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EP1438508B1 - Flanged gear pump - Google Patents

Flanged gear pump Download PDF

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Publication number
EP1438508B1
EP1438508B1 EP02787497A EP02787497A EP1438508B1 EP 1438508 B1 EP1438508 B1 EP 1438508B1 EP 02787497 A EP02787497 A EP 02787497A EP 02787497 A EP02787497 A EP 02787497A EP 1438508 B1 EP1438508 B1 EP 1438508B1
Authority
EP
European Patent Office
Prior art keywords
discs
pinion
gear pump
driven
flanges
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02787497A
Other languages
German (de)
French (fr)
Other versions
EP1438508A1 (en
Inventor
Clément Kiefer
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.)
Pierburg Pump Technology France SARL
Original Assignee
Pierburg SARL
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Pierburg SARL filed Critical Pierburg SARL
Publication of EP1438508A1 publication Critical patent/EP1438508A1/en
Application granted granted Critical
Publication of EP1438508B1 publication Critical patent/EP1438508B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • 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
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • 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
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • 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
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • 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
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms

Definitions

  • the present invention relates to a gear pump comprising a pump body closed by a cover forming a cavity in which there is a driving pinion which can be rotated by a driving pin to which it is fixed, a driven pinion whose teeth cooperate with the teeth of the pinion driving so as to be rotated by it and two flanges located on either side of the driven pinion penetrating into a cavity made for this purpose in the pump body and the lid respectively, means being provided to exert pressure on the outer face of the flanges.
  • Such pumps are commonly used, such as oil pump, gasoline or diesel. They have the major disadvantage that the cover may be deformed under the effect of the pressure in the discharge zone causing axial play of the idler gear. The deformation of the lid causes a leakage zone between the discharge and the suction, so that the volumetric efficiency of the pump decreases.
  • the outer faces are subjected at least in part to the outlet pressure.
  • These sleeves have a circular shape substantially corresponding to the diameters of the gears with a flat corresponding to the median plane between the two gears. These sleeves are locked in rotation.
  • the flats form two by two a junction at the median plane between the two gears, where the risk of backflow is greatest.
  • the object of the invention is therefore to develop a pump of the type shown in the preamble whose lid is not likely to deform under the effect of pressure and which is a simpler design.
  • the pump according to the invention in which the flanges each consist of a disc integral with one end of the driven pinion, the discs and the driven pinion being concentric, the discs covering the teeth of the driven pinion.
  • the flanges rotate at the same time as the driven gear.
  • Only the driven gear is provided with flanges which cover its teeth, which makes the pumps according to the invention simpler to achieve.
  • the pressure exerted on the outer face of the flange disks prevents them from deforming so that there is virtually no axial leakage zone between the suction and the discharge as is the case in the pumps single gear.
  • the entire area of crossing teeth is covered by the discs, so that no junction along the median plane between the gears is likely to produce leakage.
  • the discs grip the teeth of the drive gear which prevents axial play of the gears.
  • the volumetric efficiency of the pump is improved.
  • the discs may have a larger diameter than the outer diameter of the pinion, although this is not mandatory.
  • the flanges serve as guidance for the rotation of the driven gear. It is therefore not necessary to have further flanges a guide axis, as are provided with the pumps of the state of the art.
  • the means for exerting pressure on the outer faces of the disks comprise a first and a second space located between the outer face of the disks and the bottom of the cavity formed in the pump body and in the lid. respectively, and in which substantially identical pressures are applied.
  • one channel it is preferable for one channel to pass through the driven gear from one side to the other bringing the first and second spaces into contact. It is thus certain that both disks are subjected to the same pressure.
  • the first and second spaces are brought into contact with the discharge zone of the pump. For this, we can provide a channel or a groove bringing into contact the discharge zone of the pump and at least one of the spaces.
  • the discs are hollowed out to gain weight.
  • the gear pump according to the invention consists mainly of a pump body (2) closed by a cover (3) having a main cavity in which there are two pinions (4, 5) whose teeth cooperate together.
  • the first pinion (4), the driving gear is driven by a driving shaft (1).
  • the driving gear (4) As soon as the driving gear (4) is rotating, it drives the second gear (5), the driven gear.
  • the pump has a suction zone on one side and a discharge zone on the other. Under the effect of the pressure difference between the discharge zone and the suction zone and the rotation of the teeth, the lid of the single pumps tends to deform, as shown in FIG. axial leakage (6) between the discharge zone and the suction zone, which reduces the volumetric efficiency of the pump and increases the axial play of the gears.
  • the normal circulation of the fluid in the pump is shown in Figure 1 as thick arrows, while the fluid reflux due to axial leakage is represented by finer arrows.
  • the gear pump of the invention is provided with a driven gear (5) reinforced by disks (8).
  • a driven gear (5) reinforced by disks (8).
  • a disc (8) integral with the pinion and which enters a cavity (10) formed for this purpose in the pump body (2) and in the lid (3) respectively.
  • a space is provided between the outer surface of the discs and the bottom of the cavity into which they penetrate.
  • the diameter of the discs corresponds to the diameter of the pinion with tolerances.
  • the pressure exerted on the outer face of the discs (8) prevents deformation thereof. Sealing between the discharge zone and the suction zone is thus ensured. Indeed, no junction along the median plane between the gears is likely to cause leakage unlike the pumps of the state of the art.
  • only the driven gear (5) is provided with flanges (8), which makes the pump according to the invention simpler and therefore more economical to manufacture.
  • the discs (8) being integral with the driven pinion (5), they seal even when the pressure exerted on the outer faces of the discs (8) is still low, especially when the pump starts.
  • the discs also fulfill the guide axis function of the driven gear (5), so that it is also possible to give up such an axis, which is not the case of pumps of the state of the art , the flanges can not rotate due to their shape.
  • the pressure on the outer face of the disks (8) is exerted by the pumped fluid through unrepresented communication cavities (10) with the discharge zone.
  • This communication can be carried out in the form of a channel or a groove.
  • the disks (8) are secured to the driven gear by appropriate means (7). To gain weight, it is preferable that the outer surface of the disks (8) is hollowed out.
  • the volumetric efficiency of the pump according to the invention is improved.
  • the discs provide better stability of the gears which have less play.

Landscapes

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

Description

La présente invention concerne une pompe à engrenage comprenant un corps de pompe fermé par un couverde formant une cavité dans laquelle se trouvent un pignon menant pouvant être entraîné en rotation par un axe menant auquel il est fixé, un pignon mené dont les dents coopèrent avec les dents du pignon menant de sorte à être entraîné en rotation par celui-ci et deux flasques situées de part et d'autre du pignon mené pénétrant dans une cavité pratiquée à cet effet dans le corps de pompe et le couvercle respectivement, des moyens étant prévus pour exercer une pression sur la face extérieure des flasques.The present invention relates to a gear pump comprising a pump body closed by a cover forming a cavity in which there is a driving pinion which can be rotated by a driving pin to which it is fixed, a driven pinion whose teeth cooperate with the teeth of the pinion driving so as to be rotated by it and two flanges located on either side of the driven pinion penetrating into a cavity made for this purpose in the pump body and the lid respectively, means being provided to exert pressure on the outer face of the flanges.

De telles pompes sont couramment utilisées, notamment comme pompe à huile, à essence ou à gas-oil. Elles ont pour inconvénient majeur que le couverde risque de se déformer sous l'effet de la pression régnant dans la zone de refoulement entraînant un jeu axial du pignon fou. La déformation du couvercle provoque une zone de fuite entre le refoulement et l'aspiration, si bien que le rendement volumétrique de la pompe diminue.Such pumps are commonly used, such as oil pump, gasoline or diesel. They have the major disadvantage that the cover may be deformed under the effect of the pressure in the discharge zone causing axial play of the idler gear. The deformation of the lid causes a leakage zone between the discharge and the suction, so that the volumetric efficiency of the pump decreases.

De nombreux documents (FR 1 239 211 A, US 3 046 902 A, DE 11 72 959 B, GB 661 772 A et GB 1 067 552 A) ont proposé d'intercaler entre les pignons et le boîtier quatre manchons coulissants munis de logements pour les axes des pignons. Ces manchons ont pour fonction de rendre étanche la pompe en s'appuyant sur les pignons. Pour cela, les faces extérieures des manchons sont soumises à une certaine pression. Dans le premier document les faces extérieures sont soumises à la pression d'entrée de la pompe, de sorte que le risque de reflux entre les faces latérales des pignons et les manchons n'est pas exdu, la pression régnant dans la zone de refoulement étant supérieure à la pression exercée sur les manchons. Dans les quatre autres documents, les faces extérieures sont soumises au moins en partie à la pression de sortie. Ces manchons ont une forme circulaire correspondant sensiblement au diamètres des pignons avec un méplat correspondant au plan médian entre les deux pignons. Ces manchons sont donc bloqués en rotation. Par ailleurs, les méplats forment deux à deux une jonction au niveau du plan médian entre les deux pignons, là où le risque de refoulement est le plus grand.Numerous documents (FR 1 239 211 A, US 3,046,902 A, DE 11 72 959 B, GB 661 772 A and GB 1 067 552 A) have proposed to insert between the gears and the housing four sliding sleeves provided with housings for the axes of the gables. These sleeves have the function of sealing the pump by leaning on the gears. For this, the outer faces of the sleeves are subjected to a certain pressure. In the first document the outer faces are subjected to the inlet pressure of the pump, so that the risk of reflux between the side faces of the pinions and the sleeves is not exuded, the pressure prevailing in the discharge zone being greater than the pressure exerted on the sleeves. In the other four documents, the outer faces are subjected at least in part to the outlet pressure. These sleeves have a circular shape substantially corresponding to the diameters of the gears with a flat corresponding to the median plane between the two gears. These sleeves are locked in rotation. In addition, the flats form two by two a junction at the median plane between the two gears, where the risk of backflow is greatest.

Ces pompes sont compliquées et nécessitent un ajustage précis des différentes pièces, ce qui les rend coûteuses et fragiles.These pumps are complicated and require precise adjustment of the different parts, which makes them expensive and fragile.

L'objectif de l'invention est donc de développer une pompe du type de celui présenté dans le préambule dont le couvercle ne risque pas de se déformer sous l'effet de la pression et qui soit d'une conception plus simple.The object of the invention is therefore to develop a pump of the type shown in the preamble whose lid is not likely to deform under the effect of pressure and which is a simpler design.

Cet objectif est atteint par la pompe selon l'invention dans laquelle les flasques sont constitués chacun d'un disque solidaire d'une extrémité du pignon mené, les disques et le pignon mené étant concentriques, les disques recouvrant les dents du pignon mené. Ainsi, les flasques tournent en même temps que le pignon mené. Seul le pignon mené est muni de flasques qui couvrent ses dents, ce qui rend les pompes conformes à l'invention plus simples à réaliser. La pression exercée sur la face extérieure des disques servant de flasques empêchent ceux-ci de se déformer de sorte qu'il ne se forme pratiquement pas de zone de fuite axiale entre l'aspiration et le refoulement comme c'est le cas dans les pompes à engrenage simples. En outre, toute la zone de croisement des dents est couverte par les disques, de sorte qu'aucune jonction le long du plan médian entre les pignons ne risque de produire de fuite. Par ailleurs, les disques enserrent les dents du pignon menant ce qui empêche un jeu axial des pignons. Le rendement volumétrique de la pompe s'en trouve amélioré. Les disques peuvent avoir un diamètre supérieur au diamètre extérieur du pignon, bien que ce ne soit pas obligatoire.This objective is achieved by the pump according to the invention in which the flanges each consist of a disc integral with one end of the driven pinion, the discs and the driven pinion being concentric, the discs covering the teeth of the driven pinion. Thus, the flanges rotate at the same time as the driven gear. Only the driven gear is provided with flanges which cover its teeth, which makes the pumps according to the invention simpler to achieve. The pressure exerted on the outer face of the flange disks prevents them from deforming so that there is virtually no axial leakage zone between the suction and the discharge as is the case in the pumps single gear. In addition, the entire area of crossing teeth is covered by the discs, so that no junction along the median plane between the gears is likely to produce leakage. Furthermore, the discs grip the teeth of the drive gear which prevents axial play of the gears. The volumetric efficiency of the pump is improved. The discs may have a larger diameter than the outer diameter of the pinion, although this is not mandatory.

Dans un mode privilégié de réalisation de l'invention, les flasques servent de guidage pour la rotation du pignon mené. Il n'est donc pas nécessaire d'avoir outre les flasques encore un axe de guidage, comme en sont munies les pompes de l'état de la technique.In a preferred embodiment of the invention, the flanges serve as guidance for the rotation of the driven gear. It is therefore not necessary to have further flanges a guide axis, as are provided with the pumps of the state of the art.

Il est conforme à l'invention que les moyens pour exercer une pression sur les faces extérieures des disques comprennent un premier et un second espace situés entre la face externe des disques et le fond de la cavité pratiquée dans le corps de pompe et dans le couvercle respectivement, et dans lesquels sont appliquées des pressions sensiblement identiques. Pour simplifier la pompe à engrenage, il est préférable qu'un canal traverse le pignon mené de part en part mettant en contact le premier et le second espaces. On est ainsi sûr que les deux disques sont soumis à la même pression. De même, il est préférable que les premier et second espaces soient mis en contact avec la zone de refoulement de la pompe. Pour cela, on pourra prévoir un canal ou une rainure mettant en contact la zone de refoulement de la pompe et l'un au moins des espaces.It is according to the invention that the means for exerting pressure on the outer faces of the disks comprise a first and a second space located between the outer face of the disks and the bottom of the cavity formed in the pump body and in the lid. respectively, and in which substantially identical pressures are applied. To simplify the gear pump, it is preferable for one channel to pass through the driven gear from one side to the other bringing the first and second spaces into contact. It is thus certain that both disks are subjected to the same pressure. Similarly, it is preferable that the first and second spaces are brought into contact with the discharge zone of the pump. For this, we can provide a channel or a groove bringing into contact the discharge zone of the pump and at least one of the spaces.

Dans un mode de réalisation privilégié, les disques sont évidés pour gagner en poids.In a preferred embodiment, the discs are hollowed out to gain weight.

L'invention sera décrite plus en détail ci-dessous à l'aide des fiaures suivantes

Figure 1 :
Vue en coupe longitudinale d'une pompe à engrenage ;
Figure 2 :
Vue en coupe transversale d'une pompe à engrenage de l'état de la technique avec un couvercle déformé ;
Figure 3 :
Vue en coupe transversale d'une pompe à engrenage selon l'invention.
The invention will be described in more detail below with the help of the following diagrams
Figure 1 :
Longitudinal sectional view of a gear pump;
Figure 2 :
Cross-sectional view of a gear pump of the state of the art with a deformed cover;
Figure 3:
Cross-sectional view of a gear pump according to the invention.

La pompe à engrenage conforme à l'invention est constituée principalement d'un corps de pompe (2) fermé par un couvercle (3) présentant une cavité principale dans laquelle se trouvent deux pignons (4, 5) dont les dents coopèrent ensemble. Le premier pignon (4), le pignon menant, est entraîné par un axe menant (1). Dès que le pignon menant (4) est en rotation, il entraîne le second pignon (5), le pignon mené. La pompe présente une zone d'aspiration d'un côté et une zone de refoulement de l'autre. Sous l'effet de la différence de pression entre la zone de refoulement et la zone d'aspiration et de la rotation des dents, le couvercle des pompes simples a tendance à se déformer, comme le montre la figure 2. Il apparaît alors une zone de fuite axiale (6) entre la zone de refoulement et la zone d'aspiration, ce qui diminue le rendement volumétrique de la pompe et augmente le jeu axial des pignons. La circulation normale du fluide dans la pompe est représentée à la figure 1 sous forme de flèches épaisses, tandis que le reflux de fluide dû à la fuite axiale est représenté par des flèches plus fines.The gear pump according to the invention consists mainly of a pump body (2) closed by a cover (3) having a main cavity in which there are two pinions (4, 5) whose teeth cooperate together. The first pinion (4), the driving gear, is driven by a driving shaft (1). As soon as the driving gear (4) is rotating, it drives the second gear (5), the driven gear. The pump has a suction zone on one side and a discharge zone on the other. Under the effect of the pressure difference between the discharge zone and the suction zone and the rotation of the teeth, the lid of the single pumps tends to deform, as shown in FIG. axial leakage (6) between the discharge zone and the suction zone, which reduces the volumetric efficiency of the pump and increases the axial play of the gears. The normal circulation of the fluid in the pump is shown in Figure 1 as thick arrows, while the fluid reflux due to axial leakage is represented by finer arrows.

Pour contourner ce problème, la pompe à engrenage de l'invention est munie d'un pignon mené (5) renforcé par des disques (8). A chaque extrémité du pignon mené (5) se trouve un disque (8) solidaire du pignon et qui pénètre dans une cavité (10) pratiquée à cet effet dans le corps de pompe (2) et dans le couvercle (3) respectivement. Un espace est ménagé entre la surface extérieure des disques et le fond de la cavité dans laquelle ils pénètrent. Le diamètre des disques correspond au diamètre du pignon aux tolérances près. Ainsi, les dents du pignon menant (4) sont enserrées dans la zone sensible de l'engrenage par les disques (8). La pression exercée sur la face extérieure des disques (8) empêche une déformation de ceux-ci. L'étanchéité entre la zone de refoulement et la zone d'aspiration est ainsi assurée. En effet, aucune jonction le long du plan médian entre les pignons ne risque de provoquer de fuite contrairement aux pompes de l'état de la technique. De plus, seul le pignon mené (5) est muni de flasques (8), ce qui rend la pompe conforme à l'invention plus simple et donc plus économique à fabriquer.To circumvent this problem, the gear pump of the invention is provided with a driven gear (5) reinforced by disks (8). At each end of the driven gear (5) is a disc (8) integral with the pinion and which enters a cavity (10) formed for this purpose in the pump body (2) and in the lid (3) respectively. A space is provided between the outer surface of the discs and the bottom of the cavity into which they penetrate. The diameter of the discs corresponds to the diameter of the pinion with tolerances. Thus, the teeth of the drive gear (4) are clamped in the sensitive area of the gear by the discs (8). The pressure exerted on the outer face of the discs (8) prevents deformation thereof. Sealing between the discharge zone and the suction zone is thus ensured. Indeed, no junction along the median plane between the gears is likely to cause leakage unlike the pumps of the state of the art. In addition, only the driven gear (5) is provided with flanges (8), which makes the pump according to the invention simpler and therefore more economical to manufacture.

Par ailleurs, les disques (8) étant solidaires du pignon mené (5), ils assurent l'étanchéité même lorsque la pression s'exerçant sur les faces extérieures des disques (8) est encore faible, notamment au démarrage de la pompe.Furthermore, the discs (8) being integral with the driven pinion (5), they seal even when the pressure exerted on the outer faces of the discs (8) is still low, especially when the pump starts.

Les disques remplissent également la fonction d'axe de guidage du pignon mené (5), de sorte qu'il est également possible de renoncer à un tel axe, ce qui n'est pas le cas des pompes de l'état de la technique, les flasques ne pouvant pas tourner en raison même de leur forme.The discs also fulfill the guide axis function of the driven gear (5), so that it is also possible to give up such an axis, which is not the case of pumps of the state of the art , the flanges can not rotate due to their shape.

Pour assurer une pression identique sur les deux disques, il est prévu un canal (9) mettant en contact les deux cavités (10) des disques (8).To ensure an identical pressure on the two disks, there is provided a channel (9) bringing the two cavities (10) of the disks (8) into contact.

La pression régnant sur la face extérieure des disques (8) est exercée par le fluide pompé grâce à une mise en communication non représentée des cavités (10) avec la zone de refoulement. Cette mise en communication peut être réalisée sous la forme d'un canal ou d'une rainure.The pressure on the outer face of the disks (8) is exerted by the pumped fluid through unrepresented communication cavities (10) with the discharge zone. This communication can be carried out in the form of a channel or a groove.

Les disques (8) sont rendus solidaires du pignon mené par des moyens appropriés (7). Pour gagner du poids, il est préférable que la surface externe des disques (8) soit évidée.The disks (8) are secured to the driven gear by appropriate means (7). To gain weight, it is preferable that the outer surface of the disks (8) is hollowed out.

Grâce à une réduction importante des jeux, et donc à une diminution considérable des fuites entre la zone de refoulement et la zone d'aspiration, le rendement volumétrique de la pompe conforme à l'invention est amélioré. Par ailleurs, les disques assurent une meilleure stabilité des pignons qui ont ainsi moins de jeu.Thanks to a significant reduction of the games, and therefore to a considerable decrease in leaks between the discharge zone and the suction zone, the volumetric efficiency of the pump according to the invention is improved. In addition, the discs provide better stability of the gears which have less play.

Liste des références :List of references:

11
axe menantaxis leading
22
corps de pompepump body
33
couverclelid
44
pignon menantsprocket
55
pignon menédriven sprocket
66
zone de fuiteescape area
77
moyens de fixation du disquemeans of fixing the disc
88
disquesdiscs
99
canalchannel
1010
cavitéscavities

Claims (7)

  1. Gear pump, comprising
    - a pump body (2) closed by a cover (3) forming a cavity in which are located
    - a driving pinion (4) capable of being driven in rotation by a driving shaft (1) to which it is fixed,
    - a driven pinion (5) whose teeth cooperate with the teeth of the driving pinion (4) so that the driven pinion can be driven in rotation by the driving pinion and
    - two flanges located on both sides of the driven pinion protruding into a cavity (9) provided to this effect in the pump body (2) and the cover (3), respectively, means being provided for exerting a pressure on the external faces of the flanges,
    characterized in that the flanges are each constituted by a disc (8) integral with or securely attached to an end of the driven pinion (5), the discs (8) and the driven pinion (5) being concentric, the discs (8) covering the teeth of the driven pinion (5).
  2. Gear pump according to claim 1, characterized in that the flanges (8) act as guides for the rotation of the driven pinion (5).
  3. Gear pump according to one of the preceding claims, characterized in that the means for exerting a pressure on the external faces of the discs (8) comprise a first and a second space between the external faces of the discs (8) and the bottom of the cavity provided in the pump body (2) and in the cover (3) respectively, and in which are applied approximately identical pressures.
  4. Gear pump according to the preceding claim, characterized in that a canal (9) crosses the driven pinion (5) from one end to the other, so that the first and second spaces are made to communicate with each other.
  5. Gear pump according to any one of claims 3 and 4, characterized in that the first and second spaces are made to communicate with the discharge zone of the pump.
  6. Gear pump according to the preceding claim, characterized in that a canal or a groove is provided so that the discharge zone of the pump is made to communicate with at least one of the spaces.
  7. Gear pump according to any one of the preceding claims, characterized in that the discs (8) are hollowed out.
EP02787497A 2001-10-24 2002-10-23 Flanged gear pump Expired - Lifetime EP1438508B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR0113778A FR2831222B1 (en) 2001-10-24 2001-10-24 FLASKE GEAR PUMP
FR0113778 2001-10-24
PCT/EP2002/011834 WO2003036092A1 (en) 2001-10-24 2002-10-23 Flanged gear pump

Publications (2)

Publication Number Publication Date
EP1438508A1 EP1438508A1 (en) 2004-07-21
EP1438508B1 true EP1438508B1 (en) 2006-06-07

Family

ID=8868691

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02787497A Expired - Lifetime EP1438508B1 (en) 2001-10-24 2002-10-23 Flanged gear pump

Country Status (7)

Country Link
US (1) US7144234B2 (en)
EP (1) EP1438508B1 (en)
JP (1) JP4113125B2 (en)
KR (1) KR100887438B1 (en)
DE (1) DE60212165T2 (en)
FR (1) FR2831222B1 (en)
WO (1) WO2003036092A1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006025182A1 (en) 2006-05-30 2007-12-06 Trw Automotive Gmbh Gear pump, in particular for a power steering
JP2010038015A (en) * 2008-08-04 2010-02-18 Yamaha Motor Hydraulic System Co Ltd Gear pump
DE102011086435A1 (en) 2011-11-16 2013-05-16 Robert Bosch Gmbh Gear pump for conveying fluid, and for use in high-pressure injection system for internal combustion engine, particularly for motor vehicle, has pressure porting opening for discharging fluid to be conveyed from working chamber
JP5830435B2 (en) * 2012-06-06 2015-12-09 日立アプライアンス株式会社 Gear pump and refrigerator equipped with the same
ITUB20159736A1 (en) * 2015-12-21 2017-06-21 Bosch Gmbh Robert PUMPING GROUP FOR FUEL SUPPLEMENTATION, PREFERABLY GASOIL, TO AN INTERNAL COMBUSTION ENGINE
DE102016226069A1 (en) * 2016-12-22 2018-06-28 Robert Bosch Gmbh Gear machine and method of manufacturing a gear machine

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB661772A (en) * 1948-03-26 1951-11-28 Borg Warner Improvements in or relating to high pressure liquid pumps
US2915982A (en) * 1955-02-14 1959-12-08 Crandall Loid Rotary pump
DE1172959B (en) * 1957-04-09 1964-06-25 Bosch Gmbh Robert Gear pump or gear motor
FR1239211A (en) * 1958-10-30 1960-08-19 Borg Warner Hydraulic device
US3046902A (en) * 1959-03-23 1962-07-31 Clark Equipment Co Pump
GB1067552A (en) * 1962-12-10 1967-05-03 Dowty Hydraulic Units Ltd Improvements relating to gear pumps
JPS5838392A (en) * 1981-08-31 1983-03-05 Shimadzu Corp Gear pump or gear motor
JPS6075783A (en) * 1983-09-30 1985-04-30 Shimadzu Corp Gear pump or gear motor
JPH05248361A (en) * 1992-03-06 1993-09-24 Aisin Seiki Co Ltd Oil pump
JP2000161248A (en) 1998-12-01 2000-06-13 Kayaba Ind Co Ltd Hydraulic pump device

Also Published As

Publication number Publication date
JP4113125B2 (en) 2008-07-09
US20040265147A1 (en) 2004-12-30
EP1438508A1 (en) 2004-07-21
WO2003036092A1 (en) 2003-05-01
FR2831222B1 (en) 2005-08-26
US7144234B2 (en) 2006-12-05
KR20040048896A (en) 2004-06-10
JP2005506491A (en) 2005-03-03
DE60212165D1 (en) 2006-07-20
KR100887438B1 (en) 2009-03-10
FR2831222A1 (en) 2003-04-25
DE60212165T2 (en) 2007-04-12

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