EP1658437A1 - Gear tooth and external gear pump - Google Patents

Gear tooth and external gear pump

Info

Publication number
EP1658437A1
EP1658437A1 EP04785984A EP04785984A EP1658437A1 EP 1658437 A1 EP1658437 A1 EP 1658437A1 EP 04785984 A EP04785984 A EP 04785984A EP 04785984 A EP04785984 A EP 04785984A EP 1658437 A1 EP1658437 A1 EP 1658437A1
Authority
EP
European Patent Office
Prior art keywords
tooth
gear
sector
gear pump
convex
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
EP04785984A
Other languages
German (de)
French (fr)
Other versions
EP1658437B1 (en
Inventor
Jo o MERENDEIRO
José RIBAFEITA
Quê VU DO
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Renault SAS
Original Assignee
Renault SAS
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Renault SAS filed Critical Renault SAS
Publication of EP1658437A1 publication Critical patent/EP1658437A1/en
Application granted granted Critical
Publication of EP1658437B1 publication Critical patent/EP1658437B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • 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 a gear tooth and a pump, in particular an oil pump provided with corresponding gears. More specifically, this invention relates to a gear tooth having a foot concave at its starting point at the foot of the neighboring tooth, and a head connected to said foot.
  • This tooth finds a preferred, but not exclusive, application in an external gear pump comprising at least one pair of toothed pinions in mutual engagement.
  • Such a pump which is also the subject of the invention, can be used in a combustion engine, but the invention also applies to all pumps with external gears.
  • a conventional gear pump tooth profile has a concave trochoidal base followed by an involute head.
  • the object of the present invention is to increase the volume of oil displaced between the teeth by optimizing the profile thereof without prejudice to the continuity of the gear. More precisely, the objective sought is to increase the flow rate, the pressure and the volumetric efficiency at low 1 speed of a gear pump, without increasing its size.
  • the invention proposes that the head of each tooth has two convex sectors connected by a transition point marking a break in the curve.
  • the second active point of the profile thus delimits the bottom of a notch inscribed in the profile of the tooth.
  • the first convex sector of the tooth head has an involute profile.
  • the pump proposed by the invention comprises two identical or different toothed wheels.
  • FIG. 1 shows in section a tooth of a toothed wheel according to the invention
  • FIGs 2A to 2F illustrate the gearing of the two wheels of the pump
  • - Figures 3A and 3B highlight the gains obtained by l 'invention.
  • Figure 1 highlights the two main parts of tooth 1, namely its foot 2 and its head 3, connected by an active transition point 4.
  • the foot 2 has a concave shape, and is connected to its starting point 6, at the foot of the neighboring tooth (not shown in Figure 1).
  • the tooth head has two convex sectors 7, 8, connected by an active point of
  • the transition point 9 delimits the bottom of a notch inscribed in the profile of the tooth.
  • the convex sector 7 following the first transition point 4 has an involute profile. This involute profile therefore extends between the two active transition points 4 and 9 of tooth 1, and constitutes a first convex sector of the foot 2.
  • the second convex sector 8, or convex extension profile, which makes further to point 9, can also have a prof in involute of circle, without however that this particular provision is imperative, and one can envisage other extension profiles for this second convex sector, without departing from the scope of the invention.
  • the head of the tooth has a rounded end sector 11, connected to the second convex sector 8 by a transition sector 12.
  • the tooth is symmetrical, and there is a concordance of shape between the end sector 11 of the teeth. and the concave sector defined by the juxtaposition of two feet 2 of neighboring teeth, so that the end sector of a tooth can roll between two teeth of the opposite wheel, keeping contact with them until what it escapes.
  • the two gears of the pump can be identical, and this characteristic provides a considerable advantage to the proposed pump, in terms of process and manufacturing costs. Referring to Figures 2A to 2F ( Figure 2F corresponding to the same meshing situation as Figure 2A for the following teeth), we see that there are several points of contact between the teeth.
  • the tooth 1a of a first wheel has just exceeded the axis of symmetry of the opposite gap. It is in main support (double circle) by its convex surface 8 with the active transition point 4 of the opposite tooth 1b, while its end sector 11, rolls on the concave foot 2 thereof. After a slight relative displacement of the teeth 1a, 1b (FIG.
  • the main fulcrum is between the convex sector 7 of the tooth le and the active transition point 4 of the tooth ld, while the head of the wheel le, rolls in the transition region of the teeth la and ld.
  • the end sector continues to roll on the foot 2 of the tooth la, while the main support is between the active transition point 4 of the tooth ld and the convex sector 7 of the tooth le (FIG. 2E).
  • FIG. 2F a situation similar to FIG. 2A has been found, but this time between the teeth le and id.
  • FIG. 3A shows the very significant increase in the volume of the interposed displaced with respect to a conventional tooth developing in a circle, thanks to the lengthening of the height of the tooth and to the increase in the interval between the teeth.
  • FIG. 3B is a figure of principle, where one can see the different trajectories of several points of the tooth profile proposed by the invention, in the intersection of the conjugate pinion, with a pronounced elongated epicyclic effect, allowing strong development of the volume moved.
  • the tooth profile proposed by the invention has the particularity of combining sections in the involute of a circle, the advantages of which are already known, with bearing sections with special profiles. This combination simultaneously ensures continuity of engagement and a sufficient toothing line and a very strong development of the volume of oil displaced.
  • the tooth profile proposed by the invention allows in particular a flow gain, in particular at low speed, of the order of 30% to 40%, compared to a conventional pump toothing with involute of a circle.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Gears, Cams (AREA)
  • Dental Tools And Instruments Or Auxiliary Dental Instruments (AREA)

Abstract

The gear tooth (1) has a concave foot (2) connecting it to the neighbouring tooth, and a tip (3) that is connected to the foot by a first transition point (4). The tooth tip has two convex sectors (7, 8) connected by a second transition point (9) in the form of a notch marking a break in the surface of the tooth profile. The convex sectors are both in the shape of arcs that are involute to a circle, and the tooth tip has a rounded surface (11) that is connected to each second convex sector by a transition sector (12). A gear pump has at least one pair of gears with meshing teeth shaped as described above.

Description

DENT D'ENGRENAGE ET POMPE A ENGRENAGES EXTERIEURSGEAR TOOTH AND EXTERNAL GEAR PUMP
La présente invention concerne une dent d'engrenage et une pompe, notamment une pompe à huile munie d'engrenages correspondants. Plus précisément, cette invention a pour objet une dent d'engrenage présentant un pied concave à son point de départ au pied de la dent voisine, et une tête raccordée audit pied. Cette dent trouve une application privilégiée, mais non exclusive dans une pompe à engrenages extérieurs comportant au moins une paire de pignons dentés en engrènement mutuel. Une telle pompe, qui fait également l'objet de l'invention, est utilisable dans un moteur à combustion, mais l'invention s'applique également sur toutes les pompes à engrenages extérieurs. Les pompes à huile utilisées dans les moteurs sont de deux types : les pompes à engrenages extérieurs avec des dentures droites ou à développante de cercle, et les pompes à engrenages intérieurs, avec des profils de dents trochoïdaux droits ou à développante de cercle. Les évolutions actuelles des moteurs, et notamment celles de leurs accessoires, augmentent les besoins en débit et en pression d'huile des pompes utilisées. Par ailleurs, les contraintes d'encombrement dans l'environnement moteur sont de plus en plus fortes. Les voies conventionnelles empruntées pour augmenter les performances hydrauliques des pompes à engrenages sont notamment l'augmentation de la vitesse de la pompe, l'augmentation de la hauteur des engrenages pompe, la réduction des jeux hydrauliques, ou l'augmentation du nombre de pignons. Toutefois, les pompes à huile ont de faibles rendements volumétriques à bas régime, de sorte qu'elles sont généralement surdimensionnées à haut régime, et qu'il est souvent nécessaire de décharger une part importante de l'huile pompée à haut régime, voire la moitié de celle-ci, par un clapet de décharge. Il existe différents profils de denture de pompe à engrenages extérieurs. La géométrie standard, du type à denture droite à développante de cercle, a des performances modestes. En effet, si on cherche à augmenter le volume d'huile déplacé, en optimisant le profil des dents, on se heurte rapidement à différentes contraintes. La possibilité d'accroître le diamètre extérieur de la dent est limité par la faible épaisseur de celle-ci et par le risque d'avoir une dent trop pointue. Par ailleurs, l'allongement de la dent s'effectue au détriment de la continuité de l'engrènement, notamment au niveau du pied de dent. Enfin, l'interférence entre le cercle de base et le pied de dent, souffre également de l'allongement de celle-ci. Un profil classique de dent de pompe à engrenages comporte une base concave trochoïdale suivie d'une tête en développante de cercle. II a déjà été proposé d'améliorer les performances d'une pompe à engrenages extérieurs en abandonnant les profils à développantes de cercle au profit d'autres profils tels que des épicycloïdes ou des hypocycloïdes se raccordant sur le cercle primitif de la roue dentée, c'est à dire sur la ligne circulaire théorique qui roule sur une ligne équivalente de la roue opposée Cependant, les gains ainsi obtenus par rapport aux dentures classiques sont insuffisants. De plus, en s'écartant de celles-ci, on se heurte rapidement à des choix techniques difficiles, et à une augmentation des coûts de fabrication. Le but de la présente invention est d'augmenter le volume d'huile déplacé entre les dents par une optimisation du profil de celles-ci sans préjudice de la continuité de l'engrenement. Plus précisément, l'objectif recherché est d'élever le débit, la pression et le rendement volumétrique à bas1 régime d'une pompe à engrenages, sans augmenter son encombrement. Dans ce but, l'invention propose que la tête de chaque dent présente deux secteurs convexes raccordés par un point de transition marquant une rupture de courbe. Le second point actif du profil délimite ainsi le fond d'une entaille inscrite dans le profil de la dent. Selon un mode de réalisation préféré de l'invention, le premier secteur convexe de la tête de dent, a un profil en développante de cercle. Enfin, la pompe proposée par l'invention, comporte deux roues dentées identiques ou non. D'autres caractéristiques et avantages de l'invention apparaîtront clairement à la lecture de la description suivante d'un mode de réalisation particulier de celle-ci, en liaison avec les dessins annexés, sur lesquels : - la figure 1 représente en coupe une dent de roue dentée conforme à l'invention, - les figures 2A à 2F illustrent l'engrenement des deux roues de la pompe, et - les figures 3A et 3B mettent en évidence les gains obtenus par l'invention. La figure 1 met en évidence les deux parties principales de la dent 1, à savoir son pied 2 et sa tête 3, raccordés par un point actif de transition 4. Le pied 2 a une forme concave, et est raccordé à son point de départ 6, au pied de la dent voisine (non représentée sur le figure 1). Conformément à l'invention, la tête de dent présente deux secteurs convexes 7, 8, raccordés par un point actif deThe present invention relates to a gear tooth and a pump, in particular an oil pump provided with corresponding gears. More specifically, this invention relates to a gear tooth having a foot concave at its starting point at the foot of the neighboring tooth, and a head connected to said foot. This tooth finds a preferred, but not exclusive, application in an external gear pump comprising at least one pair of toothed pinions in mutual engagement. Such a pump, which is also the subject of the invention, can be used in a combustion engine, but the invention also applies to all pumps with external gears. There are two types of oil pumps used in engines: external gear pumps with straight teeth or involute, and internal gear pumps with profiles of straight or involute teeth. The current evolutions of the engines, and in particular those of their accessories, increase the needs in flow and in oil pressure of the pumps used. In addition, the space constraints in the engine environment are increasingly strong. The conventional ways used to increase the hydraulic performance of gear pumps are in particular increasing the speed of the pump, increasing the height of the pump gears, reducing the hydraulic clearances, or increasing the number of pinions. However, oil pumps have low volumetric efficiency at low speed, so that they are generally oversized at high speed, and it is often necessary to discharge a large part of the pumped oil at high speed, even the half of it, by a relief valve. There are different tooth profiles for external gear pumps. The standard geometry, of the straight tooth type with an involute, has modest performances. Indeed, if one seeks to increase the volume of oil displaced, by optimizing the profile of the teeth, one quickly encounters various constraints. The possibility of increasing the outside diameter of the tooth is limited by its small thickness and by the risk of having a tooth that is too sharp. Furthermore, the elongation of the tooth takes place at the expense of the continuity of the meshing, in particular at the level of the tooth base. Finally, the interference between the base circle and the tooth base also suffers from its elongation. A conventional gear pump tooth profile has a concave trochoidal base followed by an involute head. It has already been proposed to improve the performance of an external gear pump by abandoning the involute profiles in favor of other profiles such as epicycloids or hypocycloids connecting to the primitive circle of the gear wheel, that is to say on the theoretical circular line which rolls on an equivalent line of the opposite wheel However, the gains thus obtained compared to conventional toothing are insufficient. In addition, by deviating from these, one quickly comes up against difficult technical choices, and an increase in manufacturing costs. The object of the present invention is to increase the volume of oil displaced between the teeth by optimizing the profile thereof without prejudice to the continuity of the gear. More precisely, the objective sought is to increase the flow rate, the pressure and the volumetric efficiency at low 1 speed of a gear pump, without increasing its size. To this end, the invention proposes that the head of each tooth has two convex sectors connected by a transition point marking a break in the curve. The second active point of the profile thus delimits the bottom of a notch inscribed in the profile of the tooth. According to a preferred embodiment of the invention, the first convex sector of the tooth head, has an involute profile. Finally, the pump proposed by the invention comprises two identical or different toothed wheels. Other characteristics and advantages of the invention will appear clearly on reading the following description of a particular embodiment thereof, in conjunction with the appended drawings, in which: - Figure 1 shows in section a tooth of a toothed wheel according to the invention, - Figures 2A to 2F illustrate the gearing of the two wheels of the pump, and - Figures 3A and 3B highlight the gains obtained by l 'invention. Figure 1 highlights the two main parts of tooth 1, namely its foot 2 and its head 3, connected by an active transition point 4. The foot 2 has a concave shape, and is connected to its starting point 6, at the foot of the neighboring tooth (not shown in Figure 1). According to the invention, the tooth head has two convex sectors 7, 8, connected by an active point of
•fransiiion 9, marquant une rupture -de- cour-be. Le point de transition 9, délimite le fond d'une entaille inscrite dans le profil de la dent. Selon une autre caractéristique de l'invention, le secteur convexe 7 faisant suite au premier point de transition 4, a un profil en développante de cercle. Ce profil en développante de cercle s'étend donc entre les deux points actifs de transition 4 et 9 de la dent 1, et constitue un premier secteur convexe du pied 2. Le second secteur convexe 8, ou profil convexe d'extension, qui fait suite au point 9, peut également avoir un prof il en développante de cercle, sans toutefois que cette disposition particulière soit impérative, et on peut envisager d'autres profils d'extension pour ce second secteur convexe, sans sortir du cadre de l'invention. Enfin, la tête de la dent présente un secteur d'extrémité arrondi 11, raccordé au second secteur convexe 8 par un secteur de transition 12. La dent est symétrique, et il y a concordance de forme entre le secteur d'extrémité 11 des dents et le secteur concave défini par la juxtaposition de deux pieds 2 de dents voisines, de sorte que le secteur d'extrémité d'une dent, peut rouler entre deux dents de la roue opposée, en gardant le contact avec celles-ci jusqu'à ce qu'il s'en échappe. Enfin, les deux roues dentées de la pompe peuvent être identiques, et cette caractéristique procure un avantage considérable à la pompe proposée, en termes de procédé et de coûts de fabrication. En se reportant aux figures 2A à 2F (la figure 2F correspondant à la même situation d'engrènement que la figure 2A pour les dents suivantes), on voit qu'il y a plusieurs points de contact entre les dents. Sur ces figures, on a représenté avec un double cercle les points d'appui dits principaux par lesquels la roue menante entraîne la roue menée, et avec un simple des points de contact secondaires permettant d'assurer le rattrapage des jeux de fonctionnement et la continuité de l'engrenement. Sur la figure 2A, la dent la d'une première roue vient de dépasser l'axe de symétrie de l'entredent opposé. Elle est en appui principal (double cercle) par sa surface convexe 8 avec le point actif de transition 4 de la dent opposée lb, tandis que son secteur d'extrémité 11, roule sur le pied concave 2 de celle-ci. Après un léger déplacement relatif des dents la, lb (figure 2B), on voit que les deux points d'appui précédents se sont déplacés, et qu'ils sont maintenant tous les deux des points de contact secondaires, tandis que le point d'appui principal entre les deux roues est maintenant entre l'extrémité 11 de la dent le de la première roue, et le pied 2 de la dent suivante ld de l'autre roue. Sur la figure 2C, le point d'appui principal est entre le profil convexe 8 de la roue la et le pied 2 de la roue la, tandis qu'il y a deux points de contact secondaires entre les deux roues lb et le, respectivement entre le secteur d'extrémité 11 de la dent le et le pied d'une nouvelle dent ld, et entre les deux secteurs convexes 7 des dents la et le. Sur la figure 2D, le point d'appui principal est entre le secteur convexe 7 de la dent le et le point actif de transition 4 de la dent ld, tandis que la tête de la roue le, roule dans la zone de transition des dents la et ld. Le secteur d'extrémité continue de rouler sur le pied 2 de la dent la, tandis que l'appui principal est entre le point actif de transition 4 de la dent ld et le secteur convexe 7 de la dent le (figure 2E). Enfin, sur la figure 2F, on a retrouvé une situation analogue à la figure 2A, mais cette fois entre les dents le et id. Ces figures mettent en évidence une caractéristique importante de l'invention, selon laquelle le premier point de trαnsition 4 d'une dent roule sur le premier secteur convexe 7 d'une dent de la roue opposée. De même, elles mettent en évidence qu'un même point actif d'une dent est successivement un point d'appui principal et un point de contact secondaire au cours de l'engrenement. Enfin, comme indiqué sur les schémas, les dents des deux roues sont en contact sur plus d'un pas de dent, pendant l'engrenement. La figure 3A montre l'augmentation très importante du volume d'entredent déplacé par rapport à une dent classique en développante de cercle, grâce à l'allongement de la hauteur de la dent et à l'augmentation de l'intervalle entre les dents. La figure 3B est une figure de principe, où l'on peut voir les différentes trajectoires de plusieurs points du profil de dent proposé par l'invention, dans l'entredent du pignon conjugué, avec un effet épicycloïdal allongé prononcé, permettant le fort développement du volume déplacé. En conclusion, il faut souligner que le profil de dent proposé par l'invention a la particularité de combiner des tronçons en développante de cercle dont les avantages sont déjà connus, avec des tronçons de roulement à profil spéciaux. Cette combinaison assure simultanément une continuité d'engrènement et une conduite de denture suffisante et un très fort développement du volume d'huile déplacé. Le profil de dent proposé par l'invention permet en particulier un gain de débit, notamment à faible vitesse, de l'ordre de 30% à 40%, par rapport à une denture de pompe classique à développante de cercle. • fransiiion 9, marking a break-of-court-be. The transition point 9 delimits the bottom of a notch inscribed in the profile of the tooth. According to another characteristic of the invention, the convex sector 7 following the first transition point 4, has an involute profile. This involute profile therefore extends between the two active transition points 4 and 9 of tooth 1, and constitutes a first convex sector of the foot 2. The second convex sector 8, or convex extension profile, which makes further to point 9, can also have a prof in involute of circle, without however that this particular provision is imperative, and one can envisage other extension profiles for this second convex sector, without departing from the scope of the invention. Finally, the head of the tooth has a rounded end sector 11, connected to the second convex sector 8 by a transition sector 12. The tooth is symmetrical, and there is a concordance of shape between the end sector 11 of the teeth. and the concave sector defined by the juxtaposition of two feet 2 of neighboring teeth, so that the end sector of a tooth can roll between two teeth of the opposite wheel, keeping contact with them until what it escapes. Finally, the two gears of the pump can be identical, and this characteristic provides a considerable advantage to the proposed pump, in terms of process and manufacturing costs. Referring to Figures 2A to 2F (Figure 2F corresponding to the same meshing situation as Figure 2A for the following teeth), we see that there are several points of contact between the teeth. In these figures, there is shown with a double circle the so-called main support points by which the driving wheel drives the driven wheel, and with a simple secondary contact points making it possible to take up the play in operation and the continuity of the gear. In FIG. 2A, the tooth 1a of a first wheel has just exceeded the axis of symmetry of the opposite gap. It is in main support (double circle) by its convex surface 8 with the active transition point 4 of the opposite tooth 1b, while its end sector 11, rolls on the concave foot 2 thereof. After a slight relative displacement of the teeth 1a, 1b (FIG. 2B), it can be seen that the two preceding support points have moved, and that they are now both secondary contact points, while the point of main support between the two wheels is now between the end 11 of the tooth le of the first wheel, and the foot 2 of the next tooth ld of the other wheel. In FIG. 2C, the main fulcrum is between the convex profile 8 of the wheel la and the foot 2 of the wheel la, while there are two secondary contact points between the two wheels lb and le, respectively between the end sector 11 of the tooth le and the base of a new tooth ld, and between the two convex sectors 7 of the teeth la and the. In FIG. 2D, the main fulcrum is between the convex sector 7 of the tooth le and the active transition point 4 of the tooth ld, while the head of the wheel le, rolls in the transition region of the teeth la and ld. The end sector continues to roll on the foot 2 of the tooth la, while the main support is between the active transition point 4 of the tooth ld and the convex sector 7 of the tooth le (FIG. 2E). Finally, in FIG. 2F, a situation similar to FIG. 2A has been found, but this time between the teeth le and id. These figures highlight an important characteristic of the invention, according to which the first point of trαnsition 4 of a tooth rolls on the first convex sector 7 of a tooth of the opposite wheel. Likewise, they show that the same active point of a tooth is successively a main fulcrum and a secondary contact point during the meshing. Finally, as shown in the diagrams, the teeth of the two wheels are in contact on more than one tooth pitch, during the gearing. FIG. 3A shows the very significant increase in the volume of the interposed displaced with respect to a conventional tooth developing in a circle, thanks to the lengthening of the height of the tooth and to the increase in the interval between the teeth. FIG. 3B is a figure of principle, where one can see the different trajectories of several points of the tooth profile proposed by the invention, in the intersection of the conjugate pinion, with a pronounced elongated epicyclic effect, allowing strong development of the volume moved. In conclusion, it should be emphasized that the tooth profile proposed by the invention has the particularity of combining sections in the involute of a circle, the advantages of which are already known, with bearing sections with special profiles. This combination simultaneously ensures continuity of engagement and a sufficient toothing line and a very strong development of the volume of oil displaced. The tooth profile proposed by the invention allows in particular a flow gain, in particular at low speed, of the order of 30% to 40%, compared to a conventional pump toothing with involute of a circle.

Claims

REVENDICATIONS
1. Dent d'engrenage (1) présentant un pied concave (2) raccordé à son point de départ au pied de la dent voisine et une tête (3) raccordée audit pied (2) par un premier point de transition (4), caractérisée en ce que la tête de la dent présente deux secteurs convexes (7, 8) raccordés par un second point de transition (9) marquant une rupture de courbe sur le profil de la dent. 1. Gear tooth (1) having a concave foot (2) connected at its starting point to the foot of the neighboring tooth and a head (3) connected to said foot (2) by a first transition point (4), characterized in that the head of the tooth has two convex sectors (7, 8) connected by a second transition point (9) marking a break in the curve on the profile of the tooth.
2. Dent d'engrenage selon la revendication 1, caractérisée en ce que le second point de transition (9) délimite le fond d'une entaille inscrite dans le profil de la dent (1). 2. Gear tooth according to claim 1, characterized in that the second transition point (9) delimits the bottom of a notch inscribed in the profile of the tooth (1).
3. Dent d'engrenage selon la revendication 1 ou 2, caractérisée en ce que le secteur convexe (7) faisant suite au premier point de transition (4) a un profil en développante de cercle. 3. Gear tooth according to claim 1 or 2, characterized in that the convex sector (7) following the first transition point (4) has an involute profile.
4. Dent d'engrenage selon la revendication 1, 2 ou 3, caractérisée en ce que le secteur convexe (8) faisant suite au second point de transition (9), a un profil en développante de cercle. 4. Gear tooth according to claim 1, 2 or 3, characterized in that the convex sector (8) following the second transition point (9), has an involute profile.
5. Dent d'engrenage selon l'une des revendications 1 à 4, caractérisée en ce que la tête de la dent (2) présente un secteur d'extrémité arrondi (11) raccordé au second secteur convexe par une secteur de transition (12) . 5. Gear tooth according to one of claims 1 to 4, characterized in that the head of the tooth (2) has a rounded end sector (11) connected to the second convex sector by a transition sector (12 ).
6. Pompe à engrenages extérieurs comportant au moins une paire de pignons dentés en engrènement mutuel, dont chaque dent est conforme à l'une des revendications précédentes. 6. External gear pump comprising at least one pair of toothed pinions in mutual engagement, each tooth of which conforms to one of the preceding claims.
7. Pompe à engrenages selon la revendication 6, caractérisée en ce que les deux roues dentées sont identiques. 7. Gear pump according to claim 6, characterized in that the two toothed wheels are identical.
8. Pompe à engrenages selon la revendication 6 ou 7, caractérisée en ce que le premier point de transition (4) d'une dent roule sur le premier secteur convexe (7) d'une dent de la roue opposée. 8. Gear pump according to claim 6 or 7, characterized in that the first transition point (4) of a tooth rolls on the first convex sector (7) of a tooth of the opposite wheel.
9. Pompe à engrenages selon la revendication 6, 7 ou 8, caractérisée en ce qu'il y a concordance de forme entre le secteur d'extrémité (11) des dents et le secteur concave défini par la juxtaposition de deux pieds de dents (2) voisines. 9. Gear pump according to claim 6, 7 or 8, characterized in that there is concordance of shape between the end sector (11) of the teeth and the concave sector defined by the juxtaposition of two feet of teeth ( 2) neighbors.
10. Pompe à engrenages selon l'une des revendications 5 à10. Gear pump according to one of claims 5 to
9, caractérisée en ce que le secteur d'extrémité d'une dent (11) roule entre deux dents de la roue opposée en gardant le contact avec celles-ci jusqu'à ce qu'il s'échappe de celles-ci. 9, characterized in that the end sector of a tooth (11) rolls between two teeth of the opposite wheel, keeping contact with them until it escapes from them.
11. Pompe à engrenages selon l'une des revendications 5 à11. Gear pump according to one of claims 5 to
10, caractérisée en ce que les dents en engrènement présentent en permanence au moins un point d'appui principal et un point de contact secondaire, permettant d'assurer le rattrapage des jeux de fonctionnement et la continuité de l'engrenement. 10, characterized in that the meshing teeth permanently have at least one main bearing point and a secondary contact point, making it possible to take up the play in operation and the continuity of the gear.
12. Pompe à engrenages selon la revendication 11, caractérisée en ce que un même point actif d'une dent est successivement un point d'appui principal et un point de contact secondaire au cours de l'engrenement. 12. Gear pump according to claim 11, characterized in that the same active point of a tooth is successively a main fulcrum and a secondary contact point during the gearing.
13. Pompe à engrenages selon l'une des revendications 5 à 12, caractérisée en ce que les dents des deux roues sont en contact sur plus d'un pas. 13. Gear pump according to one of claims 5 to 12, characterized in that the teeth of the two wheels are in contact over more than one pitch.
EP04785984A 2003-08-20 2004-07-21 Gear tooth and external gear pump Expired - Lifetime EP1658437B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0310040A FR2859000B1 (en) 2003-08-20 2003-08-20 GEAR TOOTH AND EXTERNAL GEAR PUMP
PCT/FR2004/001925 WO2005021972A1 (en) 2003-08-20 2004-07-21 Gear tooth and external gear pump

Publications (2)

Publication Number Publication Date
EP1658437A1 true EP1658437A1 (en) 2006-05-24
EP1658437B1 EP1658437B1 (en) 2008-06-25

Family

ID=34112826

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Application Number Title Priority Date Filing Date
EP04785984A Expired - Lifetime EP1658437B1 (en) 2003-08-20 2004-07-21 Gear tooth and external gear pump

Country Status (8)

Country Link
US (1) US8109748B2 (en)
EP (1) EP1658437B1 (en)
JP (1) JP4936888B2 (en)
AT (1) ATE399266T1 (en)
DE (1) DE602004014625D1 (en)
ES (1) ES2305859T3 (en)
FR (1) FR2859000B1 (en)
WO (1) WO2005021972A1 (en)

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Also Published As

Publication number Publication date
EP1658437B1 (en) 2008-06-25
FR2859000B1 (en) 2005-09-30
WO2005021972A1 (en) 2005-03-10
US20070274853A1 (en) 2007-11-29
JP2007502950A (en) 2007-02-15
JP4936888B2 (en) 2012-05-23
US8109748B2 (en) 2012-02-07
FR2859000A1 (en) 2005-02-25
ES2305859T3 (en) 2008-11-01
ATE399266T1 (en) 2008-07-15
DE602004014625D1 (en) 2008-08-07

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