EP1340913A2 - Pompe à engrenages - Google Patents

Pompe à engrenages Download PDF

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Publication number
EP1340913A2
EP1340913A2 EP03003179A EP03003179A EP1340913A2 EP 1340913 A2 EP1340913 A2 EP 1340913A2 EP 03003179 A EP03003179 A EP 03003179A EP 03003179 A EP03003179 A EP 03003179A EP 1340913 A2 EP1340913 A2 EP 1340913A2
Authority
EP
European Patent Office
Prior art keywords
tooth
toothing
gear
curves
feet
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
EP03003179A
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German (de)
English (en)
Other versions
EP1340913A3 (fr
EP1340913B1 (fr
Inventor
Christof Dr. Lamparski
Sven Peters
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.)
Schwaebische Huettenwerke Automotive GmbH
Original Assignee
Schwaebische Huettenwerke Automotive GmbH
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.)
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Publication date
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Publication of EP1340913A2 publication Critical patent/EP1340913A2/fr
Publication of EP1340913A3 publication Critical patent/EP1340913A3/fr
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Publication of EP1340913B1 publication Critical patent/EP1340913B1/fr
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
    • F04C2/088—Elements in the toothed wheels or the carter for relieving the pressure of fluid imprisoned in the zones of engagement
    • 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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes

Definitions

  • the invention relates to a toothing of a gear, further one with the gear formed gear set and finally one formed with the gear set Gear machine.
  • gear machine which is preferably an internal axis Gear machine, it can be a motor or preferably a Act positive displacement pump.
  • Gerotor pumps with a gear wheel set consisting of a are known externally toothed inner rotor and an internally toothed outer rotor, which together in a meshing tooth mesh.
  • Form the toothing of the two rotors rotating, expanding and compressing delivery cells for a working fluid.
  • the for Formation of the intermeshing toothing cells have epi and / or Hypocycloids or trochoids formed tooth tips and tooth feet. If alternating, for example, one of the two toothed teeth is formed by epicycloids and hypocycloids, one results from kinematic Derivation according to the gearing law also produces counter gearing as Interlocking of alternating epicycloids and hypocycloids.
  • both theoretical tooth profiles thus obtained cannot roll on each other and would due to the deepest meshing in the area complete coverage of the base of the tooth base and the top of the tooth head cannot be controlled Cause noise problems due to pinch oil effects.
  • EP 1 016 784 A1 proposes that together intermeshing toothings of the inner rotor and the outer rotor each as To form cycloid interlocking with complete epi- and hypocycloids, but the Epicycloids of internal rotor teeth with smaller pitch circles than that Epicycloids of the outer rotor and the hypocycloids of the teeth of the outer rotor with smaller rolling circles than the hypocycloids of the teeth of the inner rotor produce.
  • the backlash is increased in the same way as space for squeeze oil. Noises are at the expense of the volumetric Efficiency reduced.
  • a gerotor pump that has been tried and tested in practice is described, for example, in EP 0 552 443 B1 described.
  • the intermeshing gears are designed as cycloid gears, however, for the purpose of flattening, they are shortened epicycloids and Hypocycloids formed. Because the epicycloids and hypocycloids on the pitch circle because of the Shortening no longer meet seamlessly, the transitions are through Line pieces bridged. However, discontinuities occur at the transition points in turn cause noise problems. Furthermore, the squeeze rooms are still not ideal.
  • a gear has a toothing, the abutting tooth heads and tooth bases of curves of second or higher order are formed that point tangentially towards each other at their ends.
  • the tooth profile at the transition points between the curves forming the tooth heads and the curves forming the tooth bases are not only continuous, but also differentiable.
  • the profile contour of the toothing can preferably be continuously differentiated everywhere.
  • the curves that form the tooth tips, or at least the curves that form the Form tooth bases, no cycloids whereby the term cycloid in the sense of Invention can also be understood as a shortened or elongated cycloid (trochoid) should.
  • That the profile contour of the tooth tips and / or the tooth feet is not cycloid means that the curves in question are not on a non-slip rolling of Rolling circles are based on a fixed circle, for example by initially acting as a cycloid shaped and then processed with an offset to a required Get tooth play.
  • the toothing preferably comprises at least four teeth. It extends preferentially over the entire inner or outer circumference of the gear.
  • the one according to the invention Form toothing in such a way that the tooth tips of cycloids and the tooth feet of each are formed by a curve of at least second order, preferably one Curve of a conic section, in particular an arc of a circle or an ellipse or an arc of an ellipse-like curve that is tangent to the ends of the curve neighboring cycloid arches point so that there are no kinks at the transitions arise.
  • the tooth heads of the counter toothing can be made of cycloids and the tooth feet are preferably also each formed by a curve of at least second order. Between the curves and the engaging cycloids of the two gears would advantageous pinch oil spaces are formed.
  • a toothing formed from cycloids and non-cycloids preferably the tooth bases from the non-cycloid curves of the second or higher order educated.
  • the tooth tips of non-cycloid curves can also second or higher order and the tooth feet are formed cycloid.
  • both the tooth heads and the tooth feet are not from Cycloids formed, neither by epi- and hypcycloids nor by shortened or elongated epi- or hypocycloids.
  • the tooth tips and are particularly preferred Nodules are also not formed by other curves that are created with the help of rolling circles that roll smoothly on the pitch or pitch circle of the gear.
  • the profile contour of the tooth heads is a conical arc. Even more preferred is the profile contour of the tooth feet, one curve curve each Conic section, i.e. a circular arc, elliptical arch, hyperbolic arch or a parabolic arch.
  • ellipse-like curves for example, a Cassini curve in its elliptical shape, which is also the Profile contour of the tooth tips and / or the tooth feet can form.
  • a Cassini curve in its elliptical shape
  • An aspect ratio ranging from 1.25 to 1.6 particularly preferred.
  • the tooth heads and the tooth feet are each formed by elliptical arcs, but the curved arcs of Tooth tips of a different ellipse than the curve arcs of the tooth feet are taken.
  • an arc of a curve of a first type forms the tooth heads, preferably each an ellipse arc or an arc of an ellipse-like curve, and each an arc of a curve of a different type, the tooth feet, preferably an arc each.
  • the same curve arcs for the tooth tips and each same curve curves are used for the tooth feet of the toothing.
  • a gear has a toothing, the abutting tooth heads and tooth bases of curves of second or higher order are formed, the curves pointing tangentially to one another at their ends and the curves that form the flanks of the tooth tips, arcs of an ellipse with uneven ones Main axes or arcs of an ellipse-like curve, preferably a Cassini curve in their elliptical shape.
  • the crowns of the tooth heads are quite flattened and / or the tooth flanks with the tooth feet through short straight sections connected, it is preferred if the elliptical or ellipse-like Arches not only the flanks of the tooth tips, but also their apices in one single continuous curve up to the two connection points with the form adjacent tooth feet.
  • a feature specific to the first aspect of the invention is described, such a feature also forms the gear according to the second aspect the invention further advantageous, unless it is contrary to the second aspect of Invention stands. It is therefore particularly preferred if the gear wheel follows a gear wheel is both aspects of the invention.
  • the tooth heads and tooth gaps on the pitch circle or pitch circle of the Gear measured have different thicknesses, with flow pulsations with in comparison to the tooth bases of wider tooth heads of the gear according to the invention, but can also be reduced with tooth heads that are narrower than the tooth feet can, as in EP 0 552 443 B1 and EP 1 016 784 A1 for other profiles has already been described.
  • the flow pulsations are already caused by the Training the toothing according to the invention compared to the known solutions diminished, so that a toothing of tooth heads and tooth feet that are the same thickness are already advantageous.
  • the curves that form the tooth tips or tooth tip flanks preferably meet directly to the curves that form the tooth bases, so that the tooth profile is everywhere has finite curvature.
  • the two curves could also be connected by straight lines. Indeed in such an embodiment of the toothing, every connecting straight line that is connected to the Extend the curves following the ends of the straight line tangentially or into these two Enter curves tangentially. There is one everywhere for the sliding movement of the tooth flanks curved course, however, cheaper.
  • the curved curves of the tooth tips and the curved curves of the tooth feet preferably meet on the pitch circle of the gear wheel and are nestled there. It is but also possible, the joints between the tooth tip curves and the tooth root curves to move a little bit from the pitch circle outwards or inwards and not only in the less preferred version, in which the curve ends are over straight sections are interconnected, but also in the preferred embodiment of the immediate clash.
  • the invention further relates to a gear wheel set consisting of at least two gear wheels exists, which are in mesh or can be brought to roll against each other. At least one of the gears has teeth of the type according to the invention.
  • the counter toothing of the other gear of the at least two gears is above it entire profile or it will be preferred only your tooth base profile after the Gearing law kinematically derived from the gearing according to the invention.
  • the noise of the Gear wheel set is therefore combined with high volumetric efficiency reduced.
  • the profile of the tooth feet Counter toothing according to the toothing law kinematically from the invention Gearing derived, while the profile of the tooth heads of the counter gearing Envelope cuts of the tooth profile of the toothing according to the invention is obtained.
  • the curve of the tooth heads of the counter-toothing is the connecting line of points Tooth curve of the toothing according to the invention.
  • the tooth tip curve of the Counter toothing envelops the tooth tooth of the counter toothing concerned turned tooth tip curves of the toothing according to the invention.
  • the the Tooth profile of the counter toothing connecting line of these points can especially a spline function.
  • the profile of the tooth feet flatten the gearing according to the invention, i.e. the tooth feet in their respective Bring the vertex area closer to the pitch circle of the gear.
  • the result of this resulting deviation from, for example, the exact circular arc shape or the otherwise selected tooth root curve is preferably such that the tooth root curve nevertheless continuous, particularly preferably at least piecewise twice continuously, differentiable is.
  • the at least two, preferably exactly two, meshing Gear teeth of the gear wheel set preferably each have such a tooth profile contour, that the rolling tooth flanks of the gears sealed against each other Form cells.
  • the gear wheel set is an internal axis set and all fluid cells only be formed by the toothing, as is preferably the case when the Difference in the number of teeth of the gears is one, so the tooth heads are the Gears shaped in such a way that at the point of minimal tooth engagement a radially narrow one Gap remains. Basically, this also applies when using a sickle internal-axis gear sets where the difference in the number of teeth is greater than one is.
  • the Gearing of a gear according to the invention is specified as a master gearing and the counter-toothing is designed based on this specification so that the tight Fluid cells and the rolling flanks are formed.
  • the rolling flanks of the Counter teeth are by Kinematic derivation based on the gearing law.
  • Forming the tooth bases of the toothing according to the invention as circular arcs results the cavity or squeeze space at the point of the deepest meshing of the Gearing by itself.
  • the cavity can also be made with an indentation of the tooth feet of the gearwheel gearing according to the invention are formed.
  • the gear with Counter-toothing in his tooth feet each has an indentation to form the Have cavity.
  • the toothing according to the invention can be used for the indentations each have a discontinuity in the derivation or also at the transitions of the curve curves according to the invention in and out of the indentation be continuously differentiable.
  • the toothing according to the invention preferably does not have such indentations so that their tooth profile contour not only on the tooth heads, but also in the Tooth feet each by a smooth, continuous curve of an inventive Curve is formed.
  • the counter toothing can advantageously be based on interpolating spline functions Support points can be obtained.
  • the support points of the tooth root curve are preferred by kinematic derivation of the gearing according to the invention Gearing law and that of the tooth tip curve preferably from envelope cuts Tooth curve of the master toothing determined. If the tooth tips of the Master gear teeth are flattened compared to their generation curve, that is Envelope cutting process, however, carried out with the generation curve not flattened. If for example, if the generation curve is an ellipse, the envelope cuts determined by means of the ellipse arc.
  • An interpolating spline function is preferred at least grade three, preferably grade three.
  • the support points can in particular formed by contact points of the rolling tooth flanks of the gear wheels become.
  • the spline functions in one corresponding to the pitch of the counter toothing The number are put together, if necessary adjusted at the transition points, that at least continuously differentiable transitions are obtained.
  • Counter toothing as such represents a toothing according to the invention, since its tooth profile is formed by a function that is continuously differentiable at least twice in parts.
  • the spline functions are preferred at or very close to the vertices in the Put the feet together where there is no rolling.
  • the tooth tip profile of the counter toothing is used formed by a spline function, whose support points are the envelope intersection points, while the tooth root profile of the counter-toothing is a polygon that consists of the Gearing law connects points of the tooth base profile obtained. From the Interlocking law can easily make the points of the tooth root profile so tight can be determined side by side that a simple polyline as a connecting line enough. For the counter toothing, this means that an alternating spline function for a tooth profile and a polygon for the tooth profile are put together and continuously differentiable, i.e. tangential, merge.
  • a gear of the moving set according to the invention for example the gear with the Counter-toothing, preferably after the shaping with a so-called offset provided by the toothing in question normal to their formed according to the invention Tooth profile exit contour equidistant over the entire contour of a given piece is withdrawn far.
  • both gears can also be equidistant be withdrawn compared to the initial contour generated according to the invention.
  • Backlash of the meshing teeth i.e. a backlash in Circumferential direction, can in particular be achieved by an equidistant withdrawal from receive one or both tooth profile contours compared to the generation specification become.
  • the intermeshing Gears formed according to their respective generation regulations so that they are in Circumferential direction on "zero clearance" are generated. Because of the preferred generation of the Tooth curve of the counter toothing from envelope cuts of the tooth profile of the This also applies to master teeth for the required radial play of the teeth the point of least tooth mesh. To the required radial tooth play, i.e. the It can do that to maintain a tooth play in the area of the smallest tooth mesh Tooth profile of the counter-toothing in relation to one of the generation instructions from Envelope cuts formed tooth tip profile be flattened, so that the radial tooth play is not only formed by an equidistant withdrawal.
  • Preferred uses of a gear pump according to the invention are, for example that of a lubricating oil pump of an internal combustion engine or a lubricating oil pump of a Gearbox of a wind power generator.
  • FIG. 1 shows a gerotor pump in a view perpendicular to a gear wheel set, which is rotatably received in a gear chamber of a pump housing 1. On Cover of the pump housing is omitted, so that the gear chamber with the Gear wheel set is recognizable.
  • the gerotor pump has an outer rotor 3 with an internal toothing 3i and one Inner rotor 4 with an external toothing 4a, which form the gear wheel set.
  • the External toothing 4a has one tooth less than the internal toothing 3i.
  • the number of teeth the internal toothing of such internal-axis pumps is at least four and preferably at most fifteen, preferably the number of teeth is between five and ten; in the exemplary embodiment, the internal toothing 3i has nine teeth.
  • An axis of rotation 5 of the outer rotor 3 runs parallel spaced, i.e. eccentric, too an axis of rotation 6 of the inner rotor 4.
  • the eccentricity i.e. the distance between the two axes of rotation 5 and 6, is designated by "e”.
  • the inner rotor 4 and the outer rotor 3 form a fluid delivery space between them.
  • This Fluid delivery chamber is divided into delivery cells 7 which are sealed off from one another in a pressure-tight manner.
  • the individual conveyor cells 7 are each between two successive teeth of the inner rotor 4 and the internal toothing 3i of the outer rotor 3 formed by two successive teeth of the inner rotor 4 head or flank contact with two each have successive, opposite teeth of the internal toothing 3i. Between the tooth heads 4k and 3k there can be a slight tooth mesh at the point there is little play, with the fluid being pumped between each other opposite tooth heads 4k and 3k of the two toothings 4a and 3i one Sealing film forms.
  • the growing conveyor cells 7 form in pump operation a low pressure side and the shrinking delivery cells 7 one High pressure side.
  • the low pressure side is with a pump inlet and the High pressure side connected to a pump outlet.
  • In the housing 1 are in the side Area of the feed cells 7 closely adjacent, kidney-shaped slot openings 8 and 9 except that are separated from one another by webs.
  • the opening 8 covers Delivery cells 7 on the low pressure side and accordingly forms an inflow opening, in pump operation, a low pressure opening, and the other opening 9 forms accordingly a high pressure opening. In an engine operation with such a Gear machine is also possible, the situation would of course be reversed.
  • the housing forms a sealing web between the adjacent inlet and Drain openings 8 and 9.
  • the pump receives its rotary drive from a rotary drive member 2, which by a Drive shaft is formed.
  • the inner rotor 4 is connected to the rotary drive member 2 non-rotatably connected.
  • the drive shaft 2 usually directly to the crankshaft or the output shaft of a gearbox, the input shaft of which is the crankshaft of the engine.
  • a balance shaft for a force balance or Torque compensation of the motor can by a balance shaft for a force balance or Torque compensation of the motor are formed.
  • Other rotary drive members are however also conceivable, especially in other uses of the pump, for example as a hydraulic pump for a servo drive of a motor vehicle.
  • the outer rotor 3 could also be driven in rotation and at take the inner rotor 4 with it when it rotates.
  • Figure 2 shows the profile contours of the teeth 3i and 4a at the point of the deepest Tooth engagement.
  • the tooth heads 3k of the internal toothing 3i are elliptical arcs and Tooth feet 3f of the internal toothing 3i are designed as circular arcs.
  • the ellipse arches and the arcs meet directly on the pitch circle T3 of the internal toothing 3i to each other and are nestled there so that they are so direct to each of the formed seams have the same slope.
  • the left-hand and right-hand derivatives are therefore the same for both curves, i.e. the tooth profile contour of the internal toothing 3i is everywhere, even on the Transition points, continuously differentiable function.
  • the laws of the axes of the ellipse forming the ellipse arcs are from the basic gear data module and Number of teeth of the outer rotor 3 derived.
  • the internal toothing 3i of the outer rotor 3 is Output gear or master gear.
  • the Zalm foot profile contour of the inner rotor 4 is kinematically based on the tooth profile profile contour of the internal toothing 3i Gear Act derived.
  • the tooth tip profile contour of the inner rotor 4 is made Obtain envelope cuts of the tooth profile profile contour of the internal toothing 3i.
  • the profile contour the external toothing 4a is in total by spline functions and polygon formed, which are placed along the pitch circle T4 of the external toothing 4a. The spline functions are obtained at support points.
  • the gearing law provides the support points for the polygons of the tooth feet 4f
  • the envelope cut method provides the support points for the spline function of the tooth tips 4k.
  • the snapshot of FIG. 1 shows the support points 10-16 for the tooth heads 4k.
  • the support points 10 to 16 are the current contact points of the rolling flanks of the two Gears 3i and 4a and in the snapshot of FIG. 1 form just that Sealing points between the individual fluid cells 7.
  • the external toothing 4a be the master toothing and in this case the Internal gearing 3i through spline functions and polygons or just through Spline functions, namely one for the tooth tips and another for the tooth feet, to be discribed. If the external toothing 4a is the master toothing, their Tooth tips 4k are formed as described above for the tooth tips 3k, and there are their tooth bases 4f are formed as described above for the tooth bases 3f.
  • the area of deepest tooth engagement is shown enlarged in FIG. Clear to see is a cavity H1, which is in the area of the vertices between the straight in deepest tooth engagement tooth head 4k of the inner rotor 4 and the receiving Tooth root 3f of the outer rotor 3 results.
  • Aspect ratios up to 6: 5 or even 10: 9 are however also still beneficial.
  • the two toothings 4a and 3i combine the noise advantages of one Gerotors with the volumetric advantages of a gear wheel set like the one from EP 0 552 443 B1 is known.
  • Figure 3 shows the location of the deepest meshing for a gear set
  • the Inner rotor 3 has the same internal toothing 3i as the inner rotor 3 of the gear wheel set of Figures 1 and 2.
  • the external toothing 4a is also the same Curved curves are formed like the external toothing 4a of the first exemplary embodiment, however, indentations are formed in the tooth bases 4f, which provide additional cavities Create H2 for the fluid.
  • the tooth bases 4f are the Variant of Figure 3, however, identical to the tooth feet 4f of the first Embodiment.
  • the internal toothing 3i has the same tooth heads 3k as the internal toothing 3i of the first embodiment.
  • the tooth feet 3f however formed by elliptical arches. These elliptical arches are in the range of theirs Provide an indentation in the apex. If because of the elliptical arches formed tooth feet 3f at the location of the deepest tooth engagement a sufficient Squeeze chamber not just because of the difference in the number of teeth between the two Toothings 3i and 4a can be created by the indentations of the tooth feet 3f nevertheless, a cavity H3 of sufficient size can be created. Basically, however, it is assumed that the inventive predetermined toothing, in the exemplary embodiment the internal toothing 3i, and the Counter-toothing formed according to the invention already without indentations at the point of the deepest tooth mesh sufficient squeeze space is created.
  • FIG. 5 shows the profile contour of an individual tooth head 3k of the master toothing 3i.
  • Figure 6 shows the same tooth head 3k and a tooth base 3f, which is on the pitch circle T3 the master toothing 3i runs tangentially into the tooth head 3k.
  • P1 is the intersection with Tangent common to pitch circle T3.
  • P2 is the radial of the Pitch circle T3 designated by the center of the circle that the profile contour of Tooth base 3f forms.
  • the ellipse arc of the tooth head 3k is an ellipse with a large semiaxis a and a small semiaxis b taken.
  • the small semi-axis b is a radial of the pitch circle T3.
  • the large semiaxis a is a tangent to the pitch circle T3.
  • the arc of the ellipse located within the pitch circle T3 forms the profile contour of the tooth head 3k. It ends on the pitch circle T3.
  • the profile shift determines the ratio of the tooth head to the tooth base and in particular the curvature of the ellipse arch forming the tooth heads 3k.
  • the constants C1 and C2 can either be used to create the gap between the Master toothing 3i and the counter toothing 4a are used or for adjustment the curvature of the ellipse or for both purposes at the same time. If they are for generation of the gap is used, the semiaxes a and b are changed by the same Amount advantageous in order to be as uniform as possible along the ellipse arc Maintain gap spread.
  • FIG. 7 shows the profile contour of FIG. 6 together with the profile contour of a tooth head 4k of the counter toothing 4a in the area of the deepest tooth engagement, where for squeezing fluid Cavity H1 between the profile contours of the tooth base 3f and the tooth head 4k remains.
  • the profile contour of the adjacent tooth base of the counter toothing 4a is not located. According to the gearing law, it is created from the ellipse of the Tooth head 3k derived from the master toothing 3i.
  • the envelope cut method for generating the profile contour of the tooth tips 4k Counter toothing 4a is illustrated in FIG. 8.
  • the profile contour of the tooth tips 4k is in the plane of the pitch circle T4 the connecting line that the envelope intersection of the Tooth tip curves 3k, i.e. the elliptical arches, the master teeth 3i with each other combines.
  • Each of the points is the intersection of one of the tooth tip curves 3k with one Straight line V, which is the center point M of the respective ellipse and the intersection point C of the Radials connects with the pitch circle T4.
  • the relevant radial through the intersection C has the same on the pitch circle T4 to the tooth bases 4f adjacent on both sides Distance on.
  • intersection point of the ellipse axes a and b understood.
  • intersection point C pitch point
  • Touch points are obtained in sufficient numbers that serve as support points for the profile contour of the tooth tips 4k to be generated.
  • the envelope intersection points are obtained by rotating tooth tip curves of the master toothing 3i about the pitch circle axis 6 of the counter toothing 4a, the tooth tip curves 3k of the master toothing 3i each being rotated onto the same tooth of the counter toothing 4a.
  • the master toothing 3i is known.
  • the position of the pitch circle axis 6 of the counter toothing 4a relative to the master toothing 3i is also known.
  • the number of teeth of the counter toothing 4a is known, so that one can position a star from radial starting from the pitch circle axis 6 of the counter toothing 4a to the apexes of the tooth heads 4k to be produced relative to the master toothing 3i.
  • the tooth tip curves 3k of the toothing according to the invention are then rotated about the pitch circle axis 6 of the counter toothing 4a into one of the radial lines.
  • a set of tooth tip curves of the master toothing 3i is obtained which envelop the tooth tip curve 4k to be generated, for example the tooth tip curves 3k 1 to 3k 5 of FIG. 8
  • Tooth curve 3k 1 to 3k 5 can be the tooth curve with the contact points 11 to 15 from the snapshot of Figure 1.
  • This procedure is repeated for different relative positions of the two toothings 3i and 4a, the pitch circle axes 5 and 6 of course maintaining their positions.
  • the master toothing 3i is rotated about the pitch circle axis 6 of the counter toothing 4a in such a way that the respective radials of the counter toothing 4a are always overlapped with the same, once defined radial.
  • the pitch circle diameter and the tip circle diameter of the counter toothing 4a are also given.
  • the following applies to the diameter of the pitch circle T4: d 4 m 4 * Z 4 .
  • FIG. 9 shows an example of how the cavity H1 is flattened by the tooth root curve 3f the master toothing can be reduced to reduce the dead volume.
  • the profile contour of the tooth feet 3f compared to the Ellipse arc of the tooth heads 3k suitably chosen circular arc in the apex area flattened.
  • the flattening is shown in dashed lines.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Gears, Cams (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Gear Transmission (AREA)
EP03003179A 2002-02-27 2003-02-19 Pompe à engrenages Expired - Lifetime EP1340913B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10208408A DE10208408A1 (de) 2002-02-27 2002-02-27 Zahnradverzahnung
DE10208408 2002-02-27

Publications (3)

Publication Number Publication Date
EP1340913A2 true EP1340913A2 (fr) 2003-09-03
EP1340913A3 EP1340913A3 (fr) 2004-07-28
EP1340913B1 EP1340913B1 (fr) 2007-09-05

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Family Applications (1)

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EP03003179A Expired - Lifetime EP1340913B1 (fr) 2002-02-27 2003-02-19 Pompe à engrenages

Country Status (6)

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US (1) US7427192B2 (fr)
EP (1) EP1340913B1 (fr)
JP (1) JP4155841B2 (fr)
AT (1) ATE372462T1 (fr)
DE (2) DE10208408A1 (fr)
ES (1) ES2292867T3 (fr)

Cited By (2)

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EP2123914A4 (fr) * 2007-03-09 2012-06-27 Aisin Seiki Rotor de pompe à huile
WO2012113768A1 (fr) * 2011-02-22 2012-08-30 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Procédé de génération de la forme de dent de la roue dentée intérieure et de la roue dentée extérieure d'une machine à roues dentées, et roue dentée produite par ce procédé

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US7472677B2 (en) * 2005-08-18 2009-01-06 Concept Solutions, Inc. Energy transfer machine
JP2009504978A (ja) * 2005-08-18 2009-02-05 コンセプト ソリューションズ インコーポレイテッド エネルギ伝達機
EP1927752B1 (fr) 2005-09-22 2018-09-12 Aisin Seiki Kabushiki Kaisha Rotor de pompe à huile
JP4675809B2 (ja) * 2006-03-28 2011-04-27 株式会社ダイヤメット 内接型ギヤポンプロータおよび内接型ギヤポンプ
DE102006015521B3 (de) * 2006-03-31 2007-04-12 ThyssenKrupp Präzisionsschmiede GmbH Verzahnung eines evolventisch wälzverzahnten Zahnrades
WO2011140358A2 (fr) 2010-05-05 2011-11-10 Ener-G-Rotors, Inc. Dispositif de transfert d'énergie de fluide
JP2012219978A (ja) * 2011-04-13 2012-11-12 Asmo Co Ltd 減速機及び歯車ポンプ
US8714951B2 (en) * 2011-08-05 2014-05-06 Ener-G-Rotors, Inc. Fluid energy transfer device
KR101270892B1 (ko) * 2011-11-01 2013-06-05 명화공업주식회사 사이클로이드 기어 펌프
JP5886601B2 (ja) * 2011-11-08 2016-03-16 株式会社山田製作所 ポンプロータ
JP5859816B2 (ja) * 2011-11-08 2016-02-16 株式会社山田製作所 内接歯車式ポンプ
JP6267458B2 (ja) * 2012-09-21 2018-01-24 株式会社エンプラス 歯車
CN104662331B (zh) * 2012-09-21 2018-12-14 恩普乐股份有限公司 齿轮
WO2014046090A1 (fr) * 2012-09-21 2014-03-27 株式会社エンプラス Engrenage et son procédé de production
JP6077373B2 (ja) * 2013-04-11 2017-02-08 豊興工業株式会社 内接歯車ポンプ
JP6306322B2 (ja) * 2013-11-11 2018-04-04 豊興工業株式会社 内接歯車ポンプ
EP3205880B1 (fr) * 2014-10-09 2022-07-27 Toyooki Kogyo Co., Ltd. Pompe à engrenages intérieurs
JP6068580B2 (ja) * 2015-08-03 2017-01-25 株式会社山田製作所 ポンプロータ
DE102018103723B4 (de) 2018-02-20 2025-08-21 Nidec Gpm Gmbh Verzahnung für eine Gerotorpumpe und Verfahren zur geometrischen Bestimmung derselben
US11761377B2 (en) 2022-02-02 2023-09-19 1159718 B.C. Ltd. Energy transfer machine

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2123914A4 (fr) * 2007-03-09 2012-06-27 Aisin Seiki Rotor de pompe à huile
WO2012113768A1 (fr) * 2011-02-22 2012-08-30 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Procédé de génération de la forme de dent de la roue dentée intérieure et de la roue dentée extérieure d'une machine à roues dentées, et roue dentée produite par ce procédé
US9273687B2 (en) 2011-02-22 2016-03-01 Nidec Gpm Gmbh Method for producing the tooth shape of the inner and outer ring of an annular gear machine and toothed ring produced by means of said method

Also Published As

Publication number Publication date
ATE372462T1 (de) 2007-09-15
EP1340913A3 (fr) 2004-07-28
US7427192B2 (en) 2008-09-23
EP1340913B1 (fr) 2007-09-05
DE10208408A1 (de) 2003-09-11
JP2003254409A (ja) 2003-09-10
US20040009085A1 (en) 2004-01-15
JP4155841B2 (ja) 2008-09-24
DE50308093D1 (de) 2007-10-18
ES2292867T3 (es) 2008-03-16

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