EP0091347A1 - Multiple-gear pump - Google Patents

Multiple-gear pump Download PDF

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Publication number
EP0091347A1
EP0091347A1 EP83400618A EP83400618A EP0091347A1 EP 0091347 A1 EP0091347 A1 EP 0091347A1 EP 83400618 A EP83400618 A EP 83400618A EP 83400618 A EP83400618 A EP 83400618A EP 0091347 A1 EP0091347 A1 EP 0091347A1
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EP
European Patent Office
Prior art keywords
pump
orifice
casing
working fluid
return
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP83400618A
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German (de)
French (fr)
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EP0091347B1 (en
Inventor
Jean-Claude Muller
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DBA SA
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DBA SA
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Publication date
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Publication of EP0091347A1 publication Critical patent/EP0091347A1/en
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Publication of EP0091347B1 publication Critical patent/EP0091347B1/en
Expired legal-status Critical Current

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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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • 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 multiple gear pumps comprising a first pump part supplying equipment with a large flow of working fluid, and at least a second pump part supplying at least one other equipment with a low flow of working fluid , in particular, although not exclusively, for agricultural vehicles.
  • a multiple gear pump 100 comprising a first pump or front pump 1 supplying equipment 3, such as lifting installations, with a large working fluid flow, and at least a second pump or rear pump 2 supplying a servomechanism, such as a power steering 4, with a small flow of working fluid.
  • the first and second pumps 1 and 2 of the driven pinion type meshing with a idler pinion, are rotated by a shaft 5 capable of being coupled to a drive motor M.
  • the first and second pumps 1 and 2 deliver working fluid under pressure through two separate outlet ports 6 and 7, respectively.
  • the multiple pump comprises an orifice 8 for admitting the working fluid from a tank or a reservoir 90, the casing of the pump being provided with first and second passages 9 and 10, respectively, of the working fluid in from the tank 90 to the first and second pumps 1 and 2. Due mainly to the locations of the various equipment in the machine or the vehicle using the double gear pump, the high-speed return 11 takes place directly at the tank 90 , while the return at a lower flow rate from the particular equipment, such as the power steering 4, takes place directly in the pump via a return orifice 12 and a fluid return passage 13 downstream of the orifice admission 8.
  • the return passage 13 communicates with the second supply passage 10 of the second pump 2, immediately upstream of the latter.
  • This arrangement has the drawback that the second pump or rear pump 2 operates in fact in a closed circuit, from which it follows a rapid heating of the working fluid passing through this second pump and the associated equipment, with the related problems.
  • the object of the present invention is precisely to present a multiple gear pump of the general type described above making it possible to avoid the operation of the second pump in a closed circuit, thereby limiting the overheating. working fluid flowing through the latter, at the cost of a simple arrangement of low manufacturing cost.
  • the gear pump of the type comprising a casing, a first and at least a second gear pump, arranged in the casing and each comprising a driven pinion and a idler pinion, means for connecting the driven pinions to a drive member, a working fluid intake port in the casing, first and second working fluid supply passages between the intake port and the first and second pumps, respectively, first and second working fluid outlet ports connected to the first and second pumps, respectively, at least one working fluid return port in the housing, and at least one fluid return passage work establishing communication between the return port and the intake port, is characterized in that the return path opens into the first working fluid supply passage to the first pump.
  • Another object of the present invention is to provide a gear pump of the type defined above allowing, without obstructing the manufacturing costs, to simply carry out the return path by using the latter in addition to recirculate any leaks of working fluid. at the bearings of the driven and idler gears of the first and second pumps.
  • the idler gears of the first and second pumps have hollow axes, the return passage of working fluid passing through these hollow axes.
  • the pump also comprises recirculation passages connecting the ends of the bearings of the pinions driven to the return passage.
  • a double gear pump 100 has the same general layout as the pump of Figure 1 except, however, that, in accordance with the present invention, the return passage 13 this time no longer communicates with the second passage 10 for supplying the working fluid to the second pump 2, but is extended, within the body of the pump, by an axial passage 13 ′ which opens into the first passage 9 supplying the working fluid to the first pump 1.
  • the return from the equipment 4 is carried out this time immediately upstream of the first pump 1 in the working fluid circulation path 9 and 6 at high speed from this first pump, the second pump 2 receiving the working fluid at low pressure directly from the supply pipe coming from the tank 90, which thus eliminates the problems of heating of the working fluid in the loop of the second pump.
  • the extension part 13 ′ of the return passage 13 can be provided, like the second supply passage, 10 in the body of the pump housing.
  • the gear pump comprises idler pinions with hollow axes, the return passage 13 'passing through these hollow axes, as will be understood from the following description given with reference with Figures 3 to 6.
  • first and second pumps 1 and 2 respectively comprising a driven pinion 101 and 102 and a idler pinion 111 and 112.
  • the driven pinions 101 and 102 are coaxial and driven by a shaft 50 in two parts coupled by a sleeve, intermediate 51.
  • the two idler gears 111 and 112 are coaxial.
  • Each pump 1 and 2 is arranged in a housing part provided with bearing elements for the pinions, the two housing parts being joined with the interposition of an intermediate part and kept assembled between two end flanges 14 and 15, l drive shaft 50 projecting externally from the flange: 14 for its connection to the drive motor M.
  • the inlet 8 and the first outlet 6 of the first pump 1 are arranged opposite in the opposite side walls of the housing part of the first pump , axially the second inlet passage 10 extending / through the casing part intermediate between the casing parts of the first and second. pumps up to the latter, the second outlet orifice 7 of the second pump 2 being formed in the end flange 15 adjacent to the latter.
  • the axes of the idler gears 111 and 112 are each formed with a through bore 113 and 114, respectively, establishing a continuous passage, via an internal chamber 115 in the part of the intermediate housing separating the two pumps between an idler end chamber 116 formed in the inner face of the end flange 15 and an idler gear end chamber 117 similarly formed in the inner face of the opposite end flange 14.
  • chambers 118 and 119 at the end of the axes of the driven pinions collecting the leaks at the bearings of the driven pinions.
  • the chamber 118 communicates with the chamber 116 by an internal passage 120 formed in the flange 15.
  • the chamber 119 communicates with the chamber 117 by an internal passage 121 formed in the end flange 14.
  • the passages 120 and 121 thus allow recovery of internal leaks in the return passage 13 '.
  • a passage 122 formed in the end flange 15, communicates the return orifice 12, also formed in this flange 15, with the chamber 116 of the shaft end idler gear of the second pump to constitute the first part 13 of the path of return of working fluid in the pump.
  • a passage 123 formed in the end flange 14, connects the chamber 117 of the idler pin end end with a housing 124 communicating with the first supply passage 9 of the working fluid to the first pump l, immediately downstream of the intake orifice 8, thus completing the return path 13, 13 'in the pump body from the return orifice 12, the passage 122, the bores 114 and 113 of the pinions. two pumps, and the passage 123 in the flange 14.
  • this arrangement ensures the uniformity of temperature of the working fluid circuit as well as the return to suction of internal leaks from the pump.
  • the pump assembly can comprise more than two adjacent pumps with mutually aligned pinions, the internal leaks from the bearings of the driven pinions being recovered in chambers such as 115 formed in the intermediate casing parts between two adjacent pumps via formed conduits. in these intermediate parts.
  • the passages formed in the end flanges consist of holes using closure plugs, they can be produced by lost wax molding.

Abstract

1. A multiple gear pump comprising in a casing a first pump (1) arranged to supply a large work fluid mass flow rate to at least a first equipment (3) and at least a second pump (2) arranged to supply a smaller work fluid mass flow rate to at least a second independent equipment (4), each pump comprising a driven pinion and an idle pinion, means for connecting the driven pinions to a drive element (M), an orifice (8) for feeding work fluid into the casing, a first (9) and a second (10) passage for feeding work fluid between the inlet orifice and the first and second pumps, respectively, formed in the casing, a first (6) and a second (7) outlet orifice for discharging work fluid separately connected to said first and second pumps, respectively, and arranged to be connected to said first (3) and second (4) independent equipments, respectively, a refeeding orifice (12) for refeeding work fluid from the second equipment (4) formed in the casing, and a refeeding line (13) providing communication between the refeeding orifice (12) and the inlet orifice (8), characterized in that the refeeding line (13, 13') opens into the first feeding passage (9) of the first pump (1) and in that the idle pinions (111, 112) each have a hollow axis (113, 114), with the refeeding line (13') passing through said hollow axes.

Description

La présente invention concerne les pompes multiples à engrenages comprenant une première partie de pompe alimentant des équipements avec un gros débit de fluide de travail, et au moins une seconde partie de pompe alimentant au moins un autre équipement avec un plus faible débit de fluide de travail, notamment, quoique non exclusivement, pour des véhicules agricoles.The present invention relates to multiple gear pumps comprising a first pump part supplying equipment with a large flow of working fluid, and at least a second pump part supplying at least one other equipment with a low flow of working fluid , in particular, although not exclusively, for agricultural vehicles.

Pour certains usages, notamment dans les véhicules agricoles, il est prévu, comme représenté sur la Figure 1, une pompe multiple à engrenages 100 comprenant une première pompe ou pompe avant 1 alimentant des équipements 3, tels que des installations de relevage, avec un gros débit de fluide de travail, et au moins une seconde pompe ou pompe arrière 2 alimentant un servomécanisme, tel qu'une servodirection 4, avec un petit débit de fluide de travail. De façon connue en soi, les première et seconde pompes 1 et 2, du type à pignon entraîné engrenant avec un pignon fou, sont entraînées en rotation par un arbre 5 susceptible d'être couplé à un moteur d'entraînement M. Les première et seconde pompes 1 et 2 débitent du fluide de travail sous pression par deux orifices de sortie distincts 6 et 7, respectivement. La pompe multiple comprend un orifice 8 d'admission du fluide de travail en provenance d'une bâche ou d'un réservoir 90, le carter de la pompe étant pourvu de premiers et seconds passages 9 et 10, respectivement, du fluide de travail en provenance de la bâche 90 vers les première et seconde pompes 1 et 2. En raison essentiellement des localisations des différents équipements dans la machine ou le véhicule utilisant la pompe double à engrenages, le retour à fort débit 11 s'effectue directement à la bâche 90, tandis que le retour à plus faible débit en provenance dé l'équipement particulier, tel que la servodirection 4, s'effectue directement dans la pompe via un orifice de retour 12 et un passage de retour de fluide 13 en aval de l'orifice d'admission 8.For certain uses, in particular in agricultural vehicles, there is provided, as shown in FIG. 1, a multiple gear pump 100 comprising a first pump or front pump 1 supplying equipment 3, such as lifting installations, with a large working fluid flow, and at least a second pump or rear pump 2 supplying a servomechanism, such as a power steering 4, with a small flow of working fluid. In a manner known per se, the first and second pumps 1 and 2, of the driven pinion type meshing with a idler pinion, are rotated by a shaft 5 capable of being coupled to a drive motor M. The first and second pumps 1 and 2 deliver working fluid under pressure through two separate outlet ports 6 and 7, respectively. The multiple pump comprises an orifice 8 for admitting the working fluid from a tank or a reservoir 90, the casing of the pump being provided with first and second passages 9 and 10, respectively, of the working fluid in from the tank 90 to the first and second pumps 1 and 2. Due mainly to the locations of the various equipment in the machine or the vehicle using the double gear pump, the high-speed return 11 takes place directly at the tank 90 , while the return at a lower flow rate from the particular equipment, such as the power steering 4, takes place directly in the pump via a return orifice 12 and a fluid return passage 13 downstream of the orifice admission 8.

Dans le mode de réalisation de l'art antérieur représenté à la Figure 1, le passage de retour 13 communique avec le second passage d'amenée 10 de la seconde pompe 2, immédiatement en amont de cette dernière. Cet agencement présente l'inconvénient que la seconde pompe ou pompe arrière 2 fonctionne de fait en circuit fermé, d'où il s'ensuit un échauffement rapide du fluide de travail traversant cette seconde pompe et l'équipement associé, avec les problèmes afférents.In the embodiment of the prior art shown in Figure 1, the return passage 13 communicates with the second supply passage 10 of the second pump 2, immediately upstream of the latter. This arrangement has the drawback that the second pump or rear pump 2 operates in fact in a closed circuit, from which it follows a rapid heating of the working fluid passing through this second pump and the associated equipment, with the related problems.

La présente invention a précisément pour objet de présenter une pompe multiple à engrenages de type général décrit ci-dessus permettant d'éviter le fonctionnement de la seconde pompe en circuit fermé, en limitant ainsi l'échauffement du fluide de travail circulant au travers de cette dernière,au prix d'un agencement simple de faible coût de fabrication.The object of the present invention is precisely to present a multiple gear pump of the general type described above making it possible to avoid the operation of the second pump in a closed circuit, thereby limiting the overheating. working fluid flowing through the latter, at the cost of a simple arrangement of low manufacturing cost.

Pour ce faire, selon une caractéristique de la présente invention, la pompe à engrenages, du type comprenant un carter, une première et au moins une seconde pompes à engrenages, disposées dans le carter et comportant chacune un pignon entraîné et un pignon fou, des moyens pour relier les pignons entraînés à un organe d'entraînement, un orifice d'admission de fluide de travail dans le carter, un premier et un second passages d'amenée de fluide de travail entre l'orifice d'admission et les première et seconde pompes, respectivement, un premier et un second orifices de sortie de fluide de travail reliés aux première et seconde pompes, respectivement, au moins un orifice de retour de fluide de travail dans le carter, et au moins un passage de retour de fluide de travail établissant une communication entre l'orifice de retour et l'orifice d'admission, est caractérisée en ce que le trajet de retour débouche dans le premier passage d'amenée de fluide de travail vers la première pompe.To do this, according to a characteristic of the present invention, the gear pump, of the type comprising a casing, a first and at least a second gear pump, arranged in the casing and each comprising a driven pinion and a idler pinion, means for connecting the driven pinions to a drive member, a working fluid intake port in the casing, first and second working fluid supply passages between the intake port and the first and second pumps, respectively, first and second working fluid outlet ports connected to the first and second pumps, respectively, at least one working fluid return port in the housing, and at least one fluid return passage work establishing communication between the return port and the intake port, is characterized in that the return path opens into the first working fluid supply passage to the first pump.

La présente invention a pour autre objet de proposer une pompe à engrenages du type défini ci-dessus permettant, sans obérer les coûts de fabrication, de réaliser simplement le trajet de retour en utilisant en outre ce dernier pour recirculer les fuites éventuelles de fluide de travail au niveau des paliers des pignons entraînés et fous des première et seconde pompes.Another object of the present invention is to provide a gear pump of the type defined above allowing, without obstructing the manufacturing costs, to simply carry out the return path by using the latter in addition to recirculate any leaks of working fluid. at the bearings of the driven and idler gears of the first and second pumps.

Pour ce faire, selon une autre caractéristique de l'invention, les pignons fous des première et seconde pompes ont des axes creux, le passage de retour de fluide de travail passant pàr ces axes creux.To do this, according to another characteristic of the invention, the idler gears of the first and second pumps have hollow axes, the return passage of working fluid passing through these hollow axes.

Selon encore une autre caractéristique de l'invention la pompe comprend en outre des passages de recirculation reliant les extrémités des paliers des pignons entraînés au passage de retour.According to yet another characteristic of the invention, the pump also comprises recirculation passages connecting the ends of the bearings of the pinions driven to the return passage.

D'autres caractéristiques et avantages de la présente invention ressortiront de la description suivante d'un mode de réalisation, donné à titre illustratif mais nullement limitatif, faite en relation avec les dessins annexés, sur lesquels:

  • La Figure 1 représente, schématiquement un agencement de pompe double à engrenages de l'art antérieur;
  • La Figure 2 représente-schématiquement une pompe double à engrenages;
  • La Figure 3 est une vue en coupe longitudinale dans un plan passant par les axes des pignons entraînés et fous d'une pompe selon l'invention;
  • La Figure 4 est une vue en coupe longitudinale dans un plan médian perpendiculaire au plan de la Figure 3; et
  • Les Figures 5 et 6 sont des vues de face, respectivement interne et externe, des flasques d'extrémité de la pompe des Figures 3 et 4.
Other characteristics and advantages of the present invention will emerge from the following description of an embodiment, given by way of illustration but in no way limiting, made in relation to the appended drawings, in which:
  • Figure 1 shows schematically a double gear pump arrangement of the prior art;
  • Figure 2 shows schematically a double gear pump;
  • Figure 3 is a longitudinal sectional view in a plane passing through the axes of the driven and idler pinions of a pump according to the invention;
  • Figure 4 is a longitudinal sectional view in a median plane perpendicular to the plane of Figure 3; and
  • Figures 5 and 6 are front views, respectively internal and external, of the end flanges of the pump of Figures 3 and 4.

Dans la description qui va suivre, et sur les dessins, les éléments identiques ou analogues portent les mêmes chiffres de référence.In the description which follows, and in the drawings, identical or analogous elements bear the same reference numbers.

Comme représenté sur la Figure 2, une pompe double à engrenages 100 selon la présente invention présente la même implantation générale que la pompe de la Figure 1 si ce n'est, toutefois, que, conformément à la présente invention, le passage de retour 13 ne communique plus, cette fois, avec le second passage 10 d'amenée du fluide de travail à la seconde pompe 2, mais est prolongé, au sein du corps de la pompe, par un passage axial 13' venant déboucher dans le premier passage 9 d'amenée du fluide de travail à la première pompe 1.As shown in Figure 2, a double gear pump 100 according to the present invention has the same general layout as the pump of Figure 1 except, however, that, in accordance with the present invention, the return passage 13 this time no longer communicates with the second passage 10 for supplying the working fluid to the second pump 2, but is extended, within the body of the pump, by an axial passage 13 ′ which opens into the first passage 9 supplying the working fluid to the first pump 1.

Conformément à l'objet de l'invention, le retour en provenance de l'équipement 4 s'effectue cette fois immédiatement en amont de la première pompe 1 dans le trajet de circulation de fluide de travail 9 et 6 à haut débit de cette première pompe, la seconde pompe 2 recevant le fluide de travail à basse pression directement de la canalisation d'amenée en provenance de la bâche 90, ce qui supprime ainsi les problèmes d'échauffement du fluide de travail dans la boucle de la seconde pompe.In accordance with the object of the invention, the return from the equipment 4 is carried out this time immediately upstream of the first pump 1 in the working fluid circulation path 9 and 6 at high speed from this first pump, the second pump 2 receiving the working fluid at low pressure directly from the supply pipe coming from the tank 90, which thus eliminates the problems of heating of the working fluid in the loop of the second pump.

La partie de prolongation 13' du passage de retour 13 peut être ménagée, cbmme le second passage d'amenée, 10 dans le corps du carter de la pompe. Toutefois, selon un mode de réalisation préféré de l'invention, la pompe à engrenages comprend des pignons fous à axes creux, le passage de retour 13' passant par ces axes creux, ainsi qu'on le comprendra de la description suivante faite en référence avec les Figures 3 à 6.The extension part 13 ′ of the return passage 13 can be provided, like the second supply passage, 10 in the body of the pump housing. However, according to a preferred embodiment of the invention, the gear pump comprises idler pinions with hollow axes, the return passage 13 'passing through these hollow axes, as will be understood from the following description given with reference with Figures 3 to 6.

Sur la Figure 3,on reconnaît les première et seconde pompes 1 et 2 comprenant respectivement un pignon entraîné 101 et 102 et un pignon fou 111 et 112. Les pignons entraînés 101 et 102 sont coaxiaux et entraînés par un arbre 50 en deux parties accouplées par un manchon, intermédiaire 51. De façon similaire, les deux pignons fous 111 et 112 sont coaxiaux. Chaque pompe 1 et 2 est disposée dans une partie de carter pourvue d'éléments de palier pour les pignons, les deux parties de carter étant accolées avec interposition d' une partie intermédiaire et maintenues assemblées entre deux flasques d'extrémité 14 et 15, l'arbre d'entraînement 50 faisant saillie extérieurement par rapport au flasque: 14 pour sa connection au moteur d'entraînement M.In Figure 3, we recognize the first and second pumps 1 and 2 respectively comprising a driven pinion 101 and 102 and a idler pinion 111 and 112. The driven pinions 101 and 102 are coaxial and driven by a shaft 50 in two parts coupled by a sleeve, intermediate 51. Similarly, the two idler gears 111 and 112 are coaxial. Each pump 1 and 2 is arranged in a housing part provided with bearing elements for the pinions, the two housing parts being joined with the interposition of an intermediate part and kept assembled between two end flanges 14 and 15, l drive shaft 50 projecting externally from the flange: 14 for its connection to the drive motor M.

Comme on le voit sur la Figure 4, l'orifice d'admission 8 et le premier orifice de sortie 6 de la première pompe 1 sont ménagés en vis-à-vis dans les parois latérales opposées de la partie de carter de la première pompe, axialement le second passage d'amenée 10 s'étendant/au travers de la partie de carter intermédiaire entre les parties de carter des première et seconde. pompes jusqu'à cette dernière, le second orifice de sortie 7 de la seconde pompe 2 étant formé dans le flasque d'extrémité 15 adjacent àcette dernière.As seen in Figure 4, the inlet 8 and the first outlet 6 of the first pump 1 are arranged opposite in the opposite side walls of the housing part of the first pump , axially the second inlet passage 10 extending / through the casing part intermediate between the casing parts of the first and second. pumps up to the latter, the second outlet orifice 7 of the second pump 2 being formed in the end flange 15 adjacent to the latter.

Comme on le voit sur la Figure 3, les axes des pignons fous 111 et 112 sont chacun formés avec un alésage traversant 113 et 114, respectivement, établissant un passage continu, via une chambre interne 115 dans la partie de carter intermédiaire séparant les deux pompes, entre une chambre d'extrémité de pignon fou 116 forméedans la face interne du flasque d'extrémité 15 et une chambre d'extrémité de pignon fou 117 forméesimilairement dans la face interne du flasque d'extrémité opposé 14. De plus, dans les flasques 14 et 15 sont formées des chambres 118 et 119 d'extrémité des axes des pignons entraînés collectant les fuites au niveau des paliers des pignons entraînés. La chambre 118 communique avec la chambre 116 par un passage interne 120 formé dans le flasque 15. De façon similaire, la chambre 119 communique avec la chambre 117 par un passage interne 121 formé dans le flasque d'extrémité 14. Les passages 120 et 121 permettent ainsi une récupération des fuites internes dans le passage de retour 13'.As seen in Figure 3, the axes of the idler gears 111 and 112 are each formed with a through bore 113 and 114, respectively, establishing a continuous passage, via an internal chamber 115 in the part of the intermediate housing separating the two pumps between an idler end chamber 116 formed in the inner face of the end flange 15 and an idler gear end chamber 117 similarly formed in the inner face of the opposite end flange 14. In addition, in the flanges 14 and 15 are formed chambers 118 and 119 at the end of the axes of the driven pinions collecting the leaks at the bearings of the driven pinions. The chamber 118 communicates with the chamber 116 by an internal passage 120 formed in the flange 15. Similarly, the chamber 119 communicates with the chamber 117 by an internal passage 121 formed in the end flange 14. The passages 120 and 121 thus allow recovery of internal leaks in the return passage 13 '.

Comme on le voit mieux sur la Figure 4, un passage 122, formé dans le flasque d'extrémité 15, met en communication l'orifice de retour 12, également formé dans ce flasque 15,avec la chambre 116 d'extrémité d'arbre de pignon fou de la seconde pompe pour constituer la première partie 13 du trajet de retour de fluide de travail dans la pompe. Parallèlement, un passage 123, formé dans le flasque d'extrémité 14, met en communication la chambre 117 d'extrémité d'axe de pignon fou avec un logement 124 communiquant avec le premier passage d'amenée 9 du fluide de travail vers la première pompe l,immédiatement en aval de l'orifice d'admission 8, complétant ainsi le trajet de retour 13, 13' dans le corps de pompe depuis l'orifice de retour 12, le passage 122, les alésages 114 et 113 des pignons .fous des deux pompes, et le passage 123 dans le flasque 14.As best seen in Figure 4, a passage 122, formed in the end flange 15, communicates the return orifice 12, also formed in this flange 15, with the chamber 116 of the shaft end idler gear of the second pump to constitute the first part 13 of the path of return of working fluid in the pump. In parallel, a passage 123, formed in the end flange 14, connects the chamber 117 of the idler pin end end with a housing 124 communicating with the first supply passage 9 of the working fluid to the first pump l, immediately downstream of the intake orifice 8, thus completing the return path 13, 13 'in the pump body from the return orifice 12, the passage 122, the bores 114 and 113 of the pinions. two pumps, and the passage 123 in the flange 14.

Conformément, à l'objet de l'invention, cet agencement assure l'uniformité de température du circuit de fluide de travail ainsi que le retour à l'aspiration des fuites internes de la pompe.In accordance with the object of the invention, this arrangement ensures the uniformity of temperature of the working fluid circuit as well as the return to suction of internal leaks from the pump.

Quoique la présente invention ait été décrite en relation avec un mode de réalisation particulier, elle ne s'en trouve pas limitée mais est au contraire susceptible de modifications et de variantes qui apparaîtront à l' homme de l'art. Ainsi, l'ensemble de pompe peut comporter plus de deux pompes adjacentes à pignons mutuellement alignés, les fuites internes des paliers des pignons entrainés étant récupérées dans des chambres telles que 115 formées dans les parties intermédiaires de carter entre deux pompes adjacentes via des conduits formés dans ces parties intermédiaires. De même, alors que, sur les dessins, les passages formés dans les flasques d'extrémités sont constitués par des perçages utilisant des bouchons de fermeture, ils peuvent être réalisés par moulage à la cire perdue.Although the present invention has been described in relation to a particular embodiment, it is not limited thereto but is on the contrary subject to modifications and variants which will appear to those skilled in the art. Thus, the pump assembly can comprise more than two adjacent pumps with mutually aligned pinions, the internal leaks from the bearings of the driven pinions being recovered in chambers such as 115 formed in the intermediate casing parts between two adjacent pumps via formed conduits. in these intermediate parts. Likewise, while, in the drawings, the passages formed in the end flanges consist of holes using closure plugs, they can be produced by lost wax molding.

Claims (6)

1. Pompe à engrenages comprenant : - un carter - une première (1) et au moins une seconde (2) pompes à engrenages dans le carter, chaque pompe comportant un pignon entraîné et un pignon fou, - des moyens pour relier les pignons entraînés à un organe d'entraînement (M), - un orifice (8) d'admission de fluide de travail dans le carter, - un premier (9) et un second (10) passages d'amenée de fluide de travail entre l'orifice d'admission et les première et seconde pompes, respectivement, formés dans le carter, - un premier (6) et un second (7) orifices de sortie de fluide de travail séparés reliés aux première et seconde pompes, respectivement, .et destinés à être reliés respectivement à des premier (3) et second (4) équipements indépendants, et - un orifice (12) de retour du fluide de travail en provenance du second équipement (4), formé dans le carter et établissant une communication (13) entre l'orifice de retour (12) et l'orifice d'admission (8),
caractérisée en ce que le trajet de retour (13,13') débouche dans le premier passage (9) d'amenée du fluide de travail à la première pompe (1) et en ce que les pignons fous (111, 112) ont chacun un axe creux (113, 114), le trajet de retour (13') passant par ces axes creux.1. Gear pump comprising: - a housing - a first (1) and at least a second (2) gear pump in the housing, each pump comprising a driven pinion and a idler pinion, - means for connecting the driven pinions to a drive member (M), an orifice (8) for admitting working fluid into the casing, - a first (9) and a second (10) working fluid supply passages between the inlet orifice and the first and second pumps, respectively, formed in the casing, - a first (6) and a second (7) separate working fluid outlet orifices connected to the first and second pumps, respectively, and intended to be connected respectively to first (3) and second (4) independent equipment, and - an orifice (12) for the return of the working fluid from the second equipment (4), formed in the casing and establishing a communication (13) between the return orifice (12) and the intake orifice (8 ),
characterized in that the return path (13,13 ') opens into the first passage (9) for supplying the working fluid to the first pump (1) and in that the idler gears (111, 112) each have a hollow axis (113, 114), the return path (13 ') passing through these hollow axes. 2. Pompe selon la revendication 1, caractérisée en ce qu'elle comporte en outre des passages, de recirculation (120, 121) reliant les extrémités (118, 119 des axes entraînés (101, 102) au passage de retour (13').2. Pump according to claim 1, characterized in that it further comprises passages, recirculation (120, 121) connecting the ends (118, 119 of the driven axes (101, 102) to the return passage (13 ') . 3. Pompe selon la revendication 2, dans laquelle le carter est constitu de parties de carter accolées entre deux flasques d'extrémité, caractérisée en ce que les passages de recirculation (120, 121) sont formés dans les flasques d'extrémité (14, 15).3. Pump according to claim 2, in which the casing is made up of casing parts joined between two end flanges, characterized in that the recirculation passages (120, 121) are formed in the end flanges (14, 15). 4. Pompe selon l'une des revendications 1 à 3, caractérisée en ce que les pignons (101, 102 ; 111, 112) des première (1) et seconde (2) pompes sont axialement alignés, respectivement.4. Pump according to one of claims 1 to 3, characterized in that the pinions (101, 102; 111, 112) of the first (1) and second (2) pumps are axially aligned, respectively. 5. Pompe selon la revendication 3 ou la revendication 4, caractérisée en ce que l'orifice de retour (12) est formé dans l'un des flasques d'extrémité (115. Pump according to claim 3 or claim 4, characterized in that the return orifice (12) is formed in one of the end flanges (11 6. Pompe selon la revendication 5, caractérisée en ce que le second orifice de sortie (7) est formé dans ledit flasque d'extrémité (15).6. Pump according to claim 5, characterized in that the second outlet orifice (7) is formed in said end flange (15).
EP19830400618 1982-03-30 1983-03-24 Multiple-gear pump Expired EP0091347B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8205409 1982-03-30
FR8205409A FR2524575B1 (en) 1982-03-30 1982-03-30 MULTIPLE GEAR PUMP

Publications (2)

Publication Number Publication Date
EP0091347A1 true EP0091347A1 (en) 1983-10-12
EP0091347B1 EP0091347B1 (en) 1985-06-19

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19830400618 Expired EP0091347B1 (en) 1982-03-30 1983-03-24 Multiple-gear pump

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EP (1) EP0091347B1 (en)
DE (1) DE3360299D1 (en)
FR (1) FR2524575B1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0787260A1 (en) * 1994-03-22 1997-08-06 Micropump Corporation Multiple-chamber gear pump
US5842848A (en) * 1997-01-03 1998-12-01 Knowles; Frederick W. Compact high-volume gear pump
EP2634430A1 (en) 2012-02-28 2013-09-04 Maag Pump Systems AG Gear pump assembly

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2830290B1 (en) * 2001-10-01 2004-01-02 Coutier Moulage Gen Ind DOUBLE GEAR PUMP, AND INSTALLATION USING SUCH A PUMP
JP5361074B2 (en) * 2009-11-20 2013-12-04 ジヤトコ株式会社 Helical gear pump

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB572967A (en) * 1942-04-15 1945-10-31 Pump Engineering Service Corp Improvements in gear-wheel pumps
FR916746A (en) * 1941-08-19 1946-12-13 Plessey Co Ltd Improvements to hydraulic pumps, multistage compressors and similar devices
GB665808A (en) * 1949-11-26 1952-01-30 Snecma Installation for the distribution of fluid under pressure
US2965036A (en) * 1957-07-08 1960-12-20 Louis S Wood Automatic dual pump single-multiple stage low-high pressure fluid supply means
US3292551A (en) * 1965-04-26 1966-12-20 Clark Equipment Co Gear pump or motor
FR1536833A (en) * 1967-09-15 1968-08-16 Hobourn Eaton Mfg Co Ltd Pump for supplying a system using a fluid

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR916746A (en) * 1941-08-19 1946-12-13 Plessey Co Ltd Improvements to hydraulic pumps, multistage compressors and similar devices
GB572967A (en) * 1942-04-15 1945-10-31 Pump Engineering Service Corp Improvements in gear-wheel pumps
GB665808A (en) * 1949-11-26 1952-01-30 Snecma Installation for the distribution of fluid under pressure
US2965036A (en) * 1957-07-08 1960-12-20 Louis S Wood Automatic dual pump single-multiple stage low-high pressure fluid supply means
US3292551A (en) * 1965-04-26 1966-12-20 Clark Equipment Co Gear pump or motor
FR1536833A (en) * 1967-09-15 1968-08-16 Hobourn Eaton Mfg Co Ltd Pump for supplying a system using a fluid

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0787260A1 (en) * 1994-03-22 1997-08-06 Micropump Corporation Multiple-chamber gear pump
EP0787260A4 (en) * 1994-03-22 1997-08-06
US5842848A (en) * 1997-01-03 1998-12-01 Knowles; Frederick W. Compact high-volume gear pump
EP2634430A1 (en) 2012-02-28 2013-09-04 Maag Pump Systems AG Gear pump assembly

Also Published As

Publication number Publication date
FR2524575A1 (en) 1983-10-07
EP0091347B1 (en) 1985-06-19
DE3360299D1 (en) 1985-07-25
FR2524575B1 (en) 1986-02-28

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