EP0802327A1 - Gear pump - Google Patents

Gear pump Download PDF

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Publication number
EP0802327A1
EP0802327A1 EP97440038A EP97440038A EP0802327A1 EP 0802327 A1 EP0802327 A1 EP 0802327A1 EP 97440038 A EP97440038 A EP 97440038A EP 97440038 A EP97440038 A EP 97440038A EP 0802327 A1 EP0802327 A1 EP 0802327A1
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EP
European Patent Office
Prior art keywords
pressure chamber
piston
gear pump
diameter
head
Prior art date
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Granted
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EP97440038A
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German (de)
French (fr)
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EP0802327B1 (en
Inventor
Clément Kiefer
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Pierburg Pump Technology France SARL
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Europeenne De Mecanique Sa Ste
Europeenne De Mecanique Sa Ste
SOC EUROP DE MECANIQUE SA
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Publication of EP0802327A1 publication Critical patent/EP0802327A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F04C14/265—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels being obtained by displacing a lateral sealing face

Definitions

  • the present invention relates to a gear pump, preferably an external gear pump, comprising a pump body in which rest at least two opposite, meshing toothed wheels, one of which is connected to a drive, a hollow cylinder, fixed to one of the side walls of the gear pump and disposed in front of an opening in this side wall, a hollow cylinder in which rests a piston movable in the axial direction of the toothed wheels, the piston head of which, at rest, comes against the front face of the cogwheels under the effect of an elastic element.
  • the face of the gearwheels will be called the face of the gear, perpendicular to the axis of the gear, facing the aforementioned piston.
  • gear pumps are suitable for many hydraulic drives. In particular, they are often used as lubricating oil pumps in internal combustion engines.
  • the oil pressure produced by the gear pump cools the piston heads, lubricates and cools the piston slide track, main bearings and connecting rod bearings as well as the rocker arms and feeds the camshaft bearings.
  • the entrainment and the delivery of the liquid results from the fact that it penetrates into the free spaces between the toothed wheels meshing with each other, moves, in the direction of rotation, outside, along the wall of the pump body. , to penetrate the pressure zone and is expelled from the beams towards the pressure chamber by the mutual meshing of the teeth.
  • Gear pumps operating on the volumetric principle have the property that the delivery and pressure of the liquid increases proportionally as the speed of rotation increases. Consequently, in the absence of regulation, the permissible permanent operating pressure - for economical use and a sufficient service life - is exceeded.
  • this regulation technique is disadvantageously accompanied by a significant power dissipation from the gear pump, which can reach, for example, around 1300 W for a delivery of 10 liters / minute; when the flow rate increases, the power dissipation decreases only relatively little.
  • An object of the present invention is to configure the gear pump described at the outset so as to achieve a substantial reduction in power dissipation and to prevent foaming.
  • Another object of the invention is to reduce the friction forces between the meshing wheels and the overpressure reducing device.
  • the elastic element may consist of a helical spring inserted between the rear face of the piston head and the internal face of the cover of the hollow cylinder.
  • the face of the piston head which faces the toothed wheel has a hollowed-out central part, the diameter of which is slightly less than the diameter of the bottom of the gaiters while the total diameter of the piston head is slightly greater than the diameter of the head circle of the gear wheel.
  • the piston is lightened and its inertia decreases.
  • the force of the support spring can be considerably reduced, which not only reduces the forces of friction between the piston head and the front face of the toothed wheel but still allows a much quieter operation of the pump.
  • the rear face of the piston on which the effect of the spring is exerted and which constitutes a back-pressure chamber is simply connected to the pressure chamber of the pump by a conduit d 'power can, in particular, pass through the piston head or pass through the wall of the pump body.
  • the back-pressure chamber is also provided with a second return conduit towards the suction chamber.
  • This return pipe to the suction chamber is fitted with a calibrated valve.
  • the back-pressure chamber is provided with a conduit leading towards the outside of the pump, in particular a conduit allowing the return to a reservoir of the fluid transported by the pump.
  • a diameter of the return duct is provided which is greater than the diameter of the supply duct of the back-pressure chamber.
  • the liquid is discharged in such a way that the liquid penetrates, suction side, in the suction chamber (2) of the pump, in the free spaces of the gear wheels (4, 5) in engagement, arranged in the pump body (3); it moves, from the outside, along the wall of the pump body, in the direction of rotation of the wheels, in the direction of the discharge side of the pump and is expelled from the teeth by the mutual meshing of the teeth. Since each entry, before complete emptying, is closed by the corresponding tooth of the opposite toothed wheel, this results here in what is called a crushing liquid which is derived in the pressure chamber (6) through bores not shown in order to avoid loss of energy and a bumpy running of the toothed wheels.
  • the toothed wheels one of which, for example the wheel (4) is connected to a drive element (20), not shown in FIGS. 1 and 2, turns with a very small clearance in the radial and axial direction between them and the pump body.
  • a through hole (8) arranged coaxially with the toothed wheel, a hole the surface of which is similar to the surface of the head circle of the teeth of the gear wheel.
  • a hollow cylinder (9) integral with the wall (7) of the pump body.
  • the cylinder (9) and the wall (7) may consist of two separate integral parts.
  • the cylinder body and the wall (7) came from one piece and the bottom of the displacement is closed by a cover.
  • the inside diameter of the hollow cylinder coincides with the diameter of the through hole.
  • a piston (10) which, in the embodiment illustrated in Figures 1 and 2, has the shape of a hollow cylinder whose piston head (11) flat, at rest, comes against the front face of the toothed wheel. Since the surface of the piston head is similar to the surface of the head circle of the teeth of the toothed wheel, the front face of the latter is completely covered by the piston head.
  • a cylindrical helical pressure spring (12) whose spring force presses, in the axial direction and against the front face of the toothed wheel, the piston head which completely covers this front face of the toothed wheel.
  • the piston When, in operation, a predetermined discharge is exceeded, the piston is, despite the force of the helical pressure spring, pushed inside the hollow cylinder, so that a slot opens between the piston head and the face front of the toothed wheel, that the excess discharge can flow, by means of this bypass, directly to the suction side, to the suction chamber of the gear pump, and that there is a drop in pressure.
  • the power dissipation decreases significantly and a smaller amount of liquid must be drawn into the circuit. Only the quantity of liquid which is actually useful is sucked up.
  • the use of the gear pump produced with a movable piston according to the invention reduces the power dissipation to 960 W. It also prevents the liquid from foaming.
  • the diameter of the piston (11) is slightly greater than the bore of the pump body (3) in which rests the gear (4) facing it.
  • the cylinder abuts against the edge of this bore. If the gear is not flush, but in very slight withdrawal, this results in very little play which advantageously reduces the frictional forces.
  • the piston head has a hollowed-out central zone E, the diameter of which is slightly less than the diameter of the wheel, at the bottom of the crossbeams. There is therefore no contact or friction between the central part of the piston and the central part of the gears or pinions.
  • the spring should provide a force of around 30 daN.
  • the spring only has to provide a force of the order of 5 daN. Spring size and therefore its price is significantly reduced and its assembly is also greatly facilitated.
  • the back pressure chamber (14) is connected to the suction chamber by a suction return duct (19) whose diameter is greater than the diameter of the duct d suction (13).
  • the return duct (19) is closed by a ball valve, comprising a sealing ball (15), on which pushes a valve spring (16), a stop (18) forming a plug.
  • This embodiment allows oil-tight circulation from the outside between the pressure chamber (6), the back-pressure chamber (14) and the suction chamber (2): it is a sealed internal circuit. This embodiment is particularly suitable for a pump placed outside a crankcase.
  • the back pressure chamber (14) is connected to the outside by a return duct (17).
  • This conduit (17) is itself closable by means of a calibrated valve comprising a ball (15), a valve spring (16) and a stop (18).
  • This embodiment having an open circuit between pressure chamber (6) - back pressure chamber (14) and outlet of the conduit (17), is particularly suitable for a pump placed in the fluid reservoir, for example at the inside of a crankcase.
  • the use of the additional calibrated valve limits the back pressure and thus facilitates the movement and the release of the piston, which allows more frank regulation.
  • the valve spring is chosen so that the valve opens at the desired control pressure.

Abstract

The pump has a casing (3) in which are mounted two gears (4,5) which are opposed and engaged and one of which is attached to a drive shaft (20). a hollow cylinder (9) is fixed to one of the lateral walls (7) of the pump and positioned in front of an opening (8) in the lateral wall. The cylinder receives a piston (10) which moves in the axial direction of the gears. The head of the piston, at rest, engages against the front face of the gear teeth under the force of a spring . The head of the piston completely covers the face of one of the gears and the central points of the piston and gear tooth ring are on the same axis. the rear face of the piston is subjected to the hydraulic pressure within the pressure chamber (6) via a passage (13).

Description

La présente invention concerne une pompe à engrenages, de préférence une pompe à engrenages extérieurs, comprenant un corps de pompe dans lequel reposent au moins deux roues dentées, opposées, en engrènement, dont une est raccordée à un entraînement, un cylindre creux, fixé à une des parois latérales de la pompe à engrenages et disposé devant une ouverture de cette paroi latérale, cylindre creux dans lequel repose un piston mobile dans le sens axial des roues dentées, dont la tête de piston, au repos, vient contre la face avant des roues dentées sous l'effet d'un élément élastique. Par commodité de langage, on appellera dans la suite de ce texte par "face avant des roues dentées" la face de l'engrenage, perpendiculaire à l'axe de l'engrenage, faisant face au piston précité.The present invention relates to a gear pump, preferably an external gear pump, comprising a pump body in which rest at least two opposite, meshing toothed wheels, one of which is connected to a drive, a hollow cylinder, fixed to one of the side walls of the gear pump and disposed in front of an opening in this side wall, a hollow cylinder in which rests a piston movable in the axial direction of the toothed wheels, the piston head of which, at rest, comes against the front face of the cogwheels under the effect of an elastic element. For convenience of language, in the rest of this text, the face of the gearwheels will be called the face of the gear, perpendicular to the axis of the gear, facing the aforementioned piston.

Du fait de leur structure assez simple accompagnée d'une précision de refoulement suffisante, les pompes à engrenages sont adaptées à de nombreux entraînements hydrauliques. En particulier, elles sont souvent utilisées comme pompes à huile de lubrification dans les moteurs à combustion interne. La pression d'huile produite par la pompe à engrenages refroidit les têtes de pistons, lubrifie et refroidit la voie de glissement de pistons, les paliers principaux et les coussinets de bielles ainsi que les culbuteurs et alimente les paliers d'arbres à cames. L'entraînement et le refoulement du liquide résulte du fait que celui-ci pénètre dans les entredents libérés des roues dentées engrenant entre elles, se déplace, dans le sens de rotation, à l'extérieur, le long de la paroi du corps de pompe, pour pénétrer dans la zone de pression et est expulsé des entredents en direction de la chambre de pression par l'engrènement mutuel des dents. Etant donné que chaque entredent est, avant le vidage complet, obturé par une dent de la roue dentée opposée, il en résulte ce qu'on appelle un liquide d'écrasement qui, pour éviter les pertes d'énergie et une marche heurtée de la pompe à engrenages, doit être dérivé dans la chambre de pression à travers des alésages ou des rainures.Due to their fairly simple structure accompanied by sufficient delivery precision, gear pumps are suitable for many hydraulic drives. In particular, they are often used as lubricating oil pumps in internal combustion engines. The oil pressure produced by the gear pump cools the piston heads, lubricates and cools the piston slide track, main bearings and connecting rod bearings as well as the rocker arms and feeds the camshaft bearings. The entrainment and the delivery of the liquid results from the fact that it penetrates into the free spaces between the toothed wheels meshing with each other, moves, in the direction of rotation, outside, along the wall of the pump body. , to penetrate the pressure zone and is expelled from the beams towards the pressure chamber by the mutual meshing of the teeth. Given that each entry is, before complete emptying, closed by a tooth on the opposite toothed wheel, this results in what is called a crushing liquid which, in order to avoid energy losses and a smooth running of the pump gears, must be diverted into the pressure chamber through bores or grooves.

Pour réduire les surpressions importantes se produisant au sein du liquide d'écrasement, certaines pompes comportent dans la paroi latérale du corps de pompe faisant face aux faces avant des deux engrenages, et placé en regard de la zone où les deux roues engrènent, un petit piston mobile, qu'un ressort arrière pousse contre les faces avant des roues engrenantes, et qui, sous l'effet de la surpression du liquide d'écrasement peut reculer et laisser s'écouler ce liquide en direction de la chambre d'aspiration. Ce dispositif permet de diminuer les surpressions locales qui peuvent atteindre ou même dépasser 8 à 15 bars. Cependant, la force du ressort doit être élevée, de sorte que lorsqu'il pousse le piston contre les faces avant des deux engrenages, il se créée un frottement d'où résulte une perte d'énergie non-négligeable.To reduce the significant overpressures occurring in the crushing liquid, certain pumps have in the side wall of the pump body facing the front faces of the two gears, and placed opposite the area where the two wheels mesh, a small movable piston, which a rear spring pushes against the front faces of the meshing wheels, and which, under the effect of the overpressure of the crushing liquid can move back and allow this liquid to flow in the direction of the suction chamber. This device makes it possible to reduce local overpressures which can reach or even exceed 8 to 15 bars. However, the force of the spring must be high, so that when it pushes the piston against the front faces of the two gears, friction is created, which results in a non-negligible loss of energy.

Les pompes à engrenages fonctionnant selon le principe volumétrique présentent la propriété selon laquelle le refoulement et la pression de liquide augmentent proportionnellement quand la vitesse de rotation augmente. Par conséquent, en l'absence de régulation, la pression de marche permanente admissible - pour une utilisation économique et une durée de vie suffisante - est dépassée. Pour pouvoir maintenir constant le refoulement quand la vitesse de rotation de la pompe à engrenages augmente et pour pouvoir ainsi maintenir constante la pression de marche permanente, on sait aussi prévoir, dans la conduite de pression raccordée à la chambre de pression de la pompe à engrenages, une soupape de détente qui s'ouvre en cas de dépassement d'une pression de marche permanente prédéterminée ; la pression est abaissée et le refoulement de liquide en excès est renvoyé dans le réservoir de liquide depuis la conduite de pression en passant par une conduite de retour. Mais cette technique de régulation est accompagnée de façon désavantageuse d'une dissipation de puissance non négligeable de la pompe à engrenages, qui peut atteindre par exemple environ 1300 W pour un refoulement de 10 litres/minute ; quand le débit augmente, la dissipation de puissance ne diminue que relativement peu.Gear pumps operating on the volumetric principle have the property that the delivery and pressure of the liquid increases proportionally as the speed of rotation increases. Consequently, in the absence of regulation, the permissible permanent operating pressure - for economical use and a sufficient service life - is exceeded. In order to be able to keep the discharge constant when the speed of rotation of the gear pump increases and in order to be able to keep the permanent running pressure constant, it is also known to provide, in the pressure line connected to the pressure chamber of the gear pump , an expansion valve which opens if a predetermined permanent operating pressure is exceeded; the pressure is lowered and the discharge of excess liquid is returned to the liquid reservoir from the pressure line via a return line. However, this regulation technique is disadvantageously accompanied by a significant power dissipation from the gear pump, which can reach, for example, around 1300 W for a delivery of 10 liters / minute; when the flow rate increases, the power dissipation decreases only relatively little.

A cela s'ajoute le fait que le débit de liquide qui reflue entraîne la formation de mousse dans le réservoir de liquide et que de la mousse peut par conséquent être aspirée.Added to this is the fact that the flow of liquid which flows back causes foaming in the liquid tank and that foam can therefore be sucked up.

Un objectif de la présente invention consiste à configurer la pompe à engrenages décrite au début de façon à obtenir une réduction sensible de la dissipation de puissance et à empêcher la formation de mousse.An object of the present invention is to configure the gear pump described at the outset so as to achieve a substantial reduction in power dissipation and to prevent foaming.

Un autre but de l'invention est de diminuer les forces de frottement entre les roues engrenantes et le dispositif réducteur de surpression.Another object of the invention is to reduce the friction forces between the meshing wheels and the overpressure reducing device.

C'est également un but de l'invention que de réduire le bruit de fonctionnement de la pompe.It is also an object of the invention to reduce the operating noise of the pump.

Ces buts sont atteints grâce à une pompe du type défini ci-dessus dans laquelle la tête de piston recouvre complètement la face avant d'une des roues dentées, que les points centraux de la tête de piston et du cercle de tête des dents de ladite roue dentée sont situés sur un même axe, et dans laquelle la face arrière du piston est soumise à la pression hydraulique régnant dans la chambre de pression par l'intermédiaire d'un conduit d'alimentation entre la chambre de pression et ladite face arrière.These aims are achieved by means of a pump of the type defined above in which the piston head completely covers the front face of one of the toothed wheels, that the central points of the piston head and of the head circle of the teeth of said toothed wheel are located on the same axis, and in which the rear face of the piston is subjected to the hydraulic pressure prevailing in the pressure chamber via a supply conduit between the pressure chamber and said rear face.

Grâce à la disposition co-axiale entre le piston et une roue dentée, il est possible d'augmenter le jeu entre la tête de piston et la face avant des engrenages et donc de diminuer les forces de frottement.Thanks to the co-axial arrangement between the piston and a toothed wheel, it is possible to increase the clearance between the piston head and the front face of the gears and therefore to reduce the frictional forces.

De préférence, l'élément élastique peut être constitué d'un ressort hélicoïdal inséré entre la face arrière de la tête de piston et la face interne du couvercle du cylindre creux.Preferably, the elastic element may consist of a helical spring inserted between the rear face of the piston head and the internal face of the cover of the hollow cylinder.

Selon un mode d'exécution préféré, la face de la tête de piston qui fait face à la roue dentée présente une partie centrale évidée, dont le diamètre est légèrement inférieur au diamètre du fond des entredents alors que le diamètre total de la tête de piston est légèrement supérieur au diamètre du cercle de tête de la roue dentée. De la sorte, seule la surface de la face avant de la roue correspondant à la couronne de dents peut se trouver en contact avec la tête de piston. Les forces de frottement s'en trouvent considérablement diminuées. De plus, le piston est allégé et son inertie diminue.According to a preferred embodiment, the face of the piston head which faces the toothed wheel has a hollowed-out central part, the diameter of which is slightly less than the diameter of the bottom of the gaiters while the total diameter of the piston head is slightly greater than the diameter of the head circle of the gear wheel. In this way, only the surface of the front face of the wheel corresponding to the crown of teeth can be in contact with the piston head. The friction forces are considerably reduced. In addition, the piston is lightened and its inertia decreases.

Grâce à la liaison entre chambre de pression et face arrière du piston, qui génère sur l'arrière du piston une contre-pression de plusieurs bars, la force du ressort d'appui peut être considérablement diminuée, ce qui non seulement diminue les forces de frottement entre tête de piston et face avant de roue dentée mais encore permet un fonctionnement beaucoup plus silencieux de la pompe.Thanks to the connection between the pressure chamber and the rear face of the piston, which generates a back pressure of several bars on the rear of the piston, the force of the support spring can be considerably reduced, which not only reduces the forces of friction between the piston head and the front face of the toothed wheel but still allows a much quieter operation of the pump.

Selon un premier mode de réalisation de la présente invention, la face arrière du piston sur laquelle s'exerce l'effet du ressort et qui constitue une chambre de contre-pression est simplement relié à la chambre de pression de la pompe par un conduit d'alimentation pouvant, notamment, passer à travers de la tête de piston ou passer par la paroi du corps de pompe.According to a first embodiment of the present invention, the rear face of the piston on which the effect of the spring is exerted and which constitutes a back-pressure chamber is simply connected to the pressure chamber of the pump by a conduit d 'power can, in particular, pass through the piston head or pass through the wall of the pump body.

Selon un deuxième mode de réalisation préféré de l'invention, la chambre de contre-pression est également munie d'un deuxième conduit de retour vers la chambre d'aspiration. Ce conduit de retour vers la chambre d'aspiration est muni d'un clapet taré.According to a second preferred embodiment of the invention, the back-pressure chamber is also provided with a second return conduit towards the suction chamber. This return pipe to the suction chamber is fitted with a calibrated valve.

Selon un troisième mode de réalisation préféré de la présente invention, la chambre de contre-pression est munie d'un conduit menant vers l'extérieur de la pompe, notamment un conduit permettant le retour vers un réservoir du fluide transporté par la pompe.According to a third preferred embodiment of the present invention, the back-pressure chamber is provided with a conduit leading towards the outside of the pump, in particular a conduit allowing the return to a reservoir of the fluid transported by the pump.

Dans les deux cas, on prévoit un diamètre du conduit de retour supérieur au diamètre du conduit d'alimentation de la chambre de contre-pression.In both cases, a diameter of the return duct is provided which is greater than the diameter of the supply duct of the back-pressure chamber.

La pompe à engrenages selon l'invention est représentée à titre illustratif sur le dessin et est décrite ci-dessous. Sur le dessin :

  • La figure 1 est une représentation générale dans l'espace des éléments constitutifs de la pompe à engrenages
  • La figure 2 est une représentation dans l'espace de la pompe à engrenages avec une coupe partielle ;
  • La figure 3 montre une vue schématique, en coupe verticale dans le plan de l'axe du cylindre creux, du premier mode de réalisation de l'invention.
  • La figure 4 montre une vue schématique, en coupe verticale dans le plan de l'axe du cylindre creux, d'un deuxième mode de réalisation préféré de l'invention.
  • La figure 5 montre une vue schématique, en coupe verticale dans le plan de l'axe de cylindre creux, d'un troisième mode de réalisation préféré de l'invention.
The gear pump according to the invention is shown by way of illustration in the drawing and is described below. On the drawing :
  • Figure 1 is a general representation in space of the components of the gear pump
  • Figure 2 is a spatial representation of the gear pump with a partial section;
  • FIG. 3 shows a schematic view, in vertical section in the plane of the axis of the hollow cylinder, of the first embodiment of the invention.
  • Figure 4 shows a schematic view, in vertical section in the plane of the axis of the hollow cylinder, of a second preferred embodiment of the invention.
  • Figure 5 shows a schematic view, in vertical section in the plane of the hollow cylinder axis, of a third preferred embodiment of the invention.

Des pièces identiques ou équivalentes portent les mêmes numéros de référence dans l'ensemble des figures.Identical or equivalent parts have the same reference numbers in all of the figures.

Dans la pompe à engrenages (1), le refoulement du liquide s'effectue de telle façon que le liquide pénètre, côté aspiration, dans la chambre d'aspiration (2) de la pompe, dans les entredents libérés des roues dentées (4, 5) en engrènement, disposées dans le corps de pompe (3) ; il se déplace, par l'extérieur, le long de la paroi du corps de pompe, dans le sens de rotation des roues, en direction du côté refoulement de la pompe et est expulsé des entredents par l'engrènement mutuel des dents. Etant donné que chaque entredent, avant le vidage complet, est fermé par la dent correspondante de la roue dentée opposée, il en résulte ici ce qu'on appelle un liquide d'écrasement qui est dérivé dans la chambre de pression (6) à travers des alésages non représentés afin d'éviter des pertes d'énergie et une marche heurtée des roues dentées. Les roues dentées, dont l'une, par exemple la roue (4) est raccordée à un élément d'entraînement (20), non représenté sur les figures 1 et 2, tournent avec un jeu des plus réduits dans le sens radial et axial entre elles et le corps de pompe. Dans la paroi latérale (7) du corps de pompe, opposée au côté entraînement de la pompe à engrenages, se trouve un trou de passage (8) disposé de façon coaxiale par rapport à la roue dentée, trou dont la surface est semblable à la surface du cercle de tête des dents de la roue dentée. Sur le côté extérieur de la paroi (7) du corps de pompe, devant le trou de passage, est disposé de façon coaxiale un cylindre creux (9) solidaire de la paroi (7) du corps de pompe. Le cylindre (9) et la paroi (7) peuvent être constitués de deux pièces distinctes solidaires. Comme représenté sur les figures 3, 4, 5, le corps du cylindre et la paroi (7) sont venus d'une pièce et le fond du cylindré est obturé par un couvercle. Le diamètre intérieur du cylindre creux coïncide avec le diamètre du trou de passage. Dans l'alésage du cylindre creux repose de façon mobile un piston (10), qui, dans le mode d'exécution illustré figures 1 et 2, présente la forme d'un cylindre creux dont la tête (11) de piston plane, au repos, vient contre la face avant de la roue dentée. Etant donné que la surface de la tête de piston est semblable à la surface du cercle de tête des dents de la roue dentée, la face avant de celle-ci est entièrement recouverte par la tête de piston. Entre la face interne du piston et la paroi de fond du cylindre creux, ou le couvercle du cylindre, est inséré un ressort de pression hélicoïdal cylindrique (12) dont la force de ressort presse, dans le sens axial et contre la face avant de la roue dentée, la tête de piston qui recouvre totalement cette face avant de la roue dentée.In the gear pump (1), the liquid is discharged in such a way that the liquid penetrates, suction side, in the suction chamber (2) of the pump, in the free spaces of the gear wheels (4, 5) in engagement, arranged in the pump body (3); it moves, from the outside, along the wall of the pump body, in the direction of rotation of the wheels, in the direction of the discharge side of the pump and is expelled from the teeth by the mutual meshing of the teeth. Since each entry, before complete emptying, is closed by the corresponding tooth of the opposite toothed wheel, this results here in what is called a crushing liquid which is derived in the pressure chamber (6) through bores not shown in order to avoid loss of energy and a bumpy running of the toothed wheels. The toothed wheels, one of which, for example the wheel (4) is connected to a drive element (20), not shown in FIGS. 1 and 2, turns with a very small clearance in the radial and axial direction between them and the pump body. In the side wall (7) of the pump body, opposite the drive side of the gear pump, is a through hole (8) arranged coaxially with the toothed wheel, a hole the surface of which is similar to the surface of the head circle of the teeth of the gear wheel. On the outside of the wall (7) of the pump body, in front of the through hole, is arranged coaxially a hollow cylinder (9) integral with the wall (7) of the pump body. The cylinder (9) and the wall (7) may consist of two separate integral parts. As shown in Figures 3, 4, 5, the cylinder body and the wall (7) came from one piece and the bottom of the displacement is closed by a cover. The inside diameter of the hollow cylinder coincides with the diameter of the through hole. In the bore of the hollow cylinder movably rests a piston (10), which, in the embodiment illustrated in Figures 1 and 2, has the shape of a hollow cylinder whose piston head (11) flat, at rest, comes against the front face of the toothed wheel. Since the surface of the piston head is similar to the surface of the head circle of the teeth of the toothed wheel, the front face of the latter is completely covered by the piston head. Between the internal face of the piston and the bottom wall of the hollow cylinder, or the cylinder cover, is inserted a cylindrical helical pressure spring (12) whose spring force presses, in the axial direction and against the front face of the toothed wheel, the piston head which completely covers this front face of the toothed wheel.

Lorsque, en fonctionnement, on dépasse un refoulement déterminé, le piston est, malgré la force du ressort de pression hélicoïdal, poussé à l'intérieur du cylindre creux, de sorte qu'une fente s'ouvre entre la tête de piston et la face avant de la roue dentée, que le refoulement en excès peut s'écouler, par le biais de cette dérivation, directement vers le côté aspiration, vers la chambre d'aspiration de la pompe à engrenages, et qu'il se produit une baisse de pression. De ce fait, la dissipation de puissance diminue d'une façon sensible et une quantité de liquide plus faible doit être entraînée dans le circuit. N'est aspirée que la quantité de liquide qui est effectivement utile. Par exemple, dans le cas d'une pompe à engrenages classique, sans piston mobile, et pour une vitesse de rotation de 3000 tours/minute, si la dissipation de puissance est de 1240 W pour un refoulement de 20 litres/minute, l'utilisation de la pompe à engrenages réalisée avec un piston mobile selon l'invention réduit à 960 W la dissipation de puissance. En outre, cela empêche le liquide de mousser.When, in operation, a predetermined discharge is exceeded, the piston is, despite the force of the helical pressure spring, pushed inside the hollow cylinder, so that a slot opens between the piston head and the face front of the toothed wheel, that the excess discharge can flow, by means of this bypass, directly to the suction side, to the suction chamber of the gear pump, and that there is a drop in pressure. As a result, the power dissipation decreases significantly and a smaller amount of liquid must be drawn into the circuit. Only the quantity of liquid which is actually useful is sucked up. For example, in the case of a conventional gear pump, without a movable piston, and for a rotation speed of 3000 revolutions / minute, if the power dissipation is 1240 W for a delivery of 20 liters / minute, the use of the gear pump produced with a movable piston according to the invention reduces the power dissipation to 960 W. It also prevents the liquid from foaming.

Comme on peut le voir sur la figure 2, ou encore sur les figures 3, 4, 5, le diamètre du piston (11) est légèrement supérieur à l'alésage du corps de pompe (3) dans lequel repose la roue dentée (4) qui lui fait face. Dans ce mode d'exécution, le cylindre vient en buttée contre le bord de cet alésage. Si l'engrenage n'est pas à fleur, mais en très léger retrait, il en résulte un très faible jeu qui diminue avantageusement les forces de frottement.As can be seen in FIG. 2, or also in FIGS. 3, 4, 5, the diameter of the piston (11) is slightly greater than the bore of the pump body (3) in which rests the gear (4) facing it. In this embodiment, the cylinder abuts against the edge of this bore. If the gear is not flush, but in very slight withdrawal, this results in very little play which advantageously reduces the frictional forces.

Cet agencement avantageux n'est pas possible dans les pompes où un petit piston de contre-pression est disposé en regard de la zone d'engrènement, entre les axes des deux roues.This advantageous arrangement is not possible in pumps where a small back-pressure piston is arranged opposite the meshing zone, between the axes of the two wheels.

Dans les modes de réalisation représentés sur les figures 3, 4, 5, la tête de piston présente une zone centrale évidée E, dont le diamètre est légèrement inférieur au diamètre de la roue, au fond des entredents. Il n'y a donc ni contact ni frottement entre la partie centrale du piston et la partie centrale des engrenages ou pignons.In the embodiments shown in FIGS. 3, 4, 5, the piston head has a hollowed-out central zone E, the diameter of which is slightly less than the diameter of the wheel, at the bottom of the crossbeams. There is therefore no contact or friction between the central part of the piston and the central part of the gears or pinions.

Comme on peut le voir par exemple sur la figure 3, grâce au conduit d'aspiration (13), lorsque la pression augmente dans la chambre de pression (6), la pression augmente de façon concomitante dans la partie du cylindre (9) à l'arrière du piston (10), qui forme une chambre de contre-pression 14. La fonction essentielle du ressort 12 dans cette configuration est alors de maintenir le piston 10 au démarrage de la pompe contre la roue dentée 4 afin de garantir une bonne étanchéité.As can be seen for example in FIG. 3, thanks to the suction duct (13), when the pressure increases in the pressure chamber (6), the pressure increases concomitantly in the part of the cylinder (9) to the rear of the piston (10), which forms a back-pressure chamber 14. The essential function of the spring 12 in this configuration is then to hold the piston 10 when the pump starts up against the toothed wheel 4 in order to guarantee good sealing.

A titre d'exemple, pour une pompe dans laquelle la pression dans la chambre de pression doit être régulée à 5 bars, et équipée d'une roue de diamètre 34 mm, en l'absence du conduit (13) permettant l'élévation de pression dans la chambre (14), le ressort devrait fournir un effort de l'ordre de 30 daN. Par contre, grâce à la contre-pression établie dans la chambre 14), le ressort n'a plus qu'à fournir un effort de l'ordre de 5 daN. La taille du ressort et donc son prix s'en trouvent nettement diminués et son montage est également grandement facilité.For example, for a pump in which the pressure in the pressure chamber must be regulated at 5 bars, and equipped with a impeller with a diameter of 34 mm, in the absence of the conduit (13) allowing the elevation of pressure in the chamber (14), the spring should provide a force of around 30 daN. By cons, thanks to the back pressure established in the chamber 14), the spring only has to provide a force of the order of 5 daN. Spring size and therefore its price is significantly reduced and its assembly is also greatly facilitated.

Dans la forme d'exécution montrée sur la figure 4, la chambre de contre-pression (14) est reliée à la chambre d'aspiration par un conduit de retour d'aspiration (19) dont le diamètre est supérieur au diamètre du conduit d'aspiration (13). Le conduit de retour (19) est obturé par un clapet à bille, comprenant une bille d'étanchéité (15), sur laquelle pousse un ressort de clapet (16), une butée (18) formant bouchon. Ce mode d'exécution permet une circulation, étanche vis à vis de l'extérieur, de l'huile entre la chambre de pression (6), la chambre de contre-pression (14) et la chambre d'aspiration (2) : il s'agit d'un circuit interne étanche. Ce mode d'exécution convient particulièrement à une pompe placée à l'extérieur d'un carter moteur.In the embodiment shown in Figure 4, the back pressure chamber (14) is connected to the suction chamber by a suction return duct (19) whose diameter is greater than the diameter of the duct d suction (13). The return duct (19) is closed by a ball valve, comprising a sealing ball (15), on which pushes a valve spring (16), a stop (18) forming a plug. This embodiment allows oil-tight circulation from the outside between the pressure chamber (6), the back-pressure chamber (14) and the suction chamber (2): it is a sealed internal circuit. This embodiment is particularly suitable for a pump placed outside a crankcase.

Dans le mode d'exécution illustré par la figure 5, la chambre de contre-pression (14) est reliée vers l'extérieur par un conduit de retour (17). Ce conduit (17) est lui-même obturable au moyen d'un clapet taré comprenant une bille (15), un ressort de clapet (16) et une butée (18). Ce mode d'exécution présentant un circuit ouvert entre chambre de pression (6) - chambre de contre-pression (14) et sortie du conduit (17), convient particulièrement à une pompe placée dans le réservoir de fluide, par exemple à l'intérieur d'un carter moteur.In the embodiment illustrated in Figure 5, the back pressure chamber (14) is connected to the outside by a return duct (17). This conduit (17) is itself closable by means of a calibrated valve comprising a ball (15), a valve spring (16) and a stop (18). This embodiment having an open circuit between pressure chamber (6) - back pressure chamber (14) and outlet of the conduit (17), is particularly suitable for a pump placed in the fluid reservoir, for example at the inside of a crankcase.

Dans les deux modes d'exécution représentés sur les figures 4 et 5, l'utilisation du clapet taré supplémentaire limite la contre-pression et ainsi facilite le déplacement et le dégagement du piston, ce qui permet une régulation plus franche. Le ressort du clapet est choisi de telle manière à ce que le clapet s'ouvre à la pression de régulation voulue.In the two embodiments shown in FIGS. 4 and 5, the use of the additional calibrated valve limits the back pressure and thus facilitates the movement and the release of the piston, which allows more frank regulation. The valve spring is chosen so that the valve opens at the desired control pressure.

Claims (8)

Une pompe à engrenages, comprenant un corps de pompe (3) dans lequel reposent au moins deux roues dentées (4, 5) opposées, en engrènement, dont une est raccordée à un entraînement (20), un cylindre creux (9), fixé à une des parois latérales (7) de la pompe à engrenages (1) et disposé devant une ouverture (8) de la paroi latérale (7), cylindre creux (9) dans lequel repose un piston (10) mobile dans le sens axial des roues dentées (4, 5), dont la tête de piston (11), au repos, vient contre la face avant des roues dentées (4, 5), sous l'effet d'un élément élastique caractérisé en ce que la tête de piston (11) recouvre complètement la face avant d'une des roues dentées (4, 5), que les points centraux de la tête de piston (11) et du cercle de tête des dents de ladite roue dentée sont situés sur un même axe, et en ce que la face arrière du piston est soumise à la pression hydraulique régnant dans la chambre de pression (6) par l'intermédiaire d'un conduit d'alimentation (13) entre ladite chambre de pression (6) et ladite face arrière, pour former une chambre de contre-pression (14).A gear pump, comprising a pump body (3) in which rest at least two opposite toothed gears (4, 5), one of which is connected to a drive (20), a fixed hollow cylinder (9) to one of the side walls (7) of the gear pump (1) and arranged in front of an opening (8) of the side wall (7), hollow cylinder (9) in which rests a piston (10) movable in the axial direction toothed wheels (4, 5), the piston head (11) of which, at rest, comes against the front face of the toothed wheels (4, 5), under the effect of an elastic element characterized in that the head piston (11) completely covers the front face of one of the toothed wheels (4, 5), that the central points of the piston head (11) and of the head circle of the teeth of said toothed wheel are located on the same axis, and in that the rear face of the piston is subjected to the hydraulic pressure prevailing in the pressure chamber (6) by means of a supply (13) between said pressure chamber (6) and said rear face, to form a back pressure chamber (14). Pompe à engrenages selon la revendication 1 caractérisée en ce que ledit élément élastique est un ressort hélicoïdal (12) inséré entre la face arrière de la tête de piston (11) et la face interne du couvercle du cylindre creux (9).Gear pump according to claim 1 characterized in that said elastic element is a helical spring (12) inserted between the rear face of the piston head (11) and the internal face of the cover of the hollow cylinder (9). Pompe à engrenages selon l'une des revendications 1 ou 2 caractérisée en ce que la tête de piston présente face à la face avant de la roue dentée une partie centrale évidée E dont le diamètre est sensiblement égal ou inférieur au diamètre du fond des entredents de ladite roue dentée et en ce que le diamètre extérieur de la tête de piston est sensiblement égal ou supérieur au diamètre du cercle de tête de ladite roue dentée.Gear pump according to either of Claims 1 and 2, characterized in that the piston head has, facing the front face of the toothed wheel, a hollowed-out central part E, the diameter of which is substantially equal to or less than the diameter of the bottom of the entredents of said toothed wheel and in that the outside diameter of the piston head is substantially equal to or greater than the diameter of the head circle of said gear. Pompe à engrenages selon l'une des revendications 1 à 3, caractérisée en ce que la chambre de contre-pression (14) est reliée seulement à la chambre de pression (6) par un conduit d'alimentation passant à travers la tête de piston.Gear pump according to one of Claims 1 to 3, characterized in that the back-pressure chamber (14) is connected only to the pressure chamber (6) by a supply conduit passing through the piston head . Pompe à engrenages selon l'une des revendications 1 à 3, caractérisée en ce que la chambre de contre-pression (14) est reliée seulement à la chambre de pression (6) par un conduit d'alimentation passant à travers la paroi du corps de pompe.Gear pump according to one of claims 1 to 3, characterized in that the back pressure chamber (14) is connected only to the pressure chamber (6) by a supply conduit passing through the wall of the body pump. Pompe à engrenages selon l'une quelconque des revendications 1 à 3, caractérisée en ce que la chambre de contre-pression (14) est munie d'un conduit de retour (19) reliant ladite chambre de contre-pression et la chambre d'aspiration (2) et en ce que ledit conduit de retour (19) est muni d'un clapet taré (15, 16, 18).Gear pump according to any one of Claims 1 to 3, characterized in that the back-pressure chamber (14) is provided with a return duct (19) connecting said back-pressure chamber and the pressure chamber. suction (2) and in that said return duct (19) is provided with a calibrated valve (15, 16, 18). Pompe à engrenages selon l'une quelconque des revendications 1 à 3, caractérisée en ce que la chambre de contre-pression (14) est muni d'un conduit (17) reliant ladite chambre de contre-pression (14) à l'extérieur de la pompe et en ce que ledit conduit menant vers l'extérieur est muni d'un clapet taré (15, 16, 18).Gear pump according to any one of claims 1 to 3, characterized in that the back pressure chamber (14) is provided with a conduit (17) connecting said back pressure chamber (14) to the outside of the pump and in that said conduit leading to the outside is provided with a calibrated valve (15, 16, 18). Pompe à engrenages selon l'une des revendications 6 ou 7, caractérisée en ce que ledit conduit de retour (17, 19) présente un diamètre supérieur au diamètre du conduit d'alimentation (13).Gear pump according to one of claims 6 or 7, characterized in that said return duct (17, 19) has a diameter greater than the diameter of the supply duct (13).
EP97440038A 1996-04-17 1997-04-16 Gear pump Expired - Lifetime EP0802327B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9605052 1996-04-17
FR9605052A FR2747743A1 (en) 1996-04-17 1996-04-17 GEAR PUMP

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EP0802327A1 true EP0802327A1 (en) 1997-10-22
EP0802327B1 EP0802327B1 (en) 2000-06-28

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EP97440038A Expired - Lifetime EP0802327B1 (en) 1996-04-17 1997-04-16 Gear pump

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EP (1) EP0802327B1 (en)
AT (1) ATE194212T1 (en)
DE (1) DE69702368T2 (en)
ES (1) ES2147429T3 (en)
FR (1) FR2747743A1 (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001092673A2 (en) * 2000-06-01 2001-12-06 Pancanadian Petroleum Limited Fluid displacement apparatus and method
US6454010B1 (en) 2000-06-01 2002-09-24 Pan Canadian Petroleum Limited Well production apparatus and method
AT503856B1 (en) * 2006-06-30 2008-01-15 Tcg Unitech Systemtechnik Gmbh GEAR PUMP WITH CHANGING CONVEYING VOLUME
EP2203624A2 (en) * 2007-10-01 2010-07-07 Raymond C. Davis Oil well pump apparatus

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CZ2017330A3 (en) * 2017-06-08 2018-11-21 Emil Brabec A piston pump for liquids, especially for more viscous and pastelike media
RU210819U1 (en) * 2022-01-07 2022-05-05 Акционерное общество "Ремдизель" Oil pump of internal combustion engine

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2437791A (en) * 1943-06-26 1948-03-16 Borg Warner Pump with unloading bushing
GB1188977A (en) * 1966-06-24 1970-04-22 Werner Schindler Rotary Positive Diplacement Pump.

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2437791A (en) * 1943-06-26 1948-03-16 Borg Warner Pump with unloading bushing
GB1188977A (en) * 1966-06-24 1970-04-22 Werner Schindler Rotary Positive Diplacement Pump.

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001092673A2 (en) * 2000-06-01 2001-12-06 Pancanadian Petroleum Limited Fluid displacement apparatus and method
WO2001092673A3 (en) * 2000-06-01 2002-04-04 Pancanadian Petroleum Fluid displacement apparatus and method
US6454010B1 (en) 2000-06-01 2002-09-24 Pan Canadian Petroleum Limited Well production apparatus and method
AT503856B1 (en) * 2006-06-30 2008-01-15 Tcg Unitech Systemtechnik Gmbh GEAR PUMP WITH CHANGING CONVEYING VOLUME
EP2203624A2 (en) * 2007-10-01 2010-07-07 Raymond C. Davis Oil well pump apparatus
EP2203624A4 (en) * 2007-10-01 2011-08-17 Raymond C Davis Oil well pump apparatus

Also Published As

Publication number Publication date
DE69702368D1 (en) 2000-08-03
EP0802327B1 (en) 2000-06-28
ATE194212T1 (en) 2000-07-15
DE69702368T2 (en) 2001-03-29
ES2147429T3 (en) 2000-09-01
FR2747743A1 (en) 1997-10-24

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