EP1340913B1 - Zahnradmaschine - Google Patents

Zahnradmaschine Download PDF

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Publication number
EP1340913B1
EP1340913B1 EP03003179A EP03003179A EP1340913B1 EP 1340913 B1 EP1340913 B1 EP 1340913B1 EP 03003179 A EP03003179 A EP 03003179A EP 03003179 A EP03003179 A EP 03003179A EP 1340913 B1 EP1340913 B1 EP 1340913B1
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EP
European Patent Office
Prior art keywords
toothing
teeth
tooth
toothed wheel
roots
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.)
Expired - Lifetime
Application number
EP03003179A
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German (de)
English (en)
French (fr)
Other versions
EP1340913A2 (de
EP1340913A3 (de
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
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Publication date
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Publication of EP1340913A2 publication Critical patent/EP1340913A2/de
Publication of EP1340913A3 publication Critical patent/EP1340913A3/de
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Publication of EP1340913B1 publication Critical patent/EP1340913B1/de
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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 comprising a toothed wheel set formed with the gear and finally a gear machine formed with the gear set.
  • the gear machine which is preferably an internal gear machine, it may be a motor or preferably a positive displacement pump.
  • the EP 1 016 784 A1 Although to form the intermeshing toothings of the inner rotor and the outer rotor, in each case as a cycloid toothing with complete epi- and hypocycloids, but the Epicycloids of the teeth of the inner rotor with smaller pitch circles than the epicycloids of the outer rotor and the hypocycloids of the teeth of the outer rotor with smaller pitch circles than the hypocycloids of the teeth of the inner rotor to produce.
  • the backlash is increased in the same way as space is created for pinch oil. Noises are at best reduced at the expense of volumetric efficiency.
  • ring gear pump A proven in practice ring gear pump is used for example in the EP 0 552 443 B1 described.
  • the tooth tips of the inner rotor and the tooth heads of the outer rotor and optionally cooperating with the tooth tips tooth roots of the other rotor to the pitch circle of the respective rotor are flattened out.
  • the intermeshing teeth are formed as Zykloidenvertechnikept, however, they are formed for the purpose of flattening as shortened epicycloids and Hypozykloiden. Since the epicycloids and hypocycloids on the pitch circle no longer abut each other due to the shortening, the transitions are bridged by straight line pieces. At the crossing points, however, discontinuities arise, which in turn cause noise problems. Furthermore, the crushing spaces are still not ideal.
  • the US 2,960,884 has gear teeth of internal gear sets on the subject. Starting from a master toothing, each of which has a circular arc or an elliptical arc shaped tooth heads, the counter toothing is generated by rolling the rolling circles of the two gears of the toothed wheel set.
  • the US 2,389,728 also describes internal-axis gear wheel sets with an external rotor forming the master toothing, whose tooth heads are predetermined as elliptical arcs. Starting from the elliptical tooth heads of the master toothing, the tooth heads and tooth roots of the counter toothing, ie the inner rotor, are generated. By means of the tooth heads of the inner rotor, the toothed feet of the master toothing are generated.
  • the teeth of the gear should be precise, but easy and inexpensive to produce.
  • a gear on a toothing the abutting tooth tips and tooth roots of curves of second or higher order are formed, which point tangentially to each other at their ends.
  • the tooth profile at the transition points between the curves forming the tooth tips and the curves forming the tooth roots is not only continuous but also differentiable.
  • the profile contour of the toothing is continuously differentiable everywhere.
  • at least the curves forming the tooth tips, or at least the curves forming the tooth roots are not cycloids, the term cycloids being used in the sense of
  • a shortened or extended cycloids to be understood.
  • the fact that the profile contour of the tooth tips and / or the tooth roots is not cycloidal means that the curves in question are not based on a smooth rolling of rolling circles on a fixed circle, for example by first forming them as cycloids and then working them off with an offset to get required backlash.
  • the toothing preferably comprises at least four teeth. It preferably extends over the entire inner or outer circumference of the gear.
  • each arc of a curve of a first type forms the tooth tips, namely one elliptical arc or one arc of an ellipse-like curve, and one arc of a curve of another type, the tooth roots, namely one circular arc each.
  • the same curves for the tooth tips and the same curve curves for the tooth roots of the toothing are ever used.
  • a gear has a toothing whose abutting tooth tips and tooth roots are formed by second or higher-order curves, the curves being tangent to one another at their ends, and the curves forming the flanks of the tooth heads forming arcs an ellipse with unequal major axes or arcs of an ellipse-like curve, preferably a cassini curve in its ellipse-like shape.
  • the vertices of the tooth heads may well be flattened and / or the Zahnkopfflanken can be connected to the tooth roots by short straight pieces, it is preferred that the elliptical or elliptical arches not only the flanks of the tooth heads, but also their vertices in a single continuous arc until to form the two connection points with the adjacent tooth feet.
  • the gear according to the second aspect of the invention advantageously further, unless it is contrary to the second aspect of the invention. It is therefore particularly preferred if the gear wheel is a gear wheel according to both aspects of the invention.
  • the ratio of the major axis length to the minor major axis length is preferably at least 1.1 and preferably at most 2.
  • An aspect ratio in the range of 1.25 to 1.6 is particularly preferred.
  • the tooth tips and tooth gaps may have different thicknesses measured on the pitch circle or pitch circle of the toothed wheel, whereby flow pulsations with tooth roots of the gear tooth according to the invention which are wider than those of the tooth roots, but also with tooth heads narrower than those of the tooth roots, can be reduced of the EP 0 552 443 B1 and the EP 1 016 784 A1 already described for other profiles.
  • the conveying flow pulsations are already reduced by the inventive design of the toothing with respect to the known solutions, so that a toothing of tooth tips and tooth roots, which are the same thickness, is already advantageous.
  • the curves forming the tooth tips or tooth tip flanks preferably abut directly against the curves forming the tooth roots so that the tooth profile has a finite curvature throughout.
  • the two curves could also be connected by straight line pieces.
  • each connecting straight would have to extend tangentially the curves adjoining the two straight line ends or tangentially enter these two curves.
  • a curved course is more favorable.
  • the curved arches of the tooth tips and the curved arches of the tooth roots preferably abut each other on the pitch circle of the gear and are nestled there against each other. But it is also possible to move the joints between the tooth head curves and the Zahnfußkurven a small distance from the pitch circle outwards or inwards, not only in the less preferred embodiment, in which the curve ends are connected to each other via straight lines, but also in the preferred embodiment of the immediate abutment.
  • the invention further relates to a gear set, which consists of at least two gears, which are in mesh or can be brought to roll to each other. At least one of the gears has a toothing of the type according to the invention.
  • the counter-toothing of the other gear of the at least two gears is over their entire profile or it is derived in a preferred embodiment only their Zahnfußprofil according to the gearing law kinematically of the inventive teeth. If the gear wheel set forms feed wheels of a toothed ring pump or output gears of a toothed ring motor, a steady rolling and sliding of the tooth flanks and sufficient crushing spaces for the working fluid are obtained between the toothing according to the invention and the counter toothing formed in this way due to the difference in the numbers of teeth of the two meshing toothings. The noise of the Zahnradlaufsatzes is therefore reduced at the same time high volumetric efficiency.
  • only the profile of the tooth roots of the counter toothing according to the toothing law is kinematically derived from the toothing according to the invention, while the profile of the tooth heads of the counter toothing is obtained from Hüllschnitten the tooth tip profile of the toothing according to the invention.
  • the curve of the tooth heads of the counter toothing is the connecting line of points on tooth head curves of the toothing according to the invention.
  • the tooth head curve of the counter toothing envelops the tooth head curves of the toothing according to the invention, which are rotated on the relevant tooth head of the counter toothing.
  • the connecting line of these points forming the tooth head profile of the counter toothing can in particular be a spline function.
  • the at least two, preferably exactly two meshing teeth of the toothed wheel train preferably each have such a tooth profile contour that the rolling edges of the gears rolling against each other form cells sealed against each other.
  • the gear train is an internal-axis flight set and all fluid cells are formed only by the gears, as is preferably the case when the difference in the number of teeth of the gears is one, the tooth tips of the gears are shaped so that at the point of least gear mesh a radially narrow gap remains. Basically, this also applies when using a sickle in innenachsigen gear sets, where the difference in the number of teeth is greater than one.
  • a minimal running play so that on the one hand compensates for manufacturing tolerances, on the other hand, but by the gap resulting losses in the field of least tooth engagement or between the tooth tips and a sickle are minimized.
  • a cavity serving as a compression space for the working fluid of the gear machine is formed according to the invention.
  • the toothing according to the invention of the one toothed wheel is predetermined as the master toothing and the counter toothing is formed on the basis of this specification in such a way that the dense fluid cells and the rolling tooth flanks are formed.
  • the Wälzflanken the counter-toothing as far as the Wälzflanken belong to the Zahnfußkurve are formed by kinematic derivation according to the gearing law.
  • the cavity or crimping space results at the point of the deepest tooth engagement of the teeth by itself.
  • the cavity can also be formed by a respective indentation of the tooth roots of the gear with the toothing according to the invention.
  • the gear with the counter teeth in its tooth roots may each have a recess for the formation of the cavity.
  • the toothing according to the invention can each have a discontinuity in the derivation at the indentations or can also be continuously differentiable at the transitions of the curved arches according to the invention into and out of the indentation.
  • the toothing according to the invention does not have such indentations, so that its tooth profile contour is formed not only on the tooth tips, but also in the tooth roots each by a smooth, continuous curve arc of a curve according to the invention.
  • the counter-toothing can advantageously be obtained by interpolating spline functions on support points.
  • the support points of the tooth root curve are preferably determined by kinematic derivation of the toothing according to the invention according to the toothing law and the tooth head curve, preferably from Hüllitesen the tooth head curve of the master toothing.
  • the envelope cut method is performed with the flattened generation curve.
  • the generating curve is an elliptical arc
  • the envelope sections are determined by means of the elliptical arc.
  • an interpolating spline function is at least grade three, preferably exactly three degrees.
  • the support points can be formed in particular by contact points of the rolling tooth flanks of the gears.
  • the spline functions in a number corresponding to the division of the countertoothing are set to one another, optionally adapted at the transition points, so that at least continuously differentiable transitions are obtained.
  • the counter-toothing as such represents a toothing according to the invention, since its tooth profile is formed by an at least piecewise twice continuously differentiable function.
  • the spline functions are placed in or very close to the vertices in the roots of the teeth where rolling does not occur.
  • only the tooth head profile of the counter toothing is formed by a spline function whose interpolation points are the envelope intersection points, while the tooth root profile of the counter toothing is a polygon, which connects the points of the tooth root profile obtained from the toothing law. From the gearing law, the points of the Zahnfußprofils can be determined so close to each other so easily that a simple polygonal pull is sufficient as a connecting line. For the counter-toothing, this means that alternately a spline function for a tooth tip profile and a polygon traction for the tooth root profile are juxtaposed and each continuously differentiable, i. tangential, merge into each other.
  • a gear wheel of the moving set according to the invention for example the gear with the counter teeth, is preferably provided with a so-called offset after shaping, in that the teeth in question are withdrawn equidistantly over the entire contour over a predetermined distance, as is the case with the tooth profile starting contour formed according to the invention.
  • both gears can be withdrawn equidistant from the starting contour produced according to the invention.
  • a backlash of the intermeshing teeth ie a backlash in the circumferential direction, can be obtained in particular by an equidistant withdrawal of one or both tooth profile contours over the production rule.
  • the intermeshing teeth of their respective production instructions are formed so that they are generated in the circumferential direction to "zero clearance".
  • the tooth head profile of the counter toothing can be flattened relative to one of the production instructions for tooth head profile formed from Hüllitesen, so that the radial backlash is not only formed by an equidistant withdrawal.
  • Preferred uses of a gear pump according to the invention are, for example, a lubricating oil pump of an internal combustion engine or a lubricating oil pump of a transmission of a wind power generator.
  • Figure 1 shows a gerotor pump in a view perpendicular to a gear set, which is rotatably received in a gear chamber of a pump housing 1.
  • a cover of the pump housing is omitted, so that the gear chamber with the gear set is visible.
  • the gerotor pump has an outer rotor 3 with an inner toothing 3i and an inner rotor 4 with an outer toothing 4a, which form the toothed wheel set.
  • the External toothing 4a has one tooth less than the internal toothing 3i.
  • the number of teeth of the internal teeth 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 is parallel spaced, i. eccentrically, to a rotation axis 6 of the inner rotor 4.
  • the eccentricity, i. the distance between the two axes of rotation 5 and 6, is denoted by "e”.
  • the inner rotor 4 and the outer rotor 3 form a fluid delivery space between them.
  • This fluid conveying space is subdivided into conveying cells 7 which are sealed off from each other in a pressure-tight manner.
  • the individual conveyor cells 7 are each formed between two consecutive teeth of the inner rotor 4 and the inner teeth 3i of the outer rotor 3 by having two successive teeth of the inner rotor 4 head or edge contact with two consecutive, opposite teeth of the internal teeth 3i. Between the tooth tips 4k and 3k, a slight clearance may exist at the point of least tooth engagement, wherein the conveyed fluid forms a sealing film between the opposite tooth heads 4k and 3k of the two toothings 4a and 3i.
  • the delivery cells 7 become progressively larger in the direction of rotation D, in order subsequently to decrease again from the location of least tooth engagement.
  • the increasing delivery cells 7 form a low-pressure side in pump operation and the decreasing delivery cells 7 a high-pressure side.
  • the low pressure side is connected to a pump inlet and the high pressure side to a pump outlet.
  • kidney-shaped slot openings 8 and 9 are excluded, which are separated from one another by webs.
  • the opening 8 covers conveyor 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 accordingly forms a high-pressure opening.
  • the housing forms a sealing ridge between the adjacent inflow and outflow openings 8 and 9th
  • the pump receives its rotary drive from a rotary drive member 2, which is formed by a drive shaft.
  • the inner rotor 4 is connected to the rotary drive member 2 against rotation.
  • the pump is usually the drive shaft 2 directly to the crankshaft or the output shaft of a transmission whose input shaft is the crankshaft of the engine.
  • a balance shaft for a force balance or torque compensation of the engine.
  • other rotary drive members are also conceivable, in particular in other uses of the pump, for example as a hydraulic pump for a servo drive of a motor vehicle.
  • the inner rotor 4 instead of driving the inner rotor 4, and the outer rotor 3 could be rotationally driven and take the inner rotor 4 with its rotary motion.
  • Figure 2 shows the profile contours of the teeth 3i and 4a at the point of the deepest tooth engagement.
  • the tooth tips 3k of the internal teeth 3i are ellipsoidal arcs and the tooth roots 3f of the internal teeth 3i are formed as circular arcs.
  • the elliptical arcs and the circular arcs abut against each other on the pitch circle T3 of the internal teeth 3i and are nestled there so that they have the same pitch at each of the immediately formed seams.
  • the left-sided and right-sided derivatives are the same, ie the tooth profile contour of the internal teeth 3i is a everywhere, even at the transition points, continuously differentiable function.
  • the laws for the axes of the ellipse forming the elliptical arcs are derived from the basic toothing data modulus and number of teeth of the outer rotor 3.
  • the internal toothing 3i of the outer rotor 3 is the output toothing or master toothing.
  • the Zalmfußprofilkontur the inner rotor 4 is derived from the tooth head profile contour of the internal teeth 3i kinematically according to the gearing law.
  • the tooth head profile contour of the inner rotor 4 is obtained from envelope sections of the tooth head profile contour of the internal toothing 3i.
  • the profile contour of the outer toothing 4a is formed as a whole by spline functions and polygons which are placed against one another along the pitch circle T4 of the outer toothing 4a. The spline functions are obtained on interpolation points.
  • the toothing law provides the interpolation points for the polygons of the tooth roots 4f
  • the envelope method provides the interpolation points for the spline function of the tooth heads 4k.
  • the support points 10-16 are the instantaneous contact points of the Wälzflanken of the two gears 3i and 4a and form in the snapshot of Figure 1 just the sealing points between the individual fluid cells 7. If the two gears 3 and 4 further rotated by a small angle, a next sentence be obtained from support points. The larger the number of support points is or the closer the support points are adjacent to each other, the more accurately the tooth tips 4k of the external toothing 4a will ever be approximated by the same interpolating spline function.
  • the external toothing 4a may just as well be the master toothing and in this case the internal toothing 3i by spline functions and polygonal pulls or else only by spline functions, namely one for the tooth heads and another for the tooth roots, to be discribed. If the external toothing 4a is the master toothing, its tooth tips 4k are formed as described above for the tooth tips 3k, and their tooth roots 4f are formed as described above for the tooth roots 3f.
  • FIG. 3 shows the point of the deepest tooth engagement for a toothed wheel set, the inner rotor 3 of which has the same internal toothing 3i as the inner rotor 3 of the toothed wheel set of FIGS. 1 and 2.
  • the external toothing 4a is also formed by the same curved arches as the external toothing 4a of the first embodiment, but indentations are formed in the tooth roots 4f, which create additional cavities H2 for the fluid.
  • the toothed feet 4f of the variant of FIG. 3 are identical to the toothed feet 4f of the first exemplary embodiment.
  • the internal toothing 3i has the same tooth heads 3k as the internal toothing 3i of the first exemplary embodiment.
  • the tooth roots 3f are formed by elliptical arcs. These elliptical arcs are each provided with a recess in the region of their vertex. If, due to the tooth roots 3f formed by elliptical arches, a sufficient crimping space is not already created solely because of the difference in the numbers of teeth of the two toothings 3i and 4a, the indentations of the tooth roots 3f can nevertheless each be a cavity H3 of sufficient size be created. In principle, however, it is assumed that the inventive 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 engagement sufficient crushing space is created.
  • FIG. 5 shows the profile contour of a single tooth head 3k of the master toothing 3i.
  • FIG. 6 shows the same tooth head 3k and a tooth root 3f, which tangentially enters the tooth head 3k on the pitch circle T3 of the master toothing 3i.
  • the tangent common at the intersection with the pitch circle T3 is designated P1.
  • P2 the radial of the pitch circle T3 is denoted by the center of the circle, which forms the profile contour of the tooth root 3f.
  • the elliptical arc of the tooth tip 3k is, as shown in FIG. 5, taken from an ellipse with a large semiaxis a and a small semiaxis b.
  • the small semi-axis b is a radial of the pitch circle T3.
  • the large semiaxis a is a tangent to the 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 circle T3.
  • the profile shift determines the ratio of tooth head to tooth root and in particular the curvature of the elliptical arc forming the tooth tips 3k.
  • the constants C1 and C2 can be used either to create the gap between the master gear 3i and the counter gear 4a, or to adjust the curvature of the ellipse, or for both purposes simultaneously. If it is used to create the gap, changing the half-axes a and b by the same amount is advantageous in order to obtain the most even distribution of fissures along the elliptical arc.
  • x1 and y1 are the coordinates of the intersection of the tangent P1 with the pitch circle T3 ( Figure 6).
  • 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 region of the deepest tooth engagement, where the cavity H1 between the profile contours of the tooth root 3f and the tooth head 4k remains for the squeezing fluid.
  • the profile contour of the adjacent tooth root of the counter-toothing 4a is not shown. It is derived according to the gearing law from the elliptical arc of the tooth head 3k of the master gearing 3i.
  • the Hüllitesmethode for generating the profile contour of the tooth tips 4k of the counter teeth 4a is illustrated in Figure 8.
  • the profile contour of the tooth tips 4k is, in the plane of the pitch circle T4, the connecting line which is the envelope intersection points of the tooth head curves 3k, i. the elliptical arches connecting master teeth 3i.
  • Each of the points is the intersection of one of the tooth head curves 3k with a straight line V which connects the center M of the respective ellipse and the intersection C of the radial with the pitch circle T4.
  • the respective radial through the intersection point C has the same distance on the pitch circle T4 to the two adjacent tooth roots 4f.
  • the center M of the ellipse is the intersection of the ellipse axes a and b.
  • the envelope intersection points are obtained by rotation of tooth head curves of the master toothing 3i about the pitch circle axis 6 of the counter toothing 4a, the tooth head curves 3k of the master toothing 3i each being rotated on the same tooth of the counter toothing 4a.
  • the master toothing 3i is known. Also known is the position of the Wälznikachse 6 of the counter toothing 4a relative to the master teeth 3i. Further, the number of teeth of the counter teeth 4a is known, so that one can position a star of radials starting from the pitch circle axis 6 of the counter teeth 4a to the vertices of the tooth heads 4k to be generated relative to the master teeth 3i.
  • the tooth head curves 3k of the toothing according to the invention are rotated about the rolling circle axis 6 of the counter toothing 4a into one of the radials.
  • a set of tooth head curves of the master toothing 3i enveloping the tooth head curve 4k to be generated for example the tooth head curves 3k 1 to 3k 5 of FIG Tooth curves 3k 1 to 3k 5 may be the tooth head curves with the points of contact 11 to 15 from the snapshot of Figure 1.
  • This procedure is repeated for different relative positions of the two gears 3i and 4a, wherein the Wälznikachsen 5 and 6, of course, maintain their positions.
  • the master gear 3i is rotated about the pitch circle axis 6 of the counter teeth 4a so that the respective radial of the counter teeth 4a are always brought into coincidence with the same, once defined radials.
  • FIG. 9 shows by way of example how the cavity H1 can be reduced by flattening the tooth-root curve 3f of the master toothing in order to reduce the dead volume.
  • the profile contour of the toothed feet 3f is flattened in the apex region in comparison with the circular arc suitably selected for the elliptical arc of the tooth tips 3k.
  • the flattening is shown by dashed lines.

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

Applications Claiming Priority (2)

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

Publications (3)

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

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EP03003179A Expired - Lifetime EP1340913B1 (de) 2002-02-27 2003-02-19 Zahnradmaschine

Country Status (6)

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

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012113768A1 (de) 2011-02-22 2012-08-30 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Verfahren zur erzeugung der zahnform von innen- und aussenring einer zahnringmaschine sowie damit erzeugter zahnring
CN104662331A (zh) * 2012-09-21 2015-05-27 恩普乐股份有限公司 齿轮及其制造方法

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Publication number Priority date Publication date Assignee Title
US7472677B2 (en) * 2005-08-18 2009-01-06 Concept Solutions, Inc. Energy transfer machine
CN101243241A (zh) * 2005-08-18 2008-08-13 詹姆斯B.·克莱森 能量转换机器
CN101832264B (zh) * 2005-09-22 2011-12-28 爱信精机株式会社 油泵转子
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DE102006015521B3 (de) * 2006-03-31 2007-04-12 ThyssenKrupp Präzisionsschmiede GmbH Verzahnung eines evolventisch wälzverzahnten Zahnrades
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CN104662331B (zh) * 2012-09-21 2018-12-14 恩普乐股份有限公司 齿轮

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DE50308093D1 (de) 2007-10-18
EP1340913A2 (de) 2003-09-03
DE10208408A1 (de) 2003-09-11
US20040009085A1 (en) 2004-01-15
JP2003254409A (ja) 2003-09-10
ATE372462T1 (de) 2007-09-15
EP1340913A3 (de) 2004-07-28
ES2292867T3 (es) 2008-03-16
US7427192B2 (en) 2008-09-23
JP4155841B2 (ja) 2008-09-24

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