EP3384159B1 - Pompe à engrenages extérieurs - Google Patents

Pompe à engrenages extérieurs Download PDF

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Publication number
EP3384159B1
EP3384159B1 EP16805286.8A EP16805286A EP3384159B1 EP 3384159 B1 EP3384159 B1 EP 3384159B1 EP 16805286 A EP16805286 A EP 16805286A EP 3384159 B1 EP3384159 B1 EP 3384159B1
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EP
European Patent Office
Prior art keywords
gear
pump
tooth flank
external gear
axial direction
Prior art date
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Active
Application number
EP16805286.8A
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German (de)
English (en)
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EP3384159A1 (fr
Inventor
Simon OCHSENKUEHN
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Audi AG
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Audi AG
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Publication of EP3384159A1 publication Critical patent/EP3384159A1/fr
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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
    • F04C2/12—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
    • F04C2/20—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 dissimilar tooth forms
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses
    • 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

Definitions

  • the invention relates to an external gear pump with a driving first feed gear as well as with a second feed gear driven by the first feed gear, which mesh with one another to convey a fluid from a suction side to a pressure side of the external gear pump, the first feed gear and the second feed gear each having a plurality of teeth have a leading tooth flank running in the direction of rotation of the corresponding conveyor gear and a trailing trailing tooth flank, the leading tooth flank of the first conveying gear cooperating with the trailing tooth flank of the second conveying gear to drive the second conveying gear through the first conveying gear.
  • the external gear pump is used to convey the fluid from its suction side to the pressure side.
  • the fluid or its physical state can be selected as desired, but it is preferably liquid under normal operating conditions of the external gear pump.
  • the external gear pump has several delivery gears, namely the first delivery gear and the second delivery gear.
  • the first conveyor gear is preferably driven directly.
  • the second conveying gear is driven indirectly by the drive shaft, namely via the first conveying gear.
  • the two gears each have a large number of teeth which, depending on the angle of rotation of the conveying gears, mesh with one another and interact to convey the fluid from the suction side to the pressure side.
  • Each tooth of the conveyor gears has via the leading tooth flank and the trailing tooth flank, with the leading tooth flank lying at the front in the direction of rotation of the respective conveyor gear, i.e. limiting the tooth forwards or in the direction of rotation, while the trailing tooth flank is at the rear in the direction of rotation, and therefore limits the tooth to the rear or counter to the direction of rotation. If the first conveying gear is driven, the leading tooth flank of at least one tooth of the first conveying gear comes into abutment contact with the trailing tooth flank of a tooth of the second conveying gear. As a result, the second conveying gear is driven by the first conveying gear.
  • the gear pump includes a driving gear and a driven gear.
  • the driving gear has symmetrical teeth
  • the driven gear has asymmetrical teeth.
  • the asymmetrical teeth of the driven gear include working surfaces which have a profile which corresponds to the profile of the working and non-working surfaces of the driving gear, but they have a non-working surface which is substantially exposed so that it is substantially flat .
  • the driving gear and the driven gear have non-contact surfaces, which are essentially flat in order to form an even larger dead space and to prevent cavitation when the teeth are made wider in the axial direction.
  • US3981646A discloses an external gear pump according to the preamble of claim 1.
  • WO2014 / 199202A1 and US1686867A disclose external gear pumps wherein the teeth include fluid pockets.
  • the object of the invention is to propose an external gear pump which has advantages over known external gear pumps, in particular enables a greater pressure ratio between outlet pressure and inlet pressure and / or has a greatly reduced tendency to cavitation, so that undesirable acoustic noise is avoided during its operation.
  • the trailing tooth flanks of the first conveying gear or the trailing tooth flanks of the teeth of the first conveying gear, in particular all teeth of the first conveying gear, have a special design. There is a fluid pocket in each of the trailing tooth flanks. This results from the fact that the corresponding trailing tooth flank is concave at least in some areas, that is to say has a curvature engaging the corresponding tooth in the circumferential direction.
  • the trailing tooth flank is curved in cross section with respect to an axis of rotation of the first conveying gear in the direction of the leading tooth flank delimiting the same tooth as the trailing tooth flank, so that the fluid pocket engages the tooth.
  • the trailing tooth flank is curved in the direction of an engaging flank of the tooth. The bulge lies in radial direction before, so in a cross section through the first conveyor gear.
  • the fluid pocket is in the at least one axial position. According to the invention, the fluid pocket only partially passes through the first conveyor gear or the trailing tooth flank in the axial direction, that is, at least on one side in the axial direction, it is closed to the edge in the first conveying gear or its trailing tooth flank.
  • the first conveying gear and the second conveying gear have the same toothing parameters.
  • the toothing parameters are, for example, the root diameter, the pitch diameter, the tip diameter, the gear pitch, the head height, the root height, the tooth width, the pitch, the number of teeth and / or the module.
  • the conveyor gears or their teeth are preferably designed in such a way that at least one of these toothing parameters, preferably several of the toothing parameters or all of the toothing parameters, match.
  • the teeth of the conveyor gears can in principle have any type of toothing which, however, is the same for the two conveyor gears. For example, an involute toothing, a cycloid toothing or a circular arc toothing can be used as the type of toothing.
  • the external gear pump runs significantly more smoothly and therefore more quietly than known external gear pumps.
  • a higher pressure or a higher pressure ratio between outlet pressure and inlet pressure can be achieved with the external gear pump according to the invention.
  • the inlet pressure is on the suction side and the outlet pressure is on the pressure side.
  • the higher pressure or the greater pressure ratio results in a very high degree of efficiency, in particular a higher degree of efficiency than in the case of an external gear pump in which the trailing tooth flanks do not run concave to form the fluid pockets.
  • the higher pressure or the greater pressure ratio is achieved in particular in the area of constant delivery of the external gear pump, in which the pressure, namely the outlet pressure, or the pressure ratio is proportional to the speed of the external gear pump or the first delivery gear.
  • the proportionality between the pressure or the pressure ratio on the one hand and the speed on the other hand is given in particular at speeds of the external gear pump in a certain speed range, which is limited upwards by a governing speed of the external gear pump.
  • the cut-off speed is the speed from which the two conveyor gears are shifted against each other in the axial direction in order to reduce their overlap.
  • the conveyor gears are in a first relative position to one another until the limiting speed is reached, in which their overlap is constant and / or maximum.
  • the further the speed exceeds the limiting speed the further the two gears are deflected from the first relative position in the direction of a second relative position in which the Coverage is smaller than in the first relative position, in particular is minimal.
  • the speed range can be limited downwards by a minimum speed of the external gear pump.
  • the minimum speed corresponds, for example, to an idling speed of a drive unit of a drive device, the external gear pump being part of the drive device and, for example, serving to convey a fluid for the drive unit.
  • the external gear pump is preferably designed as a lubricant pump or the like. Accordingly, the invention is of course also directed to a drive device, in particular for a motor vehicle, which has a drive unit, for example an internal combustion engine, and an external gear pump, in particular according to this description. A fluid conveyed by the external gear pump is fed to the drive unit by means of the external gear pump, the fluid being, for example, a lubricant or the like.
  • the external gear pump can of course be developed in accordance with the statements made in this description.
  • a preferred development of the invention provides that the teeth of the first conveyor gear are designed symmetrically. This is to be understood in particular as the fact that, viewed in cross section, the trailing tooth flank is designed symmetrically to the leading tooth flank, so that the tooth having the leading tooth flank and the trailing tooth flank is symmetrical with respect to a longitudinal center plane.
  • the trailing tooth flanks of the first feed gear are designed with the fluid pocket.
  • the second conveying gear has unchanged teeth throughout, in particular without fluid pockets.
  • the fluid pocket in the respective trailing tooth flank of the first conveying gearwheel is formed with an open edge at least on one side, in particular only on one side. It was already pointed out above that the fluid pocket preferably only partially extends through the first conveying gear or the trailing tooth flank in the axial direction. Accordingly, viewed in the axial direction, for example, it is open-edged on only one side.
  • an embodiment of the external gear pump can also be implemented in which the fluid pocket extends completely through the first delivery gear or the trailing tooth flank in the axial direction, so that the fluid pocket is open on both sides when viewed in the axial direction.
  • a further development of the invention provides that the trailing tooth flanks of the first conveyor gear wheel, viewed in the axial direction, each have a fluid pocket area receiving the fluid pocket and a contact area directly adjacent to the fluid pocket area, the trailing tooth flanks running convex in the contact area, in particular symmetrically to the respective leading tooth flanks of the corresponding Teeth are.
  • the fluid pocket only partially extends through the first feed gear in the axial direction.
  • the fluid pocket is in the fluid pocket area of the trailing tooth flank. This is followed by the contact area, seen in the axial direction, so that for example the fluid pocket is limited in the axial direction by the contact area of the trailing tooth flank.
  • the contact area preferably forms a wall delimiting the fluid pocket, which wall lies in a plane perpendicular to the axis of rotation or only encloses a small angle therewith.
  • the low angle can for example be a maximum of 20 °, a maximum of 15 °, a maximum of 10 °, a maximum of 5 °, a maximum of 2.5 ° or a maximum of 1 °.
  • the trailing tooth flanks run convexly in contrast to the fluid pocket area, that is to say they are curved outward in the circumferential direction, that is to say away from the respective leading tooth flank of the corresponding tooth.
  • the trailing tooth flank of each of the teeth viewed in cross section, runs symmetrically to the corresponding leading tooth flank of the tooth.
  • the cross-section of the trailing tooth flank in particular of the entire tooth of the first conveying gear wheel having the trailing tooth flank, is continuously the same in the axial direction in the area of the fluid pocket, that is to say in the fluid pocket area. This can additionally or alternatively also apply to the contact area.
  • first conveyor gear and the second conveyor gear can be displaced against each other in the axial direction with respect to an axis of rotation of one of the conveyor gears in order to set a certain overlap, the dimensions of the contact area being selected in the axial direction such that the Contact area is present in each position of the two conveying gears to one another in the axial direction in overlap with the second conveying gear.
  • the delivery volume flow or the delivery mass flow of the external gear pump can be adjusted.
  • the delivery volume flow is greater, the greater the overlap between the two delivery gears in the axial direction.
  • the first conveying gear is fixed in the axial direction and therefore only rotatable is stored, for example in a pump housing of the external gear pump.
  • the second feed gear is rotatably mounted and displaceable in the axial direction, preferably likewise in the pump housing.
  • the displacement of the two conveying gears can, however, be limited in such a way that they are always at least partially overlapping with one another, that is to say do not disengage in any position of the conveying gears.
  • the contact area can be designed or its dimensions selected in such a way that, regardless of the position of the feed gear wheels with respect to one another, the contact area, viewed in the axial direction, is always in overlap with the second feed gear wheel.
  • the second conveying gear viewed in longitudinal section, overlaps the contact area by at least 25%, at least 50%, at least 75% or at least 100%.
  • the second conveying gearwheel preferably ends flush with the contact area - again viewed in longitudinal section - when the smallest possible overlap is present.
  • a further preferred embodiment of the invention provides that a tooth flank wall area of the respective trailing tooth flank of the first conveyor gear wheel, which delimits the fluid pocket, starts directly from a tooth root circle, in particular runs out tangentially from it.
  • the tooth flank wall area is that area of the trailing tooth flank which delimits the fluid pocket in the circumferential direction.
  • the tooth root circle lies in each case between two teeth of the first conveyor gear in front of or limits the teeth in the radial direction inward.
  • the tooth root circle is circular or in the shape of a segment of a circle and lies over the entire circumference of the first conveyor gear on the root circle diameter, at least in sections.
  • the fluid pocket now preferably begins directly at the tooth root circle, that is to say, viewed in cross section, at the root circle diameter of the first conveyor gear wheel.
  • the tooth flank region runs tangentially into the tooth root circle or starts tangentially from it.
  • the teeth of the first conveying gear each have a head region in which the trailing tooth flank is convex, in particular is designed symmetrically to the corresponding leading tooth flank.
  • the concave course of the trailing tooth flank does not necessarily have to be provided over its entire extent in the radial direction. Rather, the concave course can only extend over part of the trailing tooth flank in the radial direction.
  • the teeth of the first conveyor gear each have a head region at which the concave profile of the respective trailing tooth flank ends.
  • the trailing tooth flank is preferably convex, that is to say is outward in the circumferential direction or curved away from the leading tooth flank belonging to the same tooth.
  • the trailing tooth flank is designed symmetrically to the leading tooth flank of the same tooth. This enables a high delivery volume flow or a high delivery pressure of the external gear pump, the delivery pressure being understood as the difference between a pressure on the pressure side and a pressure on the suction side.
  • the dimensions of the head area in the radial direction based on the difference between the tip circle radius and the root circle radius of the teeth of the first conveyor gearwheel are at least 5%, at least 10%, at least 15%, at least 20%, at least 25%, be at least 30%, at least 35% or at least 40%.
  • the dimensions of the head area are between the tip circle of the first conveying gear and the side of the fluid pocket lying on the outside in the radial direction.
  • the dimensions of the head area correspond to the tip circle radius of the first conveying gear minus the greatest extent of the fluid pocket in the radial direction, again seen in cross section. If the dimensions of the head area are now related to the difference between the tip circle radius and the root circle radius, then the values mentioned above preferably result.
  • the tooth flank wall area is in the shape of a circular arc when viewed in cross section. Seen in cross section, this is the case at least in certain areas, but preferably over the entire extent of the fluid pocket.
  • the circular arc-shaped configuration of the tooth flank wall area which, viewed in cross section, delimits the fluid pocket in the circumferential direction, results in an extremely robust embodiment of the external gear pump.
  • the tooth flank wall area adjoins the head area via a chamfer or a rounding.
  • the transition between the tooth flank wall area and the head area is - seen in cross section - so not abrupt. Rather, seen again in cross section, the chamfer or the rounding between the tooth flank area and the head area are provided in order to achieve a high level of strength of the external gear pump.
  • the rounding can be chosen as desired, for example it has a radius which, based on the dimensions of the head area, is at least 10%, at least 5%, at least 2.5%, at least 1%, at least 0.5%, at least 0.25 % or at least 0.1%.
  • the chamfer or the rounding are preferably part of the fluid pocket.
  • the Figure 1 shows part of an external gear pump 1, namely a first feed gear 2 and a second feed gear 3.
  • the first feed gear 2 is designed as a driving feed gear, so it can be driven directly.
  • the second conveying gear 3 can only be driven indirectly via the first conveying gear 2.
  • a forward direction of rotation of the first conveyor gear wheel 2 is indicated by the arrow 4.
  • the first conveying gear wheel 2 has teeth 5, while the second conveying gear wheel 3 has teeth 6, only a few of which are identified by way of example.
  • the feed gears 2 and 3 or their teeth 5 and 6 mesh with one another so that when the feed gears 2 and 3 rotate in the direction of arrow 4, a fluid is conveyed from a suction side 7 to a pressure side 8 of the external gear pump 1.
  • Each of the teeth 5 has a leading tooth flank 9 leading in the direction of rotation and a trailing trailing tooth flank 10. This is only indicated for one of the teeth 5.
  • each tooth 6 of the second conveying gear 3 has a leading tooth flank 11 in the direction of rotation and a trailing trailing tooth flank 12. If the rotary movement of the first conveying gear 2 is in the direction of the arrow 4, then the leading tooth flank 9 of one of the teeth 5 acts with the trailing tooth flank 12 one of the teeth 6 together in order to drive the second conveying gear 3 through the first conveying gear 2 and convey the fluid from the suction side 7 to the pressure side 8.
  • both feed gears 2 and 3 are rotatably mounted, for example in a pump housing not shown here External gear pump 1, they can also be displaced relative to one another in the axial direction, for example with respect to an axis of rotation 13 of the first delivery gear 2 or an axis of rotation 14 of the second delivery gear 3.
  • the first conveying gear wheel 2 is preferably arranged fixedly in the axial direction, while the second conveying gear wheel 3 can be displaced in the axial direction. This is indicated by the double arrow 15.
  • the conveyor gears 2 and 3 preferably have the same dimensions in the axial direction. Of course, however, different dimensions can also be implemented.
  • the trailing tooth flanks 10 of the first conveyor gear wheel 2 run concave in the radial direction, at least in regions, to form a fluid pocket 16 in each case.
  • Such a configuration can significantly reduce the tendency of the external gear pump 1 to cavitation, which has a positive effect on the noise behavior.
  • the Figure 2 shows the area of the external gear pump 1, ie the two feed gears 2 and 3, in a second axial position of FIG Conveyor gears 2 and 3 against each other.
  • the conveying gears 2 and 3 are, however, arranged in such a way that they do not disengage from one another in any position. Rather, the teeth 5 and 6 should be in engagement with one another in every possible position of the conveyor gears 2 and 3.
  • the fluid pocket 16 or the fluid pockets 16 only partially penetrate the teeth 5 in the axial direction, that is to say they are designed with an open edge in the axial direction only on one side.
  • the trailing tooth flanks 10 each have a fluid pocket area 17 and a contact area 18. While the trailing tooth flank 10 is concave in the radial direction at least in some areas in the fluid pocket area 17, the trailing tooth flank 10 is at least partially convex in the contact area 18, i.e. curved in the direction facing away from the respective leading tooth flank 9. For example, in the contact area 18, the trailing tooth flank 10 is formed symmetrically to the leading tooth flank 9.
  • the dimensions of the contact area 18 in the axial direction are selected in such a way that the contact area 18 is also in overlap with the second conveyor gear 3 in the position of the two conveying gears 2 and 3 with respect to one another shown here, in which there is minimal overlap.
  • the contact area 18 should therefore be present in overlap with the second conveyor gear 3 in every position of the conveyor gears 2 and 3 with respect to one another.
  • the game can be zero.
  • it is greater than zero and is, for example, based on one of the axes of rotation 7 and 13, at most 0.1 °, at most 0.25 °, at most 0.5 °, at most 0.75 °, at most 1 °, at most 2.5 ° or at most 5 °. It can also be between two of the values mentioned, for example at least 0.25 ° and at most 0.75 °.
  • the Figure 3 shows a cross-sectional view of the first conveying gear 2. It can be seen that the fluid pocket 16 is delimited in the circumferential direction by a tooth flank edge region 19.
  • the tooth flank wall region 19 is preferably circular arc-shaped when viewed in cross section.
  • the tooth flank wall area 19 preferably extends from a tooth root circle 20, which is present between two teeth 5 of the conveying gear wheel 2, to a head area 21 of the respective tooth 5.
  • the tooth root circle 20 has a root circle diameter d f .
  • a tip diameter is indicated as d k in the exemplary embodiment shown here.
  • the tooth height h is composed of a pocket height h t and a head area height h k of the head area 21. This in turn results in the fluid pocket 16 directly adjoining the tooth root circle 20 in the radial direction.
  • the fluid pocket 16 or the tooth flank wall region 19 delimiting the fluid pocket 16 particularly preferably starts directly from the tooth root circle 20. It preferably runs out of this tangentially.
  • the tooth flank wall region 19 can be in the form of a circular arc, seen in cross section, in particular over its entire extent or at least a large part of its extent in the radial direction, in particular over at least 50%, at least 75%, at least 80%, at least 85%, at least 90% or at least 100%.
  • the tooth flank wall region 19 runs out into the head region 21 or merges into it.
  • the transition can be made, for example, via a rounding 22 in order to achieve a high degree of strength of the first conveyor gear wheel 2.
  • the dimensions h k of the head region 21 are at least 5% based on half the difference between the tip circle diameter d k and the root circle diameter d f , but can also be larger. It can be clearly seen here once again that the fluid pocket 16 is only formed with an open edge on one side in the first conveying gear wheel 2. Seen on one side in the axial direction, it is delimited by a wall 23 formed by the contact area 18.
  • the Figure 4 14 shows a detailed representation of an area of the first conveying gear 2.
  • the rounding 22 can be clearly seen, via which the tooth flank wall area 19 merges into the head area 21.
  • the rounding 22 can be part of the tooth flank wall area 19 or of the head area 21.
  • the embodiment of the external gear pump 1 presented here has an extremely low tendency to cavitation, because fluid forced into the fluid pocket 16 can at least partially get out of it in the axial direction. At the same time, however, the ability of the external gear pump 1 to rotate back and a constant play in the circumferential direction, regardless of the overlap, are ensured by the presence of the contact area 18.

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

Claims (8)

  1. Pompe à roue dentée extérieure (1), avec une première roue dentée de transport (2) d'entraînement et une seconde roue dentée de transport (3) entraînée par la première roue dentée de transport (2), qui s'engrènent l'une dans l'autre pour transporter un fluide d'un côté aspiration (8) à un côté pression (7) de la pompe à roue dentée extérieure (1), dans laquelle la première roue dentée de transport (2) et la seconde roue dentée de transport (3) présentent chacune plusieurs dents (5, 6), chacune avec un flanc de dent avant (9, 11) menant dans le sens de rotation de la roue dentée de transport correspondante (2, 3) et un flanc de dent arrière (10, 12) en arrière, dans laquelle le flanc de dent avant (9, 11) de la première roue dentée de transport (2) coopère avec le flanc de dent arrière (10, 12) de la seconde roue dentée de transport (3) pour entraîner la seconde roue dentée de transport (3) par la première roue dentée de transport (2), dans laquelle les flancs de dent arrière (10, 12) de la première roue dentée de transport (2) s'étendent au moins partiellement concaves dans la direction radiale pour former chacun une poche à fluide (16) dans au moins une position axiale, dans laquelle la poche à fluide (16) est formée dans le flanc de dent arrière (10) respectif de la première roue dentée de transport (2) avec un bord ouvert seulement sur un côté vu dans la direction axiale, caractérisée en ce que les dents (6) de la seconde roue dentée de transport (3) sont conçues symétriquement et la poche à fluide (16) présente une section transversale continuellement identique dans la direction axiale.
  2. Pompe à roue dentée extérieure selon la revendication 1, caractérisée en ce que les flancs de dents arrière (10) de la première roue dentée de transport (2), vus dans la direction axiale, présentent chacun une zone de poche à fluide (17) recevant la poche à fluide (16) et une zone de contact (18) directement adjacente à la zone de poche à fluide (17), dans laquelle les flancs de dents arrière (10) s'étendent de manière convexe dans la zone de contact (18), en particulier sont symétriques par rapport aux flancs de dents avant (9) respectifs des dents correspondantes (5).
  3. Pompe à roue dentée extérieure selon l'une quelconque des revendications précédentes, caractérisée en ce que la première roue dentée de transport (2) et la seconde roue dentée de transport (3) sont déplaçables dans la direction axiale par rapport à un axe de rotation (13, 14) de l'une des roues dentées de transport (2, 3) l'une par rapport à l'autre pour régler un certain chevauchement, dans laquelle les dimensions de la zone de contact (18) dans la direction axiale sont sélectionnées de sorte que la zone de contact (18) se trouve en chevauchement avec la seconde roue dentée de transport (3) dans la direction axiale dans chaque position des deux roues dentées de transport (2, 3) l'une par rapport à l'autre.
  4. Pompe à roue dentée extérieure selon l'une quelconque des revendications précédentes, caractérisée en ce qu'une zone de paroi de flanc de dent (19) délimitant la poche à fluide (16) s'étend directement du flanc de dent arrière (10) respectif de la première roue dentée de transport (2) à partir d'un cercle de pied de dent (20), en particulier en sort tangentiellement.
  5. Pompe à roue dentée extérieure selon l'une quelconque des revendications précédentes, caractérisée en ce que les dents (5) de la première roue dentée de transport (2) présentent chacune une zone de tête (21), dans laquelle le flanc de dent arrière (10) est convexe, en particulier est formé symétriquement par rapport au flanc de dent avant (9) correspondant.
  6. Pompe à roue dentée extérieure selon l'une quelconque des revendications précédentes, caractérisée en ce que les dimensions de la zone de tête (21) dans la direction radiale, basées sur la différence entre le rayon du cercle de tête et le rayon du cercle de pied des dents (5) de la première roue dentée de transport (2), sont d'au moins 5 %, d'au moins 10 %, d'au moins 15 %, d'au moins 20 %, d'au moins 25 %, d'au moins 30 %, d'au moins 35 % ou d'au moins 40 %.
  7. Pompe à roue dentée extérieure selon l'une quelconque des revendications précédentes, caractérisée en ce que la zone de paroi de flanc de dent (19) est en forme d'arc de cercle vue en section transversale.
  8. Pompe à roue dentée extérieure selon l'une quelconque des revendications précédentes, caractérisée en ce que la zone de paroi de flanc de dent (19) se raccorde à la zone de tête (21) par un chanfrein ou un arrondi (22).
EP16805286.8A 2015-12-04 2016-11-28 Pompe à engrenages extérieurs Active EP3384159B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015015752 2015-12-04
PCT/EP2016/002007 WO2017092862A1 (fr) 2015-12-04 2016-11-28 Pompe à engrenages extérieurs

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CN109322821B (zh) * 2018-10-09 2023-07-04 宿迁学院 一种用于消除齿轮泵径向力的组合结构
CN109268258B (zh) * 2018-10-09 2023-07-07 宿迁学院 一种外啮合齿轮泵的//形卸荷槽
CN110748483B (zh) * 2019-08-20 2024-09-17 神钢无锡压缩机股份有限公司 一种螺杆压缩机主机降噪结构
CN114427532B (zh) * 2022-01-27 2024-02-23 张义山 一种泵用降噪转子机构

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CN108291537A (zh) 2018-07-17
DE102016014175A1 (de) 2017-06-08
US10989190B2 (en) 2021-04-27
EP3384159A1 (fr) 2018-10-10
WO2017092862A1 (fr) 2017-06-08
CN108291537B (zh) 2020-10-09
US20180347561A1 (en) 2018-12-06

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