EP1421281B1 - Gear pump - Google Patents
Gear pump Download PDFInfo
- Publication number
- EP1421281B1 EP1421281B1 EP02758458A EP02758458A EP1421281B1 EP 1421281 B1 EP1421281 B1 EP 1421281B1 EP 02758458 A EP02758458 A EP 02758458A EP 02758458 A EP02758458 A EP 02758458A EP 1421281 B1 EP1421281 B1 EP 1421281B1
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- EP
- European Patent Office
- Prior art keywords
- wheel
- peripheral
- wheels
- teeth
- pump
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/102—Adjustment of the interstices between moving and fixed parts of the machine by means other than fluid pressure
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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
- F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
- F04C13/001—Pumps for particular liquids
- F04C13/002—Pumps for particular liquids for homogeneous viscous liquids
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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
Definitions
- the present invention relates to positive displacement pumps especially for rubber compounds and, more particularly, gear pumps.
- volumetric gear pumps for high viscosity plastic materials. These pumps comprise an enclosure in which rotates a set of gears comprising a central gear which cooperates with one or more peripheral gears, each of these wheels being drivable by a driving torque or by a "driving wheel” capable of driving in rotation the other wheels engaged with the latter.
- a driving torque or by a "driving wheel” capable of driving in rotation the other wheels engaged with the latter.
- driving wheel capable of driving in rotation the other wheels engaged with the latter.
- the rubber compounds also have a very high viscosity which causes a very strong resisting torque on the driving wheel.
- This resistant torque is all the more important as one seeks to achieve high flow rates by increasing the width of the gears.
- the high flow rate for rubber compounds is limited by the thermal aspect. Indeed, the increase in flow, mainly a function of the increase in the speed of rotation of the gears is accompanied by a significant increase in the temperature of the rubber compounds. Now this temperature must be both controlled, and especially its increase must be limited, to avoid an anticipated vulcanization of these mixtures.
- gear pumps have the disadvantage of generating leaks that should be reduced, especially when seeking to control the instantaneous volumes of the transferred materials.
- the invention aims to overcome all of these disadvantages.
- the gear pump especially for rubber mixes, comprises an enclosure in which a set of gear wheels is rotated comprising a central gear which cooperates with two other peripheral gear wheels, each of the gear wheels being driven directly by a pair of gear wheels.
- This pump is characterized in that it comprises at least one feed chamber in which at least one feeding means acts to discharge the material towards said enclosure through at least one passage orifice, and means prestressing between the teeth ensuring a sealed contact of the meshing zone of the central wheel with each of the two peripheral wheels.
- This arrangement allows, on the one hand, the transmission of a driving torque to each gear of the gear and secondly a better distribution of the forces between the three gears making the pump more reliable and more resistant, while avoiding material leakage through the gears.
- the supply chamber comprises two passage orifices towards the enclosure, the two passage orifices being disposed symmetrically with respect to the center of the central wheel, and two outlet orifices of the mixture arranged symmetrically by relative to the center of the central wheel so that each passage opening is disposed substantially symmetrically to an outlet orifice relative to the straight line passing through the center of the three toothed wheels in projection in a plane perpendicular to the axes of said wheels
- the gear pump 1 comprises a body 10 comprising an enclosure 12 carrying a set 2 of toothed wheels whose function is to pump volumetrically.
- This assembly 2 comprises a central gear 4 which cooperate respectively with two peripheral gear wheels 3 and 5.
- each of the two peripheral wheels 3, 5 meshes respectively with the central wheel 4 without however being engaged with the latter, in particular to avoid driving one of the toothed wheels by another.
- each of the toothed wheels 3, 4, 5 is driven directly by a motor so as said above to make the pump more reliable.
- a single motor with a specific gearbox can be used to transmit power to each gearwheel.
- the two toothed wheels 3 and 5 are arranged symmetrically with respect to the center of the central gear 4 which has an odd number of teeth. Thus, considering the central wheel 4, it is found that the forces are symmetrical and therefore they cancel each other out.
- the two peripheral toothed wheels 3 and 5 have identical diameters and on each face of each of its wheels is positioned a flange respectively 6 and 7 for the wheel 3 and 8 and 9 for the wheel 5.
- These flanges 6, 7, 8 , 9 whose diameter is greater than or equal to that of the end of the teeth of the wheels 3 and 5 make it possible to eliminate the lateral shear of the rubber mixes on the walls of the pump, which considerably reduces the shears which are exerted on these mixtures.
- the small size of the toothed wheels 3 and 5 makes it possible to generate low forces at the axes.
- each peripheral wheel 3, 5 prestressing means between the teeth of the central wheel 4 and respectively the peripheral wheels 3 and 5 allow through the flanges 6, 7, 8, 9 to achieve a system dynamic sealing by a cantilever said wheels 3 and 5 and by setting atmospheric pressure leaks rubber compounds.
- the prestressing means comprise a screw 25 engaged in a through hole which simultaneously passes through the drive shaft 11 to the shaft 51 of the wheel 5 and the shaft 51.
- the screw also passes through a convex key 26 whose walls curved are respectively in contact with a wall 111 of the drive shaft and a wall 511 of the shaft 51 so that the tightening of the screw 25 generates via the key 26 a torsional torque between the shaft 11 and the shaft 51.
- This preload acts in the same direction as the rotation of the pump represented by the arrow F.
- the body 10 carries a feeding means which consists essentially of a screw 15, rotating in a feed chamber 16.
- the supply and pressurizing chamber 16 has on the opposite side to the assembly 2 of the wheels a not shown supply port for supplying the pump.
- passage orifices 17, 18 are arranged symmetrically with respect to each other with respect to the center of the central wheel 4 and such that they are arranged respectively close to said central wheel and to one of peripheral wheels.
- the enclosure 12 opens onto two outlet orifices of the mixture 19 and 20, also symmetrically disposed relative to each other with respect to the center of the central wheel 4, so that they are respectively disposed of proximity of said center wheel and one of the peripheral wheels, so that each orifice 17, 18 is disposed substantially symmetrically to an outlet port 19, 20 relative to the straight line passing through the center of the three toothed wheels 3, 4, 5 in projection in a plane perpendicular to the axes of said wheels.
- the shape of the teeth has been optimized to convey the mixture in the chamber 12.
- the displacement of the tooth axes is the greatest possible while the peripheral shear surfaces are reduced.
- the outlet orifices 19 and 20 respectively open into two channels, only the channel 19 'corresponding to the orifice 19 is shown in FIG. 4.
- the two channels meet at the junction zone 22 in a channel 23 to a point outlet port 24.
- a rubber mixture is introduced into the feed chamber 16 through a not shown orifice, in a form that can be indifferently a continuous band or granules. The mixture is thus distributed on the booster screw 15.
- the rubber mixture is discharged by being pressurized to the through orifices 17 and 18 which lead to it. in the chamber 12 opening opposite to the center of the main wheel 4 as shown in Figure 2.
- Part of the mixture B thus engages in the tooth cavities of the peripheral wheel 5 to the outlet orifice 19 while the other part of the mixture B engages in the opposite direction of rotation in the tooth cavities from the central wheel 4 to the orifice 20.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
Abstract
Description
La présente invention concerne les pompes volumétriques destinées notamment aux mélanges caoutchouteux et, plus particuliérement, les pompes à engrenage.The present invention relates to positive displacement pumps especially for rubber compounds and, more particularly, gear pumps.
Il est connu d'utiliser des pompes volumétriques à engrenage pour des matériaux plastiques à haute viscosité. Ces pompes comprennent une enceinte dans laquelle tourne un ensemble de roues dentées comprenant une roue dentée centrale qui coopère avec une ou plusieurs roues dentées périphériques, chacune de ces roues pouvant être entraînée par un couple moteur ou par une « roue menante » apte à entraîner en rotation les autres roues en prise avec cette dernière. De telles applications sont décrites dans les publications
Lorsque l'on cherche à transférer des matériaux fortement visqueux ,comme des mélanges caoutchouteux, il s'avère nécessaire en outre de placer un moyen de gavage qui permet d'alimenter de façon forcée ladite pompe en matériau, comme cela est décrit dans les publications
Les mélanges caoutchouteux présentent également une très haute viscosité qui provoque un couple résistant très important sur la roue menante. Ce couple résistant est d'autant plus important que l'on cherche à atteindre des débits importants en augmentant la largeur des roues dentées. Ces difficultés sont tellement importantes que, dans les applications de pompes à engrenage au caoutchouc, on constate de fréquentes ruptures des roues dentées.The rubber compounds also have a very high viscosity which causes a very strong resisting torque on the driving wheel. This resistant torque is all the more important as one seeks to achieve high flow rates by increasing the width of the gears. These difficulties are so great that in rubber gear pump applications there are frequent breaks in the gears.
Par ailleurs, l'atteinte de débit important pour les mélanges caoutchouteux est limitée par l'aspect thermique. En effet, l'augmentation de débit, principalement fonction de l'augmentation de la vitesse de rotation des roues dentées s'accompagne d'une élévation importante de la température des mélanges caoutchouteux. Or cette température doit être à la fois maîtrisée, et surtout son augmentation doit être limitée, pour éviter une vulcanisation anticipée de ces mélanges.Moreover, the high flow rate for rubber compounds is limited by the thermal aspect. Indeed, the increase in flow, mainly a function of the increase in the speed of rotation of the gears is accompanied by a significant increase in the temperature of the rubber compounds. Now this temperature must be both controlled, and especially its increase must be limited, to avoid an anticipated vulcanization of these mixtures.
Enfin, ces pompes à engrenage présentent l'inconvénient de générer des fuites qu'il convient de réduire, en particulier lorsque l'on cherche à contrôler les volumes instantanés des matériaux transférés.Finally, these gear pumps have the disadvantage of generating leaks that should be reduced, especially when seeking to control the instantaneous volumes of the transferred materials.
L'invention vise à pallier l'ensemble de ces inconvénients.The invention aims to overcome all of these disadvantages.
Selon l'invention, la pompe à engrenage notamment pour des mélanges caoutchouteux, comporte une enceinte dans laquelle tourne un ensemble de roues dentées comprenant une roue dentée centrale qui coopère avec deux autres roues dentées périphériques, chacune des roues dentées étant entraînée directement par un couple moteur.. Cette pompe est caractérisée en ce qu'elle comporte au moins une chambre d'alimentation dans laquelle agit au moins un moyen de gavage pour refouler la matière vers ladite enceinte au travers d'au moins un orifice de passage, et des moyens de précontrainte entre les dents assurant un contact étanche de la zone d'engrènement de la roue centrale avec chacune des deux roues périphériques.According to the invention, the gear pump, especially for rubber mixes, comprises an enclosure in which a set of gear wheels is rotated comprising a central gear which cooperates with two other peripheral gear wheels, each of the gear wheels being driven directly by a pair of gear wheels. This pump is characterized in that it comprises at least one feed chamber in which at least one feeding means acts to discharge the material towards said enclosure through at least one passage orifice, and means prestressing between the teeth ensuring a sealed contact of the meshing zone of the central wheel with each of the two peripheral wheels.
Cette disposition permet, d'une part, la transmission d'un couple moteur à chaque roue dentée de l'engrenage et d'autre part une meilleure répartition des efforts entre les trois roues dentées rendant plus fiable et plus résistante la pompe, tout en évitant les fuites de matériau par les engrenages.This arrangement allows, on the one hand, the transmission of a driving torque to each gear of the gear and secondly a better distribution of the forces between the three gears making the pump more reliable and more resistant, while avoiding material leakage through the gears.
Selon une caractéristique de l'invention, la chambre d'alimentation comporte deux orifices de passage vers l'enceinte, les deux orifices de passage étant disposés symétriquement par rapport au centre de la roue centrale, et deux orifices de sortie du mélange disposés symétriquement par rapport au centre de la roue centrale de sorte que chaque orifice de passage soit disposé sensiblement symétriquement à un orifice de sortie par rapport à la droite passant par le centre des trois roues dentées en projection dans un plan perpendiculaire aux axes desdites rouesAccording to a characteristic of the invention, the supply chamber comprises two passage orifices towards the enclosure, the two passage orifices being disposed symmetrically with respect to the center of the central wheel, and two outlet orifices of the mixture arranged symmetrically by relative to the center of the central wheel so that each passage opening is disposed substantially symmetrically to an outlet orifice relative to the straight line passing through the center of the three toothed wheels in projection in a plane perpendicular to the axes of said wheels
Ainsi, le parcours des mélanges caoutchouteux dans l'enceinte est minimisé ce qui limite également les montées en température.Thus, the course of the rubber compounds in the enclosure is minimized which also limits the rise in temperature.
D'autres caractéristiques et avantages de l'invention apparaîtront à la lecture d'un exemple de réalisation d'une pompe volumétrique conforme à l'invention, en référence au dessin dans lequel:
- la figure 1 est une coupe longitudinale partielle de la pompe conforme à l'invention selon la ligne I-I représentée sur la figure 2,
- la figure 2 est une coupe radiale grossie de la pompe conforme à l'invention selon la ligne II-II représentée sur la figure 1,
- la figure 3 est une coupe fonctionnelle de la zone de gavage de la pompe conforme à l'invention selon la ligne III représentée sur la figure 2,
- la figure 4 est une coupe fonctionnelle de la zone de refoulement de la pompe conforme à l'invention selon la ligne IV représentée sur la figure 2,
- la figure 5 est une coupe partielle des moyens de précontrainte entre les dents de la pompe selon la ligne V représentée sur la figure 1.
- FIG. 1 is a partial longitudinal section of the pump according to the invention along the line II shown in FIG. 2,
- FIG. 2 is an enlarged radial section of the pump according to the invention along the line II-II shown in FIG. 1,
- FIG. 3 is a functional section of the booster zone of the pump according to the invention along the line III shown in FIG. 2,
- FIG. 4 is a functional section of the discharge zone of the pump according to the invention along the line IV shown in FIG. 2,
- FIG. 5 is a partial section of the prestressing means between the teeth of the pump along the line V shown in FIG. 1.
Selon les figures 1 et 2, la pompe à engrenage 1 comprend un corps 10 comportant une enceinte 12 portant un ensemble 2 de roues dentées dont la fonction est de pomper volumétriquement.According to FIGS. 1 and 2, the gear pump 1 comprises a
Cet ensemble 2 comporte une roue dentée centrale 4 qui coopèrent respectivement avec deux roues dentées périphériques 3 et 5.This
Chacune des deux roues périphériques 3, 5 engrène respectivement avec la roue centrale 4 sans être cependant en prise avec cette dernière, afin d'éviter notamment l'entraînement de l'une des roues dentées par une autre. En effet, chacune des roues dentées 3, 4, 5 est entraînée directement par un moteur afin comme on l'a dit précédemment de rendre la pompe plus fiable. Bien entendu, on peut utiliser un seul moteur avec un réducteur spécifique pour transmettre la puissance à chaque roue dentée.Each of the two
Les deux roues dentées 3 et 5 sont disposées symétriquement par rapport au centre de la roue dentée centrale 4 qui comporte un nombre de dents impair. Ainsi, en considérant la roue centrale 4, on constate que les efforts sont symétriques et donc qu'ils s'annulent.The two
Les deux roues dentées périphériques 3 et 5 ont de diamètres identiques et sur chaque face de chacune de ses roues est positionné un flasque respectivement 6 et 7 pour la roue 3 et, 8 et 9 pour la roue 5. Ces flasques 6, 7, 8, 9 dont le diamètre est supérieur ou égal à celui de l'extrémité des dentures des roues 3 et 5 permettent de supprimer le cisaillement latéral des mélanges caoutchouteux sur les parois de la pompe, ce qui réduit considérablement les cisaillements qui s'exercent sur ces mélanges. De plus, la petite taille des roues dentées 3 et 5 permet d'engendrer de faibles efforts au niveau des axes.The two
Par ailleurs, il existe pour chaque roue périphérique 3, 5 des moyens de précontrainte entre les dents de la roue centrale 4 et respectivement les roues périphériques 3 et 5 permettent par l'intermédiaire des flasques 6, 7, 8, 9 de réaliser un système d'étanchéité dynamique par une mise en porte à faux desdites roues 3 et 5 et par une mise à pression atmosphérique des fuites de mélanges caoutchouteux.Moreover, there exists for each
Les moyens de précontrainte agissant sur les roues 3 et 5 étant identiques, on ne décrira dans ce qui suit que les moyens agissant sur la 5 en référence aux figures 1 et 5.Since the prestressing means acting on the
Les moyens de précontrainte comprennent une vis 25 engagée dans un orifice de passage qui traverse simultanément l'arbre moteur 11 de transmission à l'arbre 51 de la roue 5 et l'arbre 51. La vis traverse également une clavette bombée 26 dont les parois bombées sont en contact respectivement avec une paroi 111 de l'arbre moteur et une paroi 511 de l'arbre 51 de sorte que le serrage de la vis 25 génère par l'intermédiaire de la clavette 26 un couple torsionnel entre l'arbre moteur 11 et l'arbre 51. Cette précontrainte agit dans le même sens que la rotation de la pompe représenté par la flèche F.The prestressing means comprise a
L'échappement de mélanges caoutchouteux des roues 3 et 5 s'effectue par des exutoires situés sur les flasques 6, 7, 8 et 9 et azimutés avec précision, comme on le voit sur la figure 2.The escape of rubber mixtures from the
Le corps 10 porte un moyen de gavage qui consiste essentiellement en une vis 15, en rotation dans une chambre d'alimentation 16.The
On pourrait sans sortir du cadre de l'invention, envisager la présence de plusieurs vis débouchant sur une même chambre d'accumulation.Without departing from the scope of the invention, consider the presence of several screws opening on the same accumulation chamber.
La chambre d'alimentation et de mise en pression 16 comporte du côté opposé à l'ensemble 2 des roues un orifice d'alimentation non représenté servant à alimenter la pompe.The supply and pressurizing
A l'autre extrémité de la chambre d'alimentation 16, sont situés deux orifices de passage 17, 18 assurant la communication entre la chambre d'alimentation et mise en pression 16 et l'enceinte 12 contenant l'ensemble 2 des roues tel qu'on le voit sur la figure 3.At the other end of the
Ces orifices de passage 17, 18 sont disposés symétriquement l'un vis-à-vis de l'autre par rapport au centre de la roue centrale 4 et tels qu'ils soient respectivement disposés à proximité de ladite roue centrale et de l'une des roues périphériques.These
L'enceinte 12 débouche sur deux orifices de sortie du mélange 19 et 20, également disposés symétriquement l'un vis-à-vis de l'autre par rapport au centre de la roue centrale 4, de sorte qu'ils soient respectivement disposés à proximité de ladite roue centrale et de l'une des roues périphériques, de sorte que chaque orifice de passage 17, 18 soit disposé sensiblement symétriquement à un orifice de sortie 19, 20 par rapport à la droite passant par le centre des trois roues dentées 3, 4, 5 en projection dans un plan perpendiculaire aux axes desdites roues.The
Cette disposition permet d'optimiser le chemin parcouru par le mélange caoutchouteux en le minimisant comme on le verra plus clairement dans ce qui suit.This arrangement makes it possible to optimize the path traveled by the rubber compound by minimizing it, as will be seen more clearly in what follows.
Ainsi la distance entre la zone d'admission dans l'enceinte 12 et la zone de refoulement est minimale, ce qui facilité également la garantie de l'étanchéité.Thus the distance between the intake zone in the
Enfin, la forme des dentures a été optimisée pour véhiculer le mélange dans l'enceinte 12. La cylindrée des axes de dent est la plus grande possible alors que les surfaces de cisaillement périphériques sont réduites.Finally, the shape of the teeth has been optimized to convey the mixture in the
Les orifices de sortie 19 et 20 débouchent respectivement dans deux canaux, seul le canal 19' correspondant à l'orifice 19 est représenté sur la figure 4. Les deux canaux se rejoignent à la zone de jonction 22 dans un canal 23 jusqu'à un orifice de sortie 24.The
On décrira succinctement ci-après, le fonctionnement d'une pompe à engrenage conforme à l'invention telle que décrite précédemment, en référence à aux figures 2, 3 et 4.Briefly described below, the operation of a gear pump according to the invention as described above, with reference to Figures 2, 3 and 4.
On introduit un mélange caoutchouteux dans la chambre d'alimentation 16 par un orifice non représenté, sous une forme pouvant être indifféremment une bande continue ou des granulés. Le mélange est ainsi distribué sur la vis de gavage 15.A rubber mixture is introduced into the
Dans la chambre d'alimentation 15, le mélange caoutchouteux est refoulé en étant mis sous pression jusqu'aux orifices de passage 17 et 18 qui le conduisent dans l'enceinte 12 en débouchant à l'opposé par rapport au centre de la roue principale 4 comme le montre la figure 2.In the
On notera B et C les deux parties du mélange débouchant respectivement des orifices 17 et 18 pour suivre leur parcours à l'aide des flèches représentées sur la figure 2.Note B and C the two parts of the mixture opening respectively
Une partie du mélange B s'engage ainsi dans les creux de dents de la roue périphérique 5 jusqu'à l'orifice de sortie 19 alors que l'autre partie du mélange B s'engage en sens de rotation inverse dans les creux de dents de la roue centrale 4 jusqu'à l'orifice 20.Part of the mixture B thus engages in the tooth cavities of the peripheral wheel 5 to the
De la même façon une partie du flux du mélange C s'engage dans les creux de dents de la roue périphériques 3 jusqu'à l'orifice 20 et l'autre partie en sens inverse de rotation dans les creux de dents de la roue 4 vers l'orifice 19.In the same way a part of the flow of the mixture C engages in the tooth cavities of the
Le montage en précontrainte des dents des roues 3 et 5 respectivement au contact des dents de la roue 4 empêche le mélange de fluer entre les dents des roues 3 et 4 ou 5 et 4.The prestressing of the teeth of the
Le chemin parcouru dans par les flux B et C de mélange comme on le voit clairement est assez court ce qui limite considérablement les montées en température dans cette zone.The path traveled by the flow B and C mixture as clearly seen is quite short which considerably limits the rise in temperature in this area.
Les flux B et C issus des orifices de sortie 19 et 20 débouchent alors, comme le montre la figure 4 dans le canal 19' et le canal non représenté correspondant à l'orifice 20 puis les flux se rejoignent dans la zone de jonction 22 pour s'écouler à travers le canal 23 jusqu'à l'orifice de sortie 24.The flows B and C coming from the outlet orifices 19 and 20 then open, as shown in FIG. 4 in the
Claims (6)
- A gear pump (1) in particular for rubber mixes, comprising an enclosure (12) in which rotates a set of gearwheels comprising a central gearwheel (4) which cooperates with other two peripheral gearwheels (3, 5), each of the gearwheels (3, 4, 5) being driven directly by a driving torque,
characterized in that said pump comprises at least one feed chamber (15) in which acts at least one feed means for delivering the material to said enclosure (12) via at least one passage orifice (17, 18), and prestressing means between the teeth (25, 26) ensuring hermetic contact of the meshing zone of the central wheel (4) with each of the two peripheral wheels (3, 5). - A pump according to Claim 1, in which the prestressing means ensure tightness by means, for each peripheral gearwheel (3, 5), of two side plates (6, 7, 8, 9) surrounding the wheel, the diameter of these side plates being greater than or equal to that of the ends of the teeth of the wheel in question.
- A pump according to any one of Claims 1 or 2, in which the prestressing means comprise, for each peripheral wheel, a screw (25) cooperating by means of a domed wedge (26) with the driving shaft (11) for transmission to the shaft (51) for driving the wheel in question (5) and said drive shaft (51) so as to impose a torsional moment between these two shafts (11, 51).
- A pump according to any one of Claims 1 to 3, in which the two peripheral wheels (3, 5) are arranged symmetrically to the centre of the central wheel (4), which has an odd number of teeth.
- A pump according to any one of Claims 1 to 4, in which the two peripheral wheels (3, 5) have a diameter less than that of the central wheel (4).
- A pump according to any one of Claims 1 to 5, in which the feed chamber (15) comprises two passage orifices (17, 18) towards the enclosure (12), the two passage orifices (17, 18) being arranged symmetrically to the centre of the central wheel (4), and two outlet orifices (19, 20) for the mix which are arranged symmetrically to the centre of the central wheel such that each passage orifice (17, 18) is arranged substantially symmetrically to an outlet orifice (19, 20) relative to the straight line passing through the centre of the three gearwheels (3, 4, 5) projecting into a plane perpendicular to the axes of said wheels.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| FR0110879A FR2828717A1 (en) | 2001-08-16 | 2001-08-16 | GEAR PUMP |
| FR0110879 | 2001-08-16 | ||
| PCT/EP2002/008970 WO2003016720A1 (en) | 2001-08-16 | 2002-08-09 | Gear pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1421281A1 EP1421281A1 (en) | 2004-05-26 |
| EP1421281B1 true EP1421281B1 (en) | 2008-01-23 |
Family
ID=8866580
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP02758458A Expired - Lifetime EP1421281B1 (en) | 2001-08-16 | 2002-08-09 | Gear pump |
Country Status (8)
| Country | Link |
|---|---|
| US (1) | US7335005B2 (en) |
| EP (1) | EP1421281B1 (en) |
| JP (1) | JP4279139B2 (en) |
| CN (1) | CN1320276C (en) |
| AT (1) | ATE384875T1 (en) |
| DE (1) | DE60224811T2 (en) |
| FR (1) | FR2828717A1 (en) |
| WO (1) | WO2003016720A1 (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10348985B3 (en) * | 2003-10-22 | 2005-05-19 | Berstorff Gmbh | gear pump |
| US8292597B2 (en) * | 2008-10-16 | 2012-10-23 | Pratt & Whitney Canada Corp. | High-speed gear pump |
| US8137085B2 (en) * | 2008-12-18 | 2012-03-20 | Hamilton Sundstrand Corporation | Gear pump with slots in teeth to reduce cavitation |
| US8087913B2 (en) * | 2008-12-22 | 2012-01-03 | Hamilton Sundstrand Corporation | Gear pump with unequal gear teeth on drive and driven gear |
| CN103206258A (en) * | 2012-01-16 | 2013-07-17 | 陈园国 | Novel pneumatic motor |
| CN109882406B (en) * | 2019-04-18 | 2024-05-28 | 青岛科技大学 | Double-tooth feeding type rubber gear pump |
| CN111005867B (en) * | 2019-12-25 | 2021-10-08 | 潍柴动力股份有限公司 | Driving shaft connecting structure of pump and combined gear pump |
Family Cites Families (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2088121A (en) * | 1932-10-01 | 1937-07-27 | Swink Rufus Clyde | Rotary engine |
| FR1103716A (en) * | 1953-12-28 | 1955-11-07 | Prec Ind | Advanced Multi-Gear Pumps |
| US3050009A (en) * | 1960-10-28 | 1962-08-21 | Lowry Hydraulic Co | Postitive pressure pump |
| GB1057282A (en) * | 1963-04-19 | 1967-02-01 | John Wilmott Marshall | Rotary internal combustion engines and fluid motors |
| US3854492A (en) * | 1969-07-31 | 1974-12-17 | Shimadzu Corp | Gear type flow divider |
| DE2321639A1 (en) * | 1973-04-28 | 1974-11-07 | Georg Draeger | GEAR PUMP OR GEAR MOTOR |
| GB1518503A (en) * | 1974-07-15 | 1978-07-19 | Ici Ltd | Liquid mixing gear pumps |
| US3941527A (en) * | 1974-10-29 | 1976-03-02 | Allington Jackson H | Rotary engine |
| US4145168A (en) * | 1976-11-12 | 1979-03-20 | Bobby J. Travis | Fluid flow rotating machinery of lobe type |
| SE407839B (en) * | 1977-09-15 | 1979-04-23 | Imo Industri Ab | SCREWDRIVER |
| DE4111218C2 (en) * | 1991-04-07 | 1995-12-21 | Troester Maschf Paul | Gear pump for pumping rubber compounds that are difficult to process |
| US5120206A (en) | 1991-04-08 | 1992-06-09 | Bridgestone/Firestone, Inc. | Gear metering pump for compounded elastomeric material |
| DE4130312C1 (en) * | 1991-09-12 | 1992-12-24 | Hermann Berstorff Maschinenbau Gmbh, 3000 Hannover, De | |
| CN2118181U (en) * | 1992-01-04 | 1992-10-07 | 万舜伯 | Planetary gear pump |
| US5788471A (en) * | 1996-06-11 | 1998-08-04 | Eaton Corporation | Spool valve wheel motor |
-
2001
- 2001-08-16 FR FR0110879A patent/FR2828717A1/en active Pending
-
2002
- 2002-08-09 DE DE60224811T patent/DE60224811T2/en not_active Expired - Lifetime
- 2002-08-09 AT AT02758458T patent/ATE384875T1/en not_active IP Right Cessation
- 2002-08-09 CN CNB028159829A patent/CN1320276C/en not_active Expired - Fee Related
- 2002-08-09 JP JP2003520986A patent/JP4279139B2/en not_active Expired - Fee Related
- 2002-08-09 EP EP02758458A patent/EP1421281B1/en not_active Expired - Lifetime
- 2002-08-09 WO PCT/EP2002/008970 patent/WO2003016720A1/en active IP Right Grant
-
2004
- 2004-02-17 US US10/778,224 patent/US7335005B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CN1320276C (en) | 2007-06-06 |
| US20040161357A1 (en) | 2004-08-19 |
| JP2005500456A (en) | 2005-01-06 |
| DE60224811D1 (en) | 2008-03-13 |
| DE60224811T2 (en) | 2009-01-22 |
| EP1421281A1 (en) | 2004-05-26 |
| WO2003016720A1 (en) | 2003-02-27 |
| JP4279139B2 (en) | 2009-06-17 |
| US7335005B2 (en) | 2008-02-26 |
| ATE384875T1 (en) | 2008-02-15 |
| CN1543541A (en) | 2004-11-03 |
| FR2828717A1 (en) | 2003-02-21 |
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