce flasque sur lequel s'exerce cette même pression, et il a été indiqué que ce résultat était obtenu par le fait que le joint d'étanchéité 49 est soumis à la haute pression.In the foregoing, it has been specified that the surface of the rear faces of the flanges on which the pressure of the discharge conduit 26 is exerted is greater than the surface of the front face of this flange on which this same pressure is exerted, and it has been indicated that this result is obtained by the fact that the seal 49 is subjected to high pressure.

Pour augmenter encore la pression différentielle devant exister, on fait en sorte que l'angle α sur lequel s'étend chacun des plateaux 43, 44 à partir de l'axe x₁, respectivement x₂, des arbres 11 et 16 (fig. 5) soit plus grand que l'angle β séparant les extrémités de la saignée 48 des axes x₁, x₂ ci-dessus.To further increase the differential pressure which must exist, we make sure that the angle α over which each of the plates 43, 44 extends from the axis x₁, respectively x₂, of the shafts 11 and 16 (fig. 5) is greater than the angle β separating the ends of the groove 48 from the axes x₁, x₂ above.

On obtient ainsi que la pression du conduit de refoulement 26 s'exerce sur la face arrière des flasques suivant une plus grande ouverture angulaire que sur la face avant.It is thus obtained that the pressure of the discharge conduit 26 is exerted on the rear face of the flanges at a greater angular opening than on the front face.

L'invention n'est pas limitée aux exemples de réalisation, représentés et décrits en détail, car diverses modifications peuvent y être apportées sans sortir de son cadre.The invention is not limited to the exemplary embodiments, shown and described in detail, since various modifications can be made thereto without departing from its scope.

Claims (16)

1 - Machine hydraulique du type à engrenages comportant au moins un jeu de deux pignons coopérants agencés pour tourner entre deux flasques mobiles en translation dans des cavités réalisées dans un carter médian fermé sur ses deux côtés opposés par des carters antérieur et postérieur, chaque flasque étant sensiblement équilibré en pression par la disposition entre ce flasque et le carter adjacent d'un système de joint, caractérisée en ce que les flasques (14, 15) supportant les pignons (13, 17) délimitent des lobes (27, 28) de même rayon de courbure que celui de cavités circulaires (22, 23) du carter médian (3) contenant lesdits flasques qui sont montés flottants a l'intérieur de ce carter médian (3) et en ce que des moyens de pression hydrauliques (26) appliquent les lobes des flasques (14, 15) contre ledit carter médian (3). 1 - Hydraulic machine of the gear type comprising at least one set of two cooperating pinions arranged to rotate between two flanges movable in translation in cavities made in a central casing closed on its two opposite sides by anterior and posterior casings, each flange being substantially balanced in pressure by the arrangement between this flange and the adjacent casing of a seal system, characterized in that the flanges (14, 15) supporting the pinions (13, 17) delimit lobes (27, 28) similarly radius of curvature than that of circular cavities (22, 23) of the central casing (3) containing said flanges which are mounted floating inside this central casing (3) and in that hydraulic pressure means (26) apply the lobes of the flanges (14, 15) against said median casing (3). 2 - Machine suivant la revendication 1, caractérisée en ce que les lobes sont appliqués contre le carter médian (3) par une pression différentielle qui est exercée entre la face arrière et la face avant des flasques (14, 15), pression qui est obtenue en mettant en communication des chambres (46, 47) délimitées sur la face avant tournée vers les pignons (13, 17) de chaque flasque avec des parties de la paroi arrière (38) des flasques délimités par une saignée (48) et en faisant communiquer lesdites chambres et des parties de la face arrière avec un conduit de refoulement (26) dans lequel une haute pression est produite. 2 - Machine according to claim 1, characterized in that the lobes are applied against the central casing (3) by a differential pressure which is exerted between the rear face and the front face of the flanges (14, 15), pressure which is obtained by connecting chambers (46, 47) delimited on the front face facing the pinions (13, 17) of each flange with parts of the rear wall (38) of the flanges delimited by a groove (48) and making communicating said chambers and parts of the rear face with a discharge conduit (26) in which a high pressure is produced. 3 - Machine suivant l'une des revendications 1 et 2, caractérisée en ce que les flasques (14, 15) délimitent, au-delà des lobes, des parties décolletées (29, 30) formant des espaces (31, 32) mettant en communication les chambres (46, 47) des faces avant des flasques avec les faces arrière de ceux-ci. 3 - Machine according to one of claims 1 and 2, characterized in that the flanges (14, 15) delimit, beyond the lobes, necked parts (29, 30) forming spaces (31, 32) connecting the chambers (46, 47) of the front faces of the flanges with the rear faces of the latter. 4 - Machine suivant l'une des revendications 1 à 3, caractérisée en ce que les lobes (27, 28) des flasques s'étendent sur un arc de cercle inférieur à 90°. 4 - Machine according to one of claims 1 to 3, characterized in that the lobes (27, 28) of the flanges extend over an arc of a circle less than 90 °. 5 - Machine suivant l'une des revendications 1 à 4, caractérisée par des plots (33) insérés dans les flasques (14, 15), lesdits plots étant poussés par des ressorts (36) pour prendre appui contre la paroi des cavités circulaires (22, 23) en maintenant les lobes (27, 28) contre la partie de ces cavités qui leur correspond. 5 - Machine according to one of claims 1 to 4, characterized by studs (33) inserted in the flanges (14, 15), said studs being pushed by springs (36) to bear against the wall of the circular cavities ( 22, 23) by holding the lobes (27, 28) against the part of these cavities which corresponds to them. 6 - Machine suivant l'une des revendications 1 à 5, caractérisée en ce que la saignée (48) de la face arrière des flasques (14, 15) contient un joint d'étanchéité (49) présentant des bossettes (53) et encoches (53a) pour délimiter des passages pour le fluide provenant du conduit de refoulement (26). 6 - Machine according to one of claims 1 to 5, characterized in that the groove (48) of the rear face of the flanges (14, 15) contains a seal (49) having bosses (53) and notches (53 a ) to delimit passages for the fluid coming from the discharge conduit (26). 7 - Machine suivant l'une des revendications 1 à 6, caractérisée en ce que le joint (49) exerce une poussée élastique contre le carter (1, 2) qui lui fait vis-à-vis. 7 - Machine according to one of claims 1 to 6, characterized in that the seal (49) exerts an elastic thrust against the casing (1, 2) which makes it vis-à-vis. 8 - Machine suivant l'une des revendications 1 à 7, caractérisée en ce que la face avant des flasques (14, 15) délimite des segments annulaires (39, 40) prolongés par des plateaux (43, 44) et reliés entre eux par une cloison (45) coplanaire auxdits segments annulaires et plateaux formant des portées pour la face latérale des pignons. 8 - Machine according to one of claims 1 to 7, characterized in that the front face of the flanges (14, 15) delimits annular segments (39, 40) extended by plates (43, 44) and interconnected by a partition (45) coplanar with said annular segments and plates forming spans for the lateral face of the pinions. 9 - Machine suivant l'une des revendications 1 à 8, caractérisée en ce que les segments annulaires (39, 40) s'étendent jusqu'au fond de dents (41, 42) des pignons (13, 17). 9 - Machine according to one of claims 1 to 8, characterized in that the annular segments (39, 40) extend to the bottom of the teeth (41, 42) of the pinions (13, 17). 10 - Machine suivant l'une des revendications 1 à 9, caractérisée en ce que la cloison (45), reliant les segments annulaires, est conformée pour correspondre à au moins un entredent (41, 42) des pignons (13, 17) en empêchant toute communication directe entre les conduits d'admission (25) et de refoulement (26). 10 - Machine according to one of claims 1 to 9, characterized in that the partition (45), connecting the annular segments, is shaped to correspond to at least one intermedent (41, 42) of the pinions (13, 17) in preventing any direct communication between the intake (25) and discharge (26) conduits. 11 - Machine suivant l'une des revendications 1 à 10, caractérisée en ce que les arbres (11, 16) de support des pignons (13, 17) sont montés dans les flasques (14, 15) par l'intermédiaire de coussinets ou paliers (18, 18a, 19, 19a) de plus faible largeur que l'épaisseur desdits flasques. 11 - Machine according to one of claims 1 to 10, characterized in that the shafts (11, 16) for supporting the pinions (13, 17) are mounted in the flanges (14, 15) by means of bearings or bearings (18, 18 a , 19, 19 a ) of narrower width than the thickness of said flanges. 12 - Machine suivant l'une des revendications 1 à 11, caractérisée en ce que la face arrière des flasques (14, 15) présente des canaux (54, 55) mettant en communication le conduit d'admission (25) avec des rainures de lubrification (20) des coussinets (18, 18a, 19, 19a). 12 - Machine according to one of claims 1 to 11, characterized in that the rear face of the flanges (14, 15) has channels (54, 55) communicating the intake duct (25) with grooves lubrication (20) of the bearings (18, 18 a , 19, 19 a ). 13 - Machine suivant l'une des revendications 1 à 12, caractérisée en ce que l'un des arbres (11) des pignons est relié à un arbre d'entrée (11a) par un accouplement de sorte que les arbres primaire (11) et secondaire (16) soient soumis aux mêmes contraintes de flexion. 13 - Machine according to one of claims 1 to 12, characterized in that one of the shafts (11) of the pinions is connected to an input shaft (11 a ) by a coupling so that the primary shafts (11 ) and secondary (16) are subjected to the same bending stresses. 14 - Machine suivant l'une des revendications 1 à 12, caractérisée en ce que les arbres (11, 16) sont montés pour coulisser axialement dans les flasques (14, 15). 14 - Machine according to one of claims 1 to 12, characterized in that the shafts (11, 16) are mounted to slide axially in the flanges (14, 15). 15 - Machine suivant l'une des revendications 1 à 14, caractérisée par un évidement (56) pratiqué dans la face avant des flasques entre chaque plateau (43, 44) et la cloison (45) pour provoquer une circulation entre les canaux (54, 55) et cet évidement en passant par les rainures de lubrification (20) des coussinets et pour limiter la surface de frottement des pignons. 15 - Machine according to one of claims 1 to 14, characterized by a recess (56) formed in the front face of the flanges between each plate (43, 44) and the partition (45) to cause circulation between the channels (54 , 55) and this recess passing through the lubrication grooves (20) of the bearings and to limit the friction surface of the pinions. 16 - Machine hydraulique du type à engrenages à corps flottant sensiblement telle que décrite et réprésentée aux dessins annexés. 16 - Hydraulic machine of the type with substantially floating body gears as described and shown in the accompanying drawings.
EP92402597A 1991-09-24 1992-09-22 Hydraulic gear type machine with floating body Expired - Lifetime EP0534836B1 (en)

Applications Claiming Priority (2)

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FR9111745 1991-09-24
FR9111745A FR2681647B1 (en) 1991-09-24 1991-09-24 HYDRAULIC MACHINE OF THE GEAR TYPE WITH FLOATING BODY.

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EP0534836A1 true EP0534836A1 (en) 1993-03-31
EP0534836B1 EP0534836B1 (en) 1995-12-06

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EP (1) EP0534836B1 (en)
JP (1) JP2660139B2 (en)
KR (1) KR0148493B1 (en)
AT (1) ATE131255T1 (en)
CA (1) CA2078956C (en)
DE (1) DE69206564T2 (en)
ES (1) ES2081591T3 (en)
FR (1) FR2681647B1 (en)

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US5624251A (en) * 1994-07-14 1997-04-29 Casappa S.P.A. Gear pump

Also Published As

Publication number Publication date
KR0148493B1 (en) 1999-01-15
FR2681647A1 (en) 1993-03-26
ATE131255T1 (en) 1995-12-15
ES2081591T3 (en) 1996-03-16
JP2660139B2 (en) 1997-10-08
KR930006326A (en) 1993-04-21
DE69206564D1 (en) 1996-01-18
CA2078956A1 (en) 1993-03-25
CA2078956C (en) 1997-12-09
FR2681647B1 (en) 1995-05-12
DE69206564T2 (en) 1996-06-05
EP0534836B1 (en) 1995-12-06
JPH05296156A (en) 1993-11-09
US5240393A (en) 1993-08-31

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