EP1267077A1 - Gear pump with three shafts - Google Patents

Gear pump with three shafts Download PDF

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Publication number
EP1267077A1
EP1267077A1 EP02291491A EP02291491A EP1267077A1 EP 1267077 A1 EP1267077 A1 EP 1267077A1 EP 02291491 A EP02291491 A EP 02291491A EP 02291491 A EP02291491 A EP 02291491A EP 1267077 A1 EP1267077 A1 EP 1267077A1
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EP
European Patent Office
Prior art keywords
chamber
chambers
intake
gear
pressure
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Granted
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EP02291491A
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German (de)
French (fr)
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EP1267077B1 (en
Inventor
Guillaume Adam
Jean Cros
Gonzalo Portela Garnika
Denis Reverseau
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Renault SAS
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Renault SAS
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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
    • F04C14/02—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for several machines or pumps connected in series or in parallel
    • 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 the field of pumps. volumetric, i.e. whose theoretical flow is proportional to the speed, used in particular for the lubrication of combustion engines internal of road vehicles.
  • a positive displacement double gear pump comprising three pinions of pumping defining two intake chambers and two intake chambers discharge, a central supply duct connected to two ducts admission into the first and second respectively intake chamber, and a central discharge duct joining two discharge ducts respectively from the first and the second delivery chamber.
  • volumetric having more than three pinions defining between them more two intake chambers and two discharge chambers.
  • This type of pump is commonly used in systems such as than internal combustion engines of motor vehicles, the lubrication requires high flow and pressure from low revs.
  • the three gears define two by two, two intake chambers and two delivery chambers.
  • the two gears operate in parallel, driving two separate oil flows.
  • the advantage of this operating mode is to double the flow rate of a conventional single-gear pump, by adding only the volume of a pinion.
  • a second operating mode there can be only one intake chamber and a single oil discharge chamber to the outside, the two other rooms being connected, so that the oil discharged by a first gear ensures the supply of the second.
  • An oil pump must ensure in good conditions the engine lubrication, over its entire speed and temperature range. Through elsewhere, it must be compact, silent, and consume the minimum energy, at both low and high temperatures.
  • the object of the invention is to obtain high flow rates in a positive displacement pump with double gears, while keeping a size scaled down.
  • the pump comprises a first communication valve between the first intake chamber and the second discharge chamber, and a second communication valve between the second intake chamber and the first intake chamber discharge.
  • the pump has a single communication valve between the first chamber on the one hand, and between the second intake chamber and the first discharge chamber of other go.
  • the invention also relates to a method for controlling a double gear positive displacement pump with two chambers inlet and two discharge chambers depending on its pressure discharge.
  • the pump has a first mode of operation in which the intake chambers and the repression are not in communication, and a second mode of operation in which part of the flow discharged by a second gear is returned to the intake chamber of the first gear.
  • the pump behaves like a conventional pump with two gears operating in parallel, i.e. with two chambers intake 4, 7 and two discharge chambers 6, 8.
  • the two valves 17, 18 are closed.
  • the oil enters through the central supply duct 9, and gets distributes between the two intake ducts 11, 12.
  • the two pinions 1 and 2 propel the oil to the first discharge chamber 6, and the two sprockets 2 and 3 propel the oil to the second delivery chamber 8. It is then forced back through the conduits 14 and 16 towards the central discharge 13.
  • the first valve 17 opens gradually. At least part of the flow from the second chamber discharge 8 being returned to the first intake chamber 4, the pump is in a first pressure regeneration phase (cf. figure 2), where the increase in pressure as a function of the speed is more lower than between 0 and S1.
  • the first valve 17 is fully open and close the intake duct 11.
  • the pressure supplied by the pump continues to rise with the engine speed. But all the flow of the second gear 2, 3 enters the first intake chamber 4 (at volumetric efficiency), at a pressure identical to that of the second delivery chamber 8, except for pressure losses. Only one gear of the pump delivers, so that the energy consumption is almost divided by two, while the exhaust pressure of the pump increases more faster depending on the speed than between S1 and S2.
  • the pump proposed by the invention is therefore a double pump classic gear with the particularity of having means orientation of the oil making it possible to short-circuit one of the discharge to the other intake chamber at a pressure equal to that of the discharge.
  • valve 19 In FIG. 6, corresponding to the first operating mode, the valve 19 is completely closed. In Figure 7, corresponding to second operating mode, it partially frees the passage between the second discharge chamber and the first intake chamber. On the Figure 8, in accordance with the third operating mode, this passage is completely open, establishing in chamber 4 the pressure of discharge. Finally, in Figure 9, the valve clears the entry of the second inlet duct 12, and part of the flow from the first chamber of delivery 6 is returned to the second intake chamber 7. Thanks to this arrangement, the single valve 19 therefore alone performs the functions previously provided by the two valves 17, 18.
  • valve (s) proposed by the invention allows (tent) short-circuit one of the pump's outlets towards the intake to a pressure equal to that of the discharge. This measure saves power consumed by the pump in the operating phases of this one where the pressure is high and where the engine does not need all the pump flow, for example when the engine is cold.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

The double-mesh pump has three gears forming two inlet chambers (7) and two pressure chambers (6), a central feed pipe (9) connected to two inlet ducts (11, 12) leading to the inlet chambers, and a central pressure pipe connecting two pressure ducts (16) issuing from the pressure chambers. The pump incorporates pressure fluid guides (19) that are able to connect the inlet and pressure chambers and send at least part of the fluid from the second pressure chamber to the first inlet chamber. The first inlet chamber is connected to the second pressure chamber by one valve, and the second inlet chamber is connected to the first pressure chamber by another.

Description

La présente invention se rapporte au domaine des pompes volumétriques, c'est à dire dont le débit théorique est proportionnel à la vitesse, utilisées notamment pour la lubrification des moteurs à combustion interne de véhicules routiers.The present invention relates to the field of pumps. volumetric, i.e. whose theoretical flow is proportional to the speed, used in particular for the lubrication of combustion engines internal of road vehicles.

Elle trouve une application privilégiée, mais non exclusive sur une pompe volumétrique à double engrenage comprenant trois pignons de pompage définissant deux chambres d'admission et deux chambres de refoulement, un conduit d'alimentation central relié à deux conduits d'admission débouchant respectivement dans la première et dans la seconde chambre d'admission, et un conduit de refoulement central réunissant deux conduits de refoulement issus respectivement de la première et de la seconde chambre de refoulement.It finds a privileged, but not exclusive, application on a positive displacement double gear pump comprising three pinions of pumping defining two intake chambers and two intake chambers discharge, a central supply duct connected to two ducts admission into the first and second respectively intake chamber, and a central discharge duct joining two discharge ducts respectively from the first and the second delivery chamber.

Toutefois cette invention s'applique également à toute pompe volumétriques possédant plus de trois de pignons définissant entre eux plus de deux chambres d'admission et de deux chambres de refoulement.However, this invention also applies to any pump. volumetric having more than three pinions defining between them more two intake chambers and two discharge chambers.

Ce type de pompe est utilisé habituellement dans des systèmes, tels que des moteurs à combustion interne de véhicules automobiles, dont la lubrification nécessite un débit et une pression élevés dès les bas régimes.This type of pump is commonly used in systems such as than internal combustion engines of motor vehicles, the lubrication requires high flow and pressure from low revs.

Dans une telle pompe, un premier pignon menant engrène avec un second pignon mené, entraínant lui-même un troisième pignon mené. Les trois pignons définissent deux à deux, deux chambres d'admission et deux chambres de refoulement. Une telle pompe dispose de plusieurs possibilités de fonctionnement, dont notamment les deux modes suivants.In such a pump, a first pinion driving meshes with a second driven gear, itself driving a third driven gear. The three gears define two by two, two intake chambers and two delivery chambers. Such a pump has several possibilities of operation, including in particular the following two modes.

Selon un premier mode de fonctionnement, où les quatre chambres sont indépendantes, les deux engrenages fonctionnent en parallèle, en refoulant deux flux d'huile distincts. L'intérêt de ce mode de fonctionnement est de doubler le débit d'une pompe conventionnelle à simple engrenage, en rajoutant seulement le volume d'un pignon.According to a first mode of operation, where the four chambers are independent, the two gears operate in parallel, driving two separate oil flows. The advantage of this operating mode is to double the flow rate of a conventional single-gear pump, by adding only the volume of a pinion.

Selon un second mode de fonctionnement, on peut avoir une seule chambre d'admission et une seule chambre de refoulement d'huile vers l'extérieur, les deux autres chambres étant mises en communication, de sorte que l'huile refoulée par un premier engrenage assure l'alimentation du second.According to a second operating mode, there can be only one intake chamber and a single oil discharge chamber to the outside, the two other rooms being connected, so that the oil discharged by a first gear ensures the supply of the second.

De façon générale, lorsque le fluide à pomper a une faible viscosité, les fuites internes de la pompe et du moteur associé nécessitent de forts débits par tour de pompe (c'est à dire une pompe de grosse cylindrée), de façon à compenser ces pertes.Generally, when the fluid to be pumped has a low viscosity, internal leaks from the pump and associated motor require significant flow rates per pump revolution (i.e. a large displacement pump), in order to compensate for these losses.

bans le cas particulier de la lubrification des moteurs à combustion interne, les pompes volumétriques posent des problèmes d'utilisation : d'une part, la plage de viscosité de l'huile est très étendue, en raison des variations de température du moteur, et d'autre part la plage de vitesse de rotation de la pompe, directement liée au régime du moteur, est également très étendue.in the specific case of lubrication of combustion engines internal displacement pumps pose problems of use: apart, the viscosity range of the oil is very wide, due to variations engine temperature, and on the other hand the speed range of the pump, directly linked to the engine speed, is also very extensive.

Une pompe à huile doit assurer dans de bonnes conditions la lubrification du moteur, sur toute sa plage de régime et de température. Par ailleurs, elle doit être compacte, silencieuse, et consommer le minimum d'énergie, à basse comme à haute température.An oil pump must ensure in good conditions the engine lubrication, over its entire speed and temperature range. Through elsewhere, it must be compact, silent, and consume the minimum energy, at both low and high temperatures.

Les moteurs ont besoin d'un débit d'huile important pour être lubrifiés correctement dans toutes leurs conditions de fonctionnement. Généralement, les élévations de débit requises par les évolutions des moteurs sont obtenues en augmentant la cylindrée de la pompe.Engines need a large oil flow to be properly lubricated under all operating conditions. Generally, the flow increases required by changes in motors are obtained by increasing the displacement of the pump.

Or, ces augmentations de cylindrée n'ont de réel intérêt qu'aux hautes températures d'huile (120°C - 150°C), car en dessous de ces températures, le besoin en huile se réduit. En augmentant la cylindrée, on a donc, dans certaines situations, une pression d'huile dans le moteur, supérieure au juste nécessaire.However, these increases in displacement have real interest only high oil temperatures (120 ° C - 150 ° C), because below these temperatures, the need for oil is reduced. By increasing the displacement, we have therefore, in certain situations, an oil pressure in the engine, greater than just necessary.

En effet, le rendement des pompes volumétriques étant faible dans les plages de régime faible et moyen (environ jusqu'à 2000 tours /minute), les pompes doivent être dimensionnées en fonction de ce fonctionnement défavorable, et donc surdimensionnées aux régimes élevés.Indeed, the efficiency of positive displacement pumps being low in low and medium speed ranges (approximately up to 2000 revolutions / minute), the pumps must be sized according to this operation unfavorable, and therefore oversized at high speeds.

La taille des pompes à huile étant directement liée à leur cylindrée, les pompes sont donc de plus en plus encombrantes. Par ailleurs, plus les pompes sont volumineuses, plus elles sont bruyantes, car la quantité d'huile pulsée dans les engrenages augmente avec la cylindrée.The size of the oil pumps being directly linked to their displacement, the pumps are therefore increasingly bulky. In addition, the more pumps are larger, the louder they are, because the amount of oil pulsed in the gears increases with the displacement.

L'invention a pour but d'obtenir des débits importants dans une pompe volumétrique à double engrenage, tout en conservant une taille réduite.The object of the invention is to obtain high flow rates in a positive displacement pump with double gears, while keeping a size scaled down.

Dans ce but, elle propose de tirer profit de différentes combinaisons possibles entre les chambres d'admission et de refoulement pour réduire la cylindrée de la pompe. Ces combinaisons sont obtenues grâce à la présence de moyens d'orientation du fluide de pression entre les différentes chambres, plus précisément, entre les chambres d'admission et les chambres de refoulement.To this end, it proposes to take advantage of different possible combinations between inlet and outlet chambers to reduce the displacement of the pump. These combinations are obtained through the presence of means for orienting the pressure fluid between the different rooms, more precisely, between the admission rooms and the discharge chambers.

Selon un premier mode de réalisation, la pompe comporte un premier clapet de communication entre la première chambre d'admission et la seconde chambre de refoulement, et un second clapet de communication entre la seconde chambre d'admission et la première chambre de refoulement.According to a first embodiment, the pump comprises a first communication valve between the first intake chamber and the second discharge chamber, and a second communication valve between the second intake chamber and the first intake chamber discharge.

Selon un second mode de réalisation de l'invention, la pompe comporte un seul clapet de communication entre la première chambre d'admission et la seconde chambre de refoulement d'une part, et entre la seconde chambre d'admission et la première chambre de refoulement d'autre part.According to a second embodiment of the invention, the pump has a single communication valve between the first chamber on the one hand, and between the second intake chamber and the first discharge chamber of other go.

L'invention concerne également un procédé de commande d'une pompe volumétrique à double engrenage comportant deux chambres d'admission et deux chambres de refoulement en fonction de sa pression de refoulement.The invention also relates to a method for controlling a double gear positive displacement pump with two chambers inlet and two discharge chambers depending on its pressure discharge.

Selon ce procédé, la pompe dispose d'un premier mode de fonctionnement dans lequel les chambres d'admission et les chambres de refoulement ne sont pas en communication, et d'un second mode de fonctionnement dans lequel une partie du débit refoulé par un second engrenage est renvoyée vers la chambre d'admission du premier engrenage.According to this process, the pump has a first mode of operation in which the intake chambers and the repression are not in communication, and a second mode of operation in which part of the flow discharged by a second gear is returned to the intake chamber of the first gear.

Elle peut également disposer d'un troisième mode de fonctionnement dans lequel tout le débit refoulé par ce second engrenage est refoulée vers la chambre d'admission du premier engrenage, et d'un quatrième mode de fonctionnement dans lequel tout le débit refoulé par le second engrenage est refoulé vers la chambre d'admission du premier engrenage, et une partie du débit refoulé par le premier engrenage est renvoyée vers la chambre d'admission du second engrenage.It can also have a third operating mode in which all the flow discharged by this second gear is discharged towards the intake chamber of the first gear, and a fourth mode of operation in which all the flow discharged by the second gear is driven back to the intake chamber of the first gear, and part of the flow discharged by the first gear is returned to the chamber intake of the second gear.

D'autres caractéristiques et avantages de l'invention apparaítront clairement à la lecture de la description suivante d'un mode de réalisation de celle-ci, en se référant aux dessins annexés, sur lesquels :

  • les figures 1 à 4 montrent schématiquement le fonctionnement de la pompe proposée par l'invention,
  • la figure 5 illustre son fonctionnement, et
  • les figures 6 à 9 illustrent un mode de réalisation particulier de celle-ci. La pompe volumétrique à double engrenage des figures 1 à 4 comporte trois pignons 1, 2, 3, dont un premier pignon menant 1 engrenant avec un second pignon mené 2 de façon à constituer un premier engrenage 1, 2, et un second pignon mené engrenant avec le premier pignon mené, de façon à constituer un second engrenage 2, 3. Le premier engrenage 1, 2 présente une première chambre d'admission 4 et une première chambre de refoulement 6. Le second engrenage présente une seconde chambre d'admission 7 et une seconde chambre de refoulement 8. Les deux chambres d'admission 4, 6 sont reliées à un conduit d'alimentation central 9 par deux conduits d'admission 11, 12. Un conduit de refoulement central 13 réunit deux conduits de refoulement 14, 16, issus respectivement de la première et de la seconde chambre de refoulement 6, 8.Conformément à l'invention, la pompe comporte des moyens d'orientation du fluide de pression, capables de mettre en communication les chambres d'admission et les chambres de refoulement.Sur les figures 1 à 4, ces moyens d'orientation sont constitués par deux clapets 17, 18, pouvant respectivement mettre en communication la première chambre de refoulement 6 avec la seconde chambre d'admission 7, et la seconde chambre de refoulement 8 avec la première chambre d'admission 4.Conformément à l'invention, la pompe peut disposer des quatre modes de fonctionnement suivants.
  • un premier mode de fonctionnement dans lequel les chambres d'admission et les chambres de refoulement ne sont pas en communication directe, et les deux engrenages travaillent en parallèle,
  • un second mode de fonctionnement dans lequel une partie du débit refoulé par un second engrenage est renvoyée vers la chambre d'admission du premier engrenage,
  • un troisième mode de fonctionnement dans lequel tout le débit refoulé par ce second engrenage est refoulé vers la chambre d'admission du premier engrenage, et
  • un quatrième mode de fonctionnement dans lequel tout le débit refoulé par le second engrenage est refoulé vers la chambre d'admission du premier engrenage, et une partie du débit refoulé par le premier engrenage est renvoyée vers la chambre d'admission du second engrenage.
Other characteristics and advantages of the invention will appear clearly on reading the following description of an embodiment thereof, with reference to the accompanying drawings, in which:
  • FIGS. 1 to 4 schematically show the operation of the pump proposed by the invention,
  • FIG. 5 illustrates its operation, and
  • Figures 6 to 9 illustrate a particular embodiment thereof. The volumetric double gear pump of FIGS. 1 to 4 comprises three pinions 1, 2, 3, including a first driving pinion 1 meshing with a second driven pinion 2 so as to constitute a first gear 1, 2, and a second driven pinion with the first driven pinion, so as to constitute a second gear 2, 3. The first gear 1, 2 has a first inlet chamber 4 and a first delivery chamber 6. The second gear has a second inlet chamber 7 and a second discharge chamber 8. The two intake chambers 4, 6 are connected to a central supply duct 9 by two intake ducts 11, 12. A central discharge duct 13 joins two discharge ducts 14, 16, respectively from the first and second discharge chambers 6, 8. In accordance with the invention, the pump comprises means for orienting the pressure fluid, capable of bringing the intake chambers into communication. and the discharge chambers. In FIGS. 1 to 4, these orientation means consist of two valves 17, 18, which can respectively put the first discharge chamber 6 into communication with the second intake chamber 7, and the second delivery chamber 8 with the first inlet chamber 4. In accordance with the invention, the pump can have the following four operating modes.
  • a first operating mode in which the intake chambers and the discharge chambers are not in direct communication, and the two gears work in parallel,
  • a second operating mode in which part of the flow discharged by a second gear is returned to the inlet chamber of the first gear,
  • a third operating mode in which all the flow discharged by this second gear is discharged towards the inlet chamber of the first gear, and
  • a fourth mode of operation in which all the flow discharged by the second gear is discharged towards the inlet chamber of the first gear, and a part of the flow discharged by the first gear is returned towards the inlet chamber of the second gear.

En se reportant à la figure 5, illustrant l'évolution de la pression débitée par la pompe, en fonction du régime moteur, on distingue trois seuils de pression S1, 52, 53, qui définissent sur le graphe quatre zones correspondant aux modes de fonctionnement indiqués ci-dessus.Referring to Figure 5, illustrating the evolution of the pressure delivered by the pump, depending on the engine speed, there are three thresholds pressure S1, 52, 53, which define four zones on the graph corresponding to the operating modes indicated above.

Dans la première zone de fonctionnement, entre P = 0 et P = S1 (cf. figure 1), la pompe se comporte comme une pompe conventionnelle à deux engrenages fonctionnant en parallèle, c'est à dire avec deux chambres d'admission 4, 7 et deux chambres de refoulement 6, 8. Les deux clapets 17, 18 sont fermés. L'huile entre par le conduit d'alimentation central 9, et se répartit entre les deux conduits d'admission 11, 12. Les deux pignons 1 et 2 propulsent l'huile vers la première chambre de refoulement 6, et les deux pignons 2 et 3 propulsent l'huile vers la seconde chambre de refoulement 8. Elle est ensuite refoulée par les conduits 14 et 16 vers le conduit de refoulement central 13.In the first operating zone, between P = 0 and P = S1 (see figure 1), the pump behaves like a conventional pump with two gears operating in parallel, i.e. with two chambers intake 4, 7 and two discharge chambers 6, 8. The two valves 17, 18 are closed. The oil enters through the central supply duct 9, and gets distributes between the two intake ducts 11, 12. The two pinions 1 and 2 propel the oil to the first discharge chamber 6, and the two sprockets 2 and 3 propel the oil to the second delivery chamber 8. It is then forced back through the conduits 14 and 16 towards the central discharge 13.

Entre S1 et S2 (cf. figure 2), le premier clapet 17 s'ouvre progressivement. Au moins une partie du débit issu de la seconde chambre de refoulement 8 étant renvoyée vers la première chambre d'admission 4, la pompe se trouve dans une première phase de régénération de pression (cf. figure 2), où l'augmentation de la pression en fonction du régime est plus faible qu'entre 0 et S1.Between S1 and S2 (see Figure 2), the first valve 17 opens gradually. At least part of the flow from the second chamber discharge 8 being returned to the first intake chamber 4, the pump is in a first pressure regeneration phase (cf. figure 2), where the increase in pressure as a function of the speed is more lower than between 0 and S1.

Entre S2 et S3 (cf. figure 3), le premier clapet 17 est complètement ouvert et ferme le conduit d'admission 11. La pression fournie par la pompe continue à s'élever avec le régime du moteur. Mais tout le débit du second engrenage 2, 3 rentre dans la première chambre d'admission 4 (au rendement volumétrique près), à une pression identique à celle de la seconde chambre de refoulement 8, aux pertes de charge près. Seul un engrenage de la pompe débite, de sorte que la consommation d'énergie est presque divisée par deux, tandis que la pression à l'échappement de la pompe augmente plus vite en fonction du régime qu'entre S1 et S2.Between S2 and S3 (see Figure 3), the first valve 17 is fully open and close the intake duct 11. The pressure supplied by the pump continues to rise with the engine speed. But all the flow of the second gear 2, 3 enters the first intake chamber 4 (at volumetric efficiency), at a pressure identical to that of the second delivery chamber 8, except for pressure losses. Only one gear of the pump delivers, so that the energy consumption is almost divided by two, while the exhaust pressure of the pump increases more faster depending on the speed than between S1 and S2.

Lorsque P > S3 (cf. figure 4), le second clapet 18 s'ouvre, et au moins une partie du débit de la première chambre refoulement 7 est renvoyée vers la seconde chambre d'admission 6, de sorte qu'au delà de S3, la pente de la courbe est plus faible qu'entre S2 et S3 (cf. figure 5). On se trouve alors dans une deuxième phase de régénération de débit.When P> S3 (cf. FIG. 4), the second valve 18 opens, and at least part of the flow from the first discharge chamber 7 is returned to the second intake chamber 6, so that beyond S3, the slope of the curve is lower than between S2 and S3 (see Figure 5). We are then in a second flow regeneration phase.

La pompe proposée par l'invention est donc une pompe à double engrenage classique avec la particularité de posséder des moyens d'orientation de l'huile permettant de court-circuiter un des conduits de refoulement vers l'autre chambre d'admission à une pression égale à celle du refoulement.The pump proposed by the invention is therefore a double pump classic gear with the particularity of having means orientation of the oil making it possible to short-circuit one of the discharge to the other intake chamber at a pressure equal to that of the discharge.

Sur, les figures 6 à 9, correspondant respectivement aux mêmes modes de fonctionnement que les figures 1 à 4, les deux clapets sont remplacés par un clapet unique 19, qui remplace les deux clapets précédents. On, Figures 6 to 9, corresponding respectively to the same operating modes as Figures 1 to 4, the two valves are replaced by a single valve 19, which replaces the two previous valves.

Sur ces schémas, on reconnaít les trois pignons 1, 2, 3, les deux chambres d'admission 4, 7, les deux chambres de refoulement 6, 8, le conduit d'alimentation central 9, le conduit de refoulement central 13, le premier conduit d'admission 11 et les deux conduits de refoulement 14, 16. Quant au second conduit d'admission 12, il est ici représenté en pointillés pour des raisons de clarté.In these diagrams, we recognize the three pinions 1, 2, 3, both intake chambers 4, 7, the two discharge chambers 6, 8, the central supply duct 9, the central discharge duct 13, the first intake duct 11 and the two discharge ducts 14, 16. As for the second intake duct 12, it is shown here in dotted lines for the sake of clarity.

Sur la figure 6, correspondant au premier mode de fonctionnement, le clapet 19 est complètement fermé. Sur la figure 7, correspondant au second mode de fonctionnement, il libère partiellement le passage entre la seconde chambre de refoulement et la première chambre d'admission. Sur la figure 8, conformément au troisième mode de fonctionnement, ce passage est complètement ouvert, établissant dans la chambre 4 la pression de refoulement. Enfin, sur la figure 9, le clapet dégage l'entrée du second conduit d'admission 12, et une partie du débit de la première chambre de refoulement 6 est renvoyé vers la seconde chambre d'admission 7. Grâce à cette disposition, le clapet unique 19 assure donc à lui seul les fonctions assurées précédemment par les deux clapets 17, 18.In FIG. 6, corresponding to the first operating mode, the valve 19 is completely closed. In Figure 7, corresponding to second operating mode, it partially frees the passage between the second discharge chamber and the first intake chamber. On the Figure 8, in accordance with the third operating mode, this passage is completely open, establishing in chamber 4 the pressure of discharge. Finally, in Figure 9, the valve clears the entry of the second inlet duct 12, and part of the flow from the first chamber of delivery 6 is returned to the second intake chamber 7. Thanks to this arrangement, the single valve 19 therefore alone performs the functions previously provided by the two valves 17, 18.

En résumé, le ou les clapet(s) proposé(s) par l'invention permet(tent) de court-circuiter un des refoulements de la pompe vers l'admission à une pression égale à celle du refoulement. Cette mesure assure une économie de puissance consommée par la pompe dans les phases de fonctionnement de celle-ci où la pression est élevée et où le moteur n'a pas besoin de tout le débit de la pompe, par exemple quand le moteur est froid.In summary, the valve (s) proposed by the invention allows (tent) short-circuit one of the pump's outlets towards the intake to a pressure equal to that of the discharge. This measure saves power consumed by the pump in the operating phases of this one where the pressure is high and where the engine does not need all the pump flow, for example when the engine is cold.

Claims (9)

Pompe volumétrique à double engrenage (1, 2 ; 2, 3) comprenant trois pignons de pompage (1, 2, 3) définissant deux chambres d'admission (4, 7) et deux chambres de refoulement (6, 8), un conduit d'alimentation central (9) relié à deux conduits d'admission (11, 12) débouchant respectivement dans la première et dans la seconde chambre d'admission, et un conduit d'échappement central (13) réunissant deux conduits de refoulement (14, 16) issus respectivement de la première et de la seconde chambre de refoulement, caractérisé en ce qu'il comporte des moyens d'orientation du fluide de pression (17, 18 ; 19) capables de mettre en communication les chambres d'admission et les chambres de refoulement, de manière à renvoyer au moins une partie du débit issu de la seconde chambre de refoulement vers la première chambre d'admission.Volumetric double gear pump (1, 2; 2, 3) comprising three pumping pinions (1, 2, 3) defining two intake chambers (4, 7) and two discharge chambers (6, 8), a conduit central supply (9) connected to two intake ducts (11, 12) opening respectively into the first and second intake chambers, and a central exhaust duct (13) joining two discharge ducts (14 , 16) originating respectively from the first and from the second delivery chamber, characterized in that it comprises means for orienting the pressure fluid (17, 18; 19) capable of bringing the intake chambers into communication with the discharge chambers, so as to return at least part of the flow rate coming from the second discharge chamber to the first intake chamber. Pompe volumétrique selon la revendication 1, caractérisée en ce qu'elle comporte un premier clapet de communication (17) entre la première chambre d'admission (4) et la seconde chambre de refoulement (8), et un second clapet de communication (18) entre la seconde chambre d'admission (7) et la première chambre de refoulement (6).Positive displacement pump according to claim 1, characterized in that it comprises a first communication valve (17) between the first inlet chamber (4) and the second delivery chamber (8), and a second communication valve (18 ) between the second intake chamber (7) and the first discharge chamber (6). Pompe volumétrique selon la revendication 1, caractérisée en ce qu'elle comporte un seul clapet de communication (19) entre la première chambre d'admission (4) et la seconde chambre de refoulement (8) d'une part, et entre la seconde chambre d'admission (7) et la première chambre de refoulement (6) d'autre part. Positive displacement pump according to claim 1, characterized in that it comprises a single communication valve (19) between the first inlet chamber (4) and the second delivery chamber (8) on the one hand, and between the second intake chamber (7) and the first discharge chamber (6) on the other hand. Procédé de commande d'une pompe volumétrique à double engrenage (1, 2 ; 2, 3) comportant deux chambres d'admission (4, 7) et deux chambres de refoulement (6, 8), en fonction de sa pression de refoulement, caractérisée en ce la pompe dispose d'un premier mode de fonctionnement dans lequel les chambres d'admission (4, 7) et les chambres de refoulement (6, 8) ne sont pas en communication, et d'un second mode de fonctionnement dans lequel au moins une partie de la pression refoulée par un second engrenage (2, 3) est renvoyée dans la chambre d'admission (4) du premier engrenage (1).Method of controlling a positive displacement double gear pump (1, 2; 2, 3) comprising two intake chambers (4, 7) and two delivery chambers (6, 8), depending on its pressure delivery, characterized in that the pump has a first mode of operation in which the intake chambers (4, 7) and the delivery chambers (6, 8) are not in communication, and of a second mode of operation in which at least part of the pressure discharged by a second gear (2, 3) is returned to the inlet chamber (4) of the first gear (1). Procédé de commande selon la revendication 4, caractérisé en ce que la pompe dispose d'un troisième mode de fonctionnement, dans lequel toute la pression refoulée par le second engrenage (2, 3) est refoulée dans la chambre d'admission (4) du premier engrenage (1, 2).Control method according to claim 4, characterized in that the pump has a third operating mode, in which all the pressure discharged by the second gear (2, 3) is discharged into the inlet chamber (4) of the first gear (1, 2). Procédé de commande selon la revendication 5, caractérisé en ce que la pompe dispose d'un quatrième mode de fonctionnement, dans lequel toute la pression refoulée par le second engrenage (2, 3) est refoulée dans la chambre d'admission (4) du premier engrenage (1, 2), et une partie de la pression refoulée par ce dernier est renvoyée dans la chambre d'admission (7) du second engrenage (2, 3)Control method according to claim 5, characterized in that the pump has a fourth operating mode, in which all the pressure discharged by the second gear (2, 3) is discharged into the intake chamber (4) of the first gear (1, 2), and part of the pressure discharged by the latter is returned to the intake chamber (7) of the second gear (2, 3) Procédé de commande selon la revendication 4, 5 ou 6, caractérisé en ce le premier mode de fonctionnement est conservé en dessous d'un premier seuil de pression de refoulement S1, et en en ce que le second mode de fonctionnement est adopté entre le premier seuil S1 et un second seuil de pression S2 supérieur à S1.Control method according to claim 4, 5 or 6, characterized in this the first operating mode is kept below a first discharge pressure threshold S1, and in that the second operating mode is adopted between the first threshold S1 and a second pressure threshold S2 higher than S1. Procédé de commande selon la revendication 5, 6 ou 7, caractérisé en ce que le troisième mode de fonctionnement est adopté entre le second seuil S2 de pression, et un troisième seuil et un troisième seuil S3 supérieur à S2.Control method according to claim 5, 6 or 7, characterized in that the third operating mode is adopted between the second pressure threshold S2, and a third threshold and a third threshold S3 greater than S2. Procédé de commande selon la revendication 8, caractérisé en ce que le quatrième mode de fonctionnement est adopté au delà du troisième seuil de pression S3.Control method according to claim 8, characterized in that the fourth operating mode is adopted beyond the third pressure threshold S3.
EP20020291491 2001-06-15 2002-06-14 Gear pump with three shafts Expired - Fee Related EP1267077B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0107834A FR2826069B1 (en) 2001-06-15 2001-06-15 DOUBLE GEAR VOLUMETRIC PUMP
FR0107834 2001-06-15

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EP1267077A1 true EP1267077A1 (en) 2002-12-18
EP1267077B1 EP1267077B1 (en) 2008-02-27

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EP20020291491 Expired - Fee Related EP1267077B1 (en) 2001-06-15 2002-06-14 Gear pump with three shafts

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EP (1) EP1267077B1 (en)
DE (1) DE60225207T2 (en)
FR (1) FR2826069B1 (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2397345A (en) * 2003-01-17 2004-07-21 Dana Automotive Ltd A Triple Gear Pump
CN100419267C (en) * 2004-09-22 2008-09-17 株式会社Tbk No-load operation system of tadem pump
CN102926997A (en) * 2012-10-28 2013-02-13 张意立 Flange internal thread conical spring gear pump
EP2634430A1 (en) 2012-02-28 2013-09-04 Maag Pump Systems AG Gear pump assembly
CN107366619A (en) * 2016-05-13 2017-11-21 王冬 The anti-decompression gear oil pump of fragmentation bubble

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2536736C1 (en) * 2013-11-07 2014-12-27 Закрытое Акционерное Общество "Новомет-Пермь" Gear wheel pump for fluid pumping

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Publication number Priority date Publication date Assignee Title
BE549734A (en) *
DE674380C (en) * 1937-02-18 1939-04-13 Ehrich & Graetz Akt Ges Control device for fuel pumps
US2665637A (en) * 1947-05-07 1954-01-12 Borg Warner Pumping system
US4502845A (en) * 1983-03-24 1985-03-05 General Motors Corporation Multistage gear pump and control valve arrangement

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE549734A (en) *
DE674380C (en) * 1937-02-18 1939-04-13 Ehrich & Graetz Akt Ges Control device for fuel pumps
US2665637A (en) * 1947-05-07 1954-01-12 Borg Warner Pumping system
US4502845A (en) * 1983-03-24 1985-03-05 General Motors Corporation Multistage gear pump and control valve arrangement

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2397345A (en) * 2003-01-17 2004-07-21 Dana Automotive Ltd A Triple Gear Pump
CN100419267C (en) * 2004-09-22 2008-09-17 株式会社Tbk No-load operation system of tadem pump
EP2634430A1 (en) 2012-02-28 2013-09-04 Maag Pump Systems AG Gear pump assembly
CN102926997A (en) * 2012-10-28 2013-02-13 张意立 Flange internal thread conical spring gear pump
CN102926997B (en) * 2012-10-28 2016-03-16 张意立 A kind of flange internal thread volute spring gear pump
CN107366619A (en) * 2016-05-13 2017-11-21 王冬 The anti-decompression gear oil pump of fragmentation bubble

Also Published As

Publication number Publication date
EP1267077B1 (en) 2008-02-27
FR2826069B1 (en) 2004-03-12
DE60225207T2 (en) 2009-03-26
FR2826069A1 (en) 2002-12-20
DE60225207D1 (en) 2008-04-10

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