EP1267077B1 - Gear pump with three shafts - Google Patents
Gear pump with three shafts Download PDFInfo
- Publication number
- EP1267077B1 EP1267077B1 EP20020291491 EP02291491A EP1267077B1 EP 1267077 B1 EP1267077 B1 EP 1267077B1 EP 20020291491 EP20020291491 EP 20020291491 EP 02291491 A EP02291491 A EP 02291491A EP 1267077 B1 EP1267077 B1 EP 1267077B1
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- Prior art keywords
- chamber
- delivery
- pump
- inlet
- chambers
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Classifications
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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
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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
- 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 volumetric pumps, ie whose theoretical flow rate is proportional to the speed, used in particular for the lubrication of internal combustion engines of road vehicles.
- a dual-gear volumetric pump comprising three pumping gears defining two intake chambers and two delivery chambers, a central supply duct connected to two inlet ducts opening respectively into the first and in the second inlet chamber, and a central discharge pipe joining two discharge pipes respectively from the first and the second discharge chamber.
- this invention also applies to any volumetric pump having more than three gears defining between them more than two inlet chambers and two discharge chambers.
- This type of pump is commonly used in systems, such as internal combustion engines of motor vehicles, whose lubrication requires a high flow and pressure at low speeds.
- a first drive gear meshes with a second driven gear, driving itself a third driven gear.
- the three gables define two by two, two intake chambers and two discharge chambers.
- the two gears operate in parallel, in repressing two separate streams of oil.
- the advantage of this mode of operation is to double the flow rate of a conventional single gear pump, by adding only the volume of a pinion.
- the positive displacement pumps pose problems of use: on the one hand, the viscosity range of the oil is very wide, because of the variations of temperature of the engine, and on the other hand the speed range of the pump, directly related to the engine speed, is also very extensive.
- An oil pump must ensure good lubrication of the engine over its entire operating range and temperature. Moreover, it must be compact, silent, and consume the minimum of energy, low and high temperature.
- the efficiency of the positive displacement pumps being low in the low and medium speed ranges (approximately up to 2000 revolutions / minute), the pumps must be dimensioned according to this unfavorable operation, and therefore oversized at high speeds.
- the size of the oil pumps being directly related to their capacity, the pumps are therefore more and more bulky. Moreover, the larger the pumps, the more they are noisy because the amount of pulsed oil in the gears increases with the cubic capacity.
- the object of the invention is to obtain high flow rates in a dual gear volumetric pump, while keeping a small size.
- 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 discharge chamber.
- the pump comprises a single communication valve between the first chamber inlet and second discharge chamber on the one hand, and between the second inlet chamber and the first discharge chamber on the other.
- the invention also relates to a method for controlling a dual-gear volumetric pump comprising two intake chambers and two discharge chambers depending on its delivery pressure as defined in claim 3.
- the pump has a first mode of operation in which the intake chambers and the discharge chambers are not in communication, and a second mode of operation in which a portion of the flow discharged by a second gear is returned to the inlet chamber of the first gear.
- It may also have a third mode of operation in which all the flow delivered by the second gear is discharged to the inlet chamber of the first gear, and a fourth operating mode in which all the flow discharged by the second gear.
- the gear is pushed back to the inlet chamber of the first gear, and a portion of the flow delivered by the first gear is returned to the intake chamber of the second gear.
- the pump behaves like a conventional pump with two gears operating in parallel, that is to say with two inlet chambers 4, 7 and two delivery chambers 6, 8.
- the two valves 17, 18 are closed.
- the oil enters through the central supply duct 9, and is distributed between the two intake ducts 11, 12.
- the two pinions 1 and 2 propel the oil towards the first delivery chamber 6, and the two pinions 2 and 3 propel the oil to the second discharge chamber 8. It is then discharged through the conduits 14 and 16 to the central discharge pipe 13.
- the first valve 17 opens gradually. At least part of the flow from the second chamber discharge 8 being returned to the first inlet chamber 4, the pump is in a first phase of pressure regeneration (cf. figure 2 ), where the increase in pressure as a function of the speed is lower than between 0 and S1.
- the first valve 17 is fully open and closes 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 inlet chamber 4 (volumetric efficiency close), at a pressure identical to that of the second discharge chamber 8, the pressure losses close. Only one gear pump pumps, so the energy consumption is almost halved, while the pump exhaust pressure increases faster than the speed between S1 and S2.
- the second valve 18 opens, and at least a portion of the flow of the first discharge chamber 6 is returned to the second intake chamber 7, so that beyond S3, the slope of the curve is more between S2 and S3 (cf. figure 5 ). We are then in a second phase of regeneration of flow.
- the pump proposed by the invention is therefore a conventional double-gear pump with the particularity of having oil orientation means for short-circuiting one of the discharge pipes to the other inlet chamber at a pressure equal to that of repression.
- the valve 19 On the figure 6 , corresponding to the first mode of operation, the valve 19 is completely closed. On the figure 7 , corresponding to the second mode of operation, it partially releases the passage between the second discharge chamber and the first inlet chamber. On the figure 8 according to the third mode of operation, this passage is completely open, establishing in the chamber 4 the discharge pressure. Finally, on the figure 9 the valve releases the inlet of the second intake duct 12, and a portion of the flow rate of the first discharge chamber 6 is returned to the second intake chamber 7. With this arrangement, the single valve 19 thus ensures only the functions previously performed by the two valves 17, 18.
- valve (s) proposed (s) proposed by the invention allows (tent) to bypass one of the pump backs to the inlet at a pressure equal to that of the discharge. This measurement ensures a power saving consumed by the pump in the operating phases thereof where the pressure is high and where the motor does not need the full flow of the pump, 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)
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 volumetric pumps, ie whose theoretical flow rate is proportional to the speed, used in particular for the lubrication of internal combustion engines of road vehicles.
Elle concerne ainsi une pompe comme définit dans les préambules de la revendication 1. Une telle pompe est connue du document
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 preferred, but not exclusive, application to a dual-gear volumetric pump comprising three pumping gears defining two intake chambers and two delivery chambers, a central supply duct connected to two inlet ducts opening respectively into the first and in the second inlet chamber, and a central discharge pipe joining two discharge pipes respectively from the first and the second discharge 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 volumetric pump having more than three gears defining between them more than two inlet 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 internal combustion engines of motor vehicles, whose lubrication requires a high flow and pressure at low speeds.
Dans une telle pompe, un premier pignon menant engrène avec un second pignon mené, entraînant 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 drive gear meshes with a second driven gear, driving itself a third driven gear. The three gables define two by two, two intake chambers and two discharge chambers. Such a pump has several operating possibilities, including the two following 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, in repressing two separate streams of oil. The advantage of this mode of operation 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 mode of operation, one can have a single inlet chamber and a single oil discharge chamber to the outside, the other two chambers being placed in communication, so that the oil discharged by a first gear ensures the feeding 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 speaking, when the fluid to be pumped has a low viscosity, the internal leaks of the pump and the associated engine require high flows per pump revolution (ie a large displacement pump), so as to compensate for these losses. 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 particular case of the lubrication of internal combustion engines, the positive displacement pumps pose problems of use: on the one hand, the viscosity range of the oil is very wide, because of the variations of temperature of the engine, and on the other hand the speed range of the pump, directly related 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 good lubrication of the engine over its entire operating range and temperature. Moreover, it must be compact, silent, and consume the minimum of energy, low and high temperature.
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 require a large oil flow to be properly lubricated in all operating conditions. Generally, the flow elevations required by engine evolutions 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 are of real interest only at high oil temperatures (120 ° C - 150 ° C), because below these temperatures, the need for oil is reduced. By increasing the displacement, there is 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 the positive displacement pumps being low in the low and medium speed ranges (approximately up to 2000 revolutions / minute), the pumps must be dimensioned according to this unfavorable operation, 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 related to their capacity, the pumps are therefore more and more bulky. Moreover, the larger the pumps, the more they are noisy because the amount of pulsed oil in the gears increases with the cubic capacity.
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 dual gear volumetric pump, while keeping a small size.
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.For this purpose, it proposes to take advantage of various possible combinations between the intake and discharge chambers to reduce the displacement of the pump. These combinations are obtained thanks to the presence of means for directing the pressure fluid between the different chambers, more precisely between the inlet chambers 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 discharge chamber.
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 comprises a single communication valve between the first chamber inlet and second discharge chamber on the one hand, and between the second inlet chamber and the first discharge chamber on the other.
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 comme définit dans la revendication 3.The invention also relates to a method for controlling a dual-gear volumetric pump comprising two intake chambers and two discharge chambers depending on its delivery pressure as defined in
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 method, the pump has a first mode of operation in which the intake chambers and the discharge chambers are not in communication, and a second mode of operation in which a portion of the flow discharged by a second gear is returned to the inlet 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 may also have a third mode of operation in which all the flow delivered by the second gear is discharged to the inlet chamber of the first gear, and a fourth operating mode in which all the flow discharged by the second gear. The gear is pushed back to the inlet chamber of the first gear, and a portion of the flow delivered by the first gear is returned to the intake chamber of the second gear.
D'autres caractéristiques et avantages de l'invention apparaîtront 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 desfigures 1 à 4 comporte trois 1, 2, 3, dont un premier pignon menant 1 engrenant avec un second pignon mené 2 de façon à constituer unpignons premier engrenage 1, 2, et un second pignon mené engrenant avec le premier pignon mené, de façon à constituer un 2, 3. Lesecond engrenage premier engrenage 1, 2 présente une première chambre d'admission 4 et une première chambre derefoulement 6. Le second engrenage présente une seconde chambre d'admission 7 et une seconde chambre derefoulement 8. Les deux chambres d'admission 4, 7 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 14, 16, issus respectivement de la première et de la seconde chambre derefoulement 6, 8.refoulement
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 lesfigures 1 à 4 , ces moyens d'orientation sont constitués par deux 17, 18, pouvant respectivement mettre en communication la première chambre declapets refoulement 6 avec la seconde chambre d'admission 7, et la seconde chambre derefoulement 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.
- the
Figures 1 to 4 schematically show the operation of the pump proposed by the invention, - the
figure 5 illustrates how it works, and - the
Figures 6 to 9 illustrate a particular embodiment thereof.
The volumetric pump with double gearFigures 1 to 4 comprises three 1, 2, 3, including a first driving pinion 1 meshing with a second drivenpinions pinion 2 so as to constitute afirst gear 1, 2, and a second driven pinion meshing with the first driven pinion, so as to constitute a 2, 3. Thesecond gear first gear 1, 2 has a first intake chamber 4 and afirst delivery chamber 6. The second gear has asecond intake chamber 7 and asecond delivery chamber 8. Bothchambers 4, 7 are connected to acentral supply duct 9 by two 11, 12. Aintake ducts central discharge duct 13 joins two 14, 16, coming respectively from the first and the second ducts.delivery ducts 6, 8.discharge chamber
In accordance with the invention, the pump comprises means for orienting the pressure fluid, capable of bringing the intake chambers and the discharge chambers into communication.
On theFigures 1 to 4 these orientation means are constituted by two 17, 18, respectively able to put in communication thevalves first discharge chamber 6 with thesecond inlet chamber 7, and thesecond discharge chamber 8 with the first inlet chamber 4 .
According to the invention, the pump can have the following four modes of operation. - a first mode of operation in which the intake chambers and the delivery chambers are not in direct communication, and the two gears work in parallel,
- a second mode of operation in which a portion of the flow delivered by a second gear is returned to the inlet chamber of the first gear,
- a third mode of operation in which all the flow delivered by this second gear is discharged to the inlet chamber of the first gear, and
- a fourth mode of operation in which all the flow delivered by the second gear is discharged to the inlet chamber of the first gear, and a portion of the flow delivered by the first gear is returned to the intake chamber of the second gear.
En se reportant à la
Dans la première zone de fonctionnement, entre P = 0 et P = S1 (cf.
Entre S1 et S2 (cf.
Entre S2 et S3 (cf.
Lorsque P > S3 (cf.
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 conventional double-gear pump with the particularity of having oil orientation means for short-circuiting one of the discharge pipes to the other inlet chamber at a pressure equal to that of repression.
Sur, les
Sur ces schémas, on reconnaît 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, the three
Sur la
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 (s) proposed by the invention allows (tent) to bypass one of the pump backs to the inlet at a pressure equal to that of the discharge. This measurement ensures a power saving consumed by the pump in the operating phases thereof where the pressure is high and where the motor does not need the full flow of the pump, for example when the engine is cold.
Claims (8)
- Double gearing volumetric pump (1, 2; 2, 3) comprising three pumping gears (1, 2, 3) defining two inlet chambers (4, 7) and two delivery chambers (6, 8), a central feed pipe (9) connected to two inlet pipes (11, 12) respectively emerging in the first and in the second inlet chamber, and a central outlet pipe (13) uniting two delivery pipes (14, 16) respectively coming from the first and from the second delivery chamber and comprising means of orientation of the pressure fluid (17, 18; 19) able to connect the inlet chambers and the delivery chambers, in such a way as to return at least a portion of the flow coming from the second delivery chamber to the first inlet chamber, characterized in that it comprises a first connecting valve (17) between the first inlet chamber (4) and the second delivery chamber (8), and a second connecting valve (18) between the second inlet chamber (7) and the first delivery chamber (6).
- Volumetric pump according to the preamble of Claim 1, characterized in that it comprises a single connecting valve (19) between the first inlet chamber (4) and the second delivery chamber (8), on the one hand, and between the second inlet chamber (7) and the first delivery chamber (6), on the other hand.
- Method of controlling a volumetric pump according to Claim 1 or 2, characterized in that the pump has a first operating mode in which the inlet chambers (4, 7) and the delivery chambers (6, 8) are not connected, and a second operating mode in which at least a portion of the pressure delivered by the second gearing (2, 3) is sent into the inlet chamber (4) of the first gearing (1).
- Control method according to Claim 3, characterized in that the pump has a third operating mode, in which all of the pressure delivered by the second gearing (2, 3) is delivered into the inlet chamber (4) of the first gearing (1, 2).
- Control method according to Claim 4, characterized in that the pump has a fourth operating mode, in which all of the pressure delivered by the second gearing (2, 3) is delivered into the inlet chamber (4) of the first gearing (1, 2), and a portion of the pressure delivered by the latter is sent into the inlet chamber (7) of the second gearing (2, 3).
- Control method according to Claim 3, 4 or 5, characterized in that the first operating mode is maintained below a first delivery 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.
- Control method according to Claim 4, 5 or 6, characterized in that the third operating mode is adopted between the second pressure threshold S2 and a third threshold S3 higher than S2.
- Control method according to Claim 7, characterized in that the fourth operating mode is adopted beyond the third pressure threshold S3.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR0107834 | 2001-06-15 | ||
FR0107834A FR2826069B1 (en) | 2001-06-15 | 2001-06-15 | DOUBLE GEAR VOLUMETRIC PUMP |
Publications (2)
Publication Number | Publication Date |
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EP1267077A1 EP1267077A1 (en) | 2002-12-18 |
EP1267077B1 true EP1267077B1 (en) | 2008-02-27 |
Family
ID=8864341
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20020291491 Expired - Fee Related EP1267077B1 (en) | 2001-06-15 | 2002-06-14 | Gear pump with three shafts |
Country Status (3)
Country | Link |
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EP (1) | EP1267077B1 (en) |
DE (1) | DE60225207T2 (en) |
FR (1) | FR2826069B1 (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2397345A (en) * | 2003-01-17 | 2004-07-21 | Dana Automotive Ltd | A Triple Gear Pump |
JPWO2006033207A1 (en) * | 2004-09-22 | 2008-05-15 | 株式会社Tbk | Tandem pump no-load operation device |
EP2634430B1 (en) | 2012-02-28 | 2018-08-08 | Maag Pump Systems AG | Gear pump assembly |
CN102926997B (en) * | 2012-10-28 | 2016-03-16 | 张意立 | A kind of flange internal thread volute spring gear pump |
RU2536736C1 (en) * | 2013-11-07 | 2014-12-27 | Закрытое Акционерное Общество "Новомет-Пермь" | Gear wheel pump for fluid pumping |
CN107366619A (en) * | 2016-05-13 | 2017-11-21 | 王冬 | The anti-decompression gear oil pump of fragmentation bubble |
Family Cites Families (4)
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 |
-
2001
- 2001-06-15 FR FR0107834A patent/FR2826069B1/en not_active Expired - Lifetime
-
2002
- 2002-06-14 DE DE2002625207 patent/DE60225207T2/en not_active Expired - Lifetime
- 2002-06-14 EP EP20020291491 patent/EP1267077B1/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
FR2826069B1 (en) | 2004-03-12 |
FR2826069A1 (en) | 2002-12-20 |
DE60225207T2 (en) | 2009-03-26 |
DE60225207D1 (en) | 2008-04-10 |
EP1267077A1 (en) | 2002-12-18 |
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