EP1180217B1 - Toothed rotor set - Google Patents

Toothed rotor set Download PDF

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Publication number
EP1180217B1
EP1180217B1 EP20000941957 EP00941957A EP1180217B1 EP 1180217 B1 EP1180217 B1 EP 1180217B1 EP 20000941957 EP20000941957 EP 20000941957 EP 00941957 A EP00941957 A EP 00941957A EP 1180217 B1 EP1180217 B1 EP 1180217B1
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EP
European Patent Office
Prior art keywords
tooth
rotor
set
toothed
teeth
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EP20000941957
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German (de)
French (fr)
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EP1180217A1 (en
Inventor
Josef Bachmann
Harald Neubert
Eberhard Ernst
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GKN Sinter Metals GmbH and Co KG
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GKN Sinter Metals GmbH and Co KG
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Priority to DE1999122792 priority Critical patent/DE19922792A1/en
Priority to DE19922792 priority
Application filed by GKN Sinter Metals GmbH and Co KG filed Critical GKN Sinter Metals GmbH and Co KG
Priority to PCT/EP2000/004474 priority patent/WO2000070228A1/en
Publication of EP1180217A1 publication Critical patent/EP1180217A1/en
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Publication of EP1180217B1 publication Critical patent/EP1180217B1/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10Rotary-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

Abstract

The invention relates to a toothed rotor set for a pump, especially for a lubricating oil pump for internal combustion engines, wherein the toothed rotor set has a toothed configuration similar to a toothed ring pump and functioning and operation of said toothed rotor set corresponds to that of a toothed ring pump.

Description

  • The invention relates to a toothed rotor set for a pump, in particular for a lubricating oil pump for internal combustion engines. The toothed rotor is similar to a toothed ring pump with a toothed design, wherein the function and operation of a toothed rotor set, which corresponds to a gerotor pump.
  • In gerotor pumps, the pressure chamber is not separated from the suction chamber by a crescent-shaped filler, but a special design of the teeth - based on the trochoid toothing - ensures the seal between the toothed ring and externally toothed pinion. The internally toothed ring has one more tooth than the pinion, so that with appropriate design of the teeth, the tooth heads touch exactly opposite the tooth engagement point. In order to ensure unwinding, there must be head play between the tooth head of the outer rotor and the tooth head of the inner rotor. The disadvantage of gerotor pumps is that internal leakage and thus poor volumetric efficiency occurs through this head clearance in the gerotor pumps. As a result, high pressures can not be built up at low speeds.
  • More advantageous compared to gerotor pumps is a pump according to the teaching of DE-A-196 46 359 , The pump forms a generic Zahnahnungsrotorsatz consisting of an outer ring with an internal toothing and a gear externally recorded therein with external teeth, wherein the internal toothing is formed by rollers rotatably mounted in the outer ring and a tooth more than the outer toothing, wherein the outer toothing of the gear fine teeth superimposed with a much smaller module and each roller on its perimeter with a fine toothing has the same module, in which engage the teeth of the gear.
  • The function of the toothed rotor set results from the fact that a drive torque acts on the inner rotor via a drive shaft and rotates the latter. From the toothed inner rotor, a force is transmitted to the planetary gear, on the one hand results in an impact force through the center of the planetary gear and a circumferential force, which causes a torque of the planetary gear. The impact force acting on the bearing ring causes it to rotate.
  • The occurring forces and moments can not be optimally absorbed by the previously used involute toothing in the generic Zahnahnungsrotorsatz. In particular, there is the problem that the known toothing does not transmit the impact and peripheral forces without large surface pressure in the form of a line contact. The previously known gears are only suitable for the transmission of high circumferential forces and not for the transmission of large impact forces that pass through the center of the planetary gear.
  • A disadvantage of the generic type Zahnahnungsrotorsatz proves that not under all operating conditions a clean rolling is ensured without interference interference. The movement of the planet gears relative to the bearing comes to a halt in one position.
  • In this state, in which the planetary gear almost stops and at the same time a large force is transmitted, there is a risk that the lubricating film between the planetary gear head and outer rotor collapses, whereby the Couetteströmung comes to a standstill. This creates solid state contact by the loss of the lubricant in the gap. There is thus no longer a favorable hydrodynamic lubrication but it creates mixed friction conditions and in the worst case stiction. In the case of mixed and static friction wear occurs and the service life of the gear rotor set decreases.
  • From the US-A-5 595 479 a hydraulic machine is known, which is formed of a rotatable bearing ring with bearing pockets, wherein in the bearing pockets rotatably mounted rollers are arranged with recesses on the peripheral surface, with an eccentrically mounted to the bearing ring inner rotor with approximately star-shaped outer contour, wherein the teeth of the star in the Recesses of the rollers engage. The rollers and the inner rotor do not have the fine toothing according to the invention, as a result of which engagement errors occur, in particular in gear tooth sets with a higher number of teeth, for example 11/12. The design can only be run with very small tolerances.
  • From the disadvantages of the known prior art, the task results to form a Verzahnungsrotorsatz, which is designed so that a permanent lubricating film construction to avoid adverse frictional conditions is ensured, the Verzahnungsrotorsatz must transmit the forces and moments occurring safely.
  • The object is achieved by a Verzahnungsrotorsatz consisting of a rotatable bearing ring with bearing pockets in which rotatably mounted planetary rotors are arranged, which form an internal toothing, with an eccentrically mounted to the bearing ring inner rotor with approximately star-shaped outer contour, which is provided with an outer toothing the external toothing has one tooth less than the internal toothing and the toothing of at least one of the two rotor systems has an arcuate component at least in partial regions of the tooth form of the toothing. The advantage of such a designed Zahnahnungsrotorsatzes is that due to the arcuate portion of the tooth shape substantially rolling friction and no sliding friction occurs, so that the wear on the teeth is minimized. Due to the convex tooth head of the toothed inner rotor and the concave tooth root of the toothed planetary rotor, there is a contact surface and not to a contact line. The Hertzian pressure is greatly reduced by this Wälzpaarung.
  • This also applies to the tooth flanks of the toothed inner rotor and the toothed planetary gear. By including a backlash between the tooth of the planetary rotor and the tooth gap of the inner rotor ensures that the large impact forces are transmitted only over the tooth head and tooth root. This prevents that act on the tooth flanks large wedge forces that can lead to the destruction of the flank surfaces. In addition, by the backlash the fluid drain from the tooth gaps, otherwise it comes to squeezing oil, which can lead to very high pressure build-up.
  • In an advantageous embodiment of the invention it is provided that in the region of the tooth tip and / or the tooth root, the tooth shape is arcuate. Such a design of the tooth shape in the region of the tooth head and / or the tooth root makes it possible for very large impact forces (radial forces) to be transmitted, it being possible for the proportion of peripheral force to be transmitted to be small. In this case, the tooth head and the tooth root, in contrast to the involute toothings known in the case of toothed rotors, are introduced into the rolling process, i. the rolling of the toothed planetary rotors on the toothed inner rotor curve, with included.
  • The convexly curved tooth flank of the planetary rotor and the concavely curved tooth flank of the inner rotor form a relatively large sealing surface during tooth engagement, which seals the displacement chamber from the suction region into the pressure region when the displacement chamber passes. Even deviations of the squareness of the rotor do not lead to leakage of the displacement chamber.
  • In an advantageous embodiment of the invention it is provided that in particular the region of the tooth tip and / or the tooth root has the tooth shape a flattening. In the main zone of the power transmission, in which the torque acts through the toothed inner rotor via the toothed planetary rotor on the bearing ring, it comes, geometrically caused, almost to a stop of the planetary gear. In the described relative standstill and the simultaneous transmission of a large force there is a risk that the lubricating film between the planetary gear head and bearing ring collapses. To counteract this, the planetary rotor tooth heads were flattened. The size of the flattening depends on the field of application of the toothed rotor. At low speeds and high pressures, a strong flattening is necessary. At high speeds and low pressures, less flattening is necessary to to ensure a lubricating film structure even at low sliding speeds. For the transition from the tooth tip of the planetary rotor to the flattening, a special curve, a cycloid, was used, which promotes the lubricating film structure more than a simple transition radius.
  • In a further advantageous embodiment of the invention it is provided that in particular the region of the tooth tip and / or the tooth root has the tooth shape a large radius of curvature. Instead of a flattening, it is also expedient to provide a surface with a large radius of curvature in the region of the tooth tip and / or tooth root.
  • The flattening of the planetary rotor tooth heads also causes an improvement in the transmission of power (Hertzian pressure) from the planetary rotor to the bearing ring.
  • In a particularly advantageous embodiment of the invention it is provided that the arcuate portion is at least partially formed as a cycloid. The cycloid has proven to be particularly advantageous in terms of roll-off and transfer of impact forces. This cycloid toothing ensures perfect sliding low rolling, even with considerable changes in curvature and small radii of curvature, which in turn reduces wear.
  • In an advantageous embodiment of the invention it is provided that at least in the region of the tooth flanks, the tooth form is formed as involute. In this toothing, the tooth flanks of the toothed inner rotor and the toothed planetary rotor are formed by an involute, but in this embodiment, engagement errors may occur more easily than in an embodiment whose tooth flanks are formed as cycloids.
  • In an advantageous embodiment of the invention, it is provided that the toothing has a low-wear surface. The low-wear surface can be replaced by a chemical, in particular thermochemical and / or physical surface treatment can be achieved. The surface can also be galvanized. Further advantageous surface treatment methods are caburation and nitration and / or nitrocarburizing, boriding and / or chromating.
  • In an advantageous embodiment of the invention it is provided that at least one fluid channel is arranged in the region of the bearing pockets. The fluid channel may be connected to the pressure side of the pump so that lubricating oil is continuously supplied between the planetary rotor and the bearing pocket in order to ensure an improved lubricating film structure.
  • Advantageously, all movable parts of the toothed rotor set, in particular the bearing ring and / or the planetary rotors and / or the inner rotor on at least one end face on a circumferential ridge. This circumferential ridge serves as a seal within the housing in which the toothed rotor set is received. Usually, such movable parts have a sealing surface on their end faces, which extends over the entire surface, with the exception of the teeth. The seal according to the invention by means of the circumferential ridge has the advantage that the high friction forces occurring in the known seals are greatly reduced and thus the toothed rotor set works lighter and thus more efficient. In this case, the circumferential ridge has a width which represents the optimum between sealing effect and frictional force.
  • Finally, the invention relates to a method for producing a Verzahungsrotorsatzes, wherein this is in a molding process, preferably by means of powder metallurgy process, plastic injection molding, extrusion, die casting, especially aluminum die casting, and stamping process is prepared. Such a complex toothing, as having the toothed rotor set according to the invention, is simple and inexpensive to produce by means of these methods. A filing and sawing, which is known in the usual gears Can be used, can find no application in the invention, since the toothing is too complicated for this purpose.
  • In an advantageous embodiment of the invention it is provided that the toothed rotor set in a pump, in particular a lubricating oil pump for internal combustion engines, is used.
  • In a further advantageous embodiment of the invention it is provided that the Verzahnungsrotorsatz is used as a motor.
  • The invention will be explained in more detail with reference to schematic drawings. Show it:
  • Fig. 1
    a gear rotor set,
    Fig. 1a
    Gear rotor set in a second working position,
    Fig. 1b
    Top view of the toothed rotor set with suction side and pressure side,
    Fig. 2
    a variant I of the inventive toothing according to the item "X" in Fig. 1 .
    Fig. 3
    a variant II of the toothing according to the invention
    Fig. 4
    a variant III of the toothing according to the invention
    Fig. 5
    a representation of the parameters used for the toothing calculation
  • Fig. 1 shows a Verzahnungsrotorsatz 1 invention, consisting of a rotatable bearing ring 2 with bearing pockets 3, in which rotatably mounted planetary rotors 4 are arranged, which form an internal toothing, with an eccentrically mounted to the bearing ring 2 inner rotor 5 with approximately star-shaped outer contour, which is provided with an external toothing 6 is, wherein the external toothing 6 has a tooth less than the internal toothing.
  • The toothed rotor set 1 has a suction region 7, a pressure region 8 and a displacement chamber 9.
  • A drive torque M1 acts on the toothed inner rotor 5 via a drive shaft 10. A circumferential force F2 acts on the toothed planetary rotor 4, which is mounted in a bearing ring 2 (housing), from the toothed inner rotor 5. The circumferential force F2 is divided into two components, the impact force (radial force) F3 and the torque M4, both acting on the toothed planetary rotor. The impact force F3 acts through the center of the toothed planetary rotor 4, which is mounted in a bearing ring 2, and sets the bearing ring 2 in rotation. By the torque M4 of the toothed planetary rotor is rotated.
  • The toothed rotor set 1 according to the invention can be used as a pump for generating pressure by the inner rotor 5 is driven via a drive shaft 10. On the other hand, the toothed rotor set 1 according to the invention can also be used as a motor by the pressure area is pressurized, so that the inner rotor 5 is set in rotation and the drive shaft 10 drives.
  • In the main zone of the transmission 11, in which the torque acts through the toothed inner rotor 5 via the toothed planetary rotor 4 on the bearing ring, it comes, geometrically caused, almost to a standstill of the planetary rotor 4. In the described relative stoppage and the simultaneous transmission of a large There is a risk that the Lubricating film between the planetary gear head 11 and bearing ring 2 collapses.
  • Fig. 1a shows the Verzahnungsrotorsatz 1 in a second working position. In this a maximum pressure is generated because the inner rotor 5 operates at most on the planetary rotors 4.
  • Fig. 1b shows a plan view of the Verzahnungsrotorsatz 1, wherein both a suction side 21 and a pressure side 23 are shown. In the suction side 21 opens an inlet opening 22, which may be formed, for example, laterally as a bore in the toothed rotor set receiving housing. Likewise, an outlet opening 24 opens into the pressure side 23. The diameter of the Auslaßöffung 24 is less than that of the inlet opening 22, since in the latter a higher flow rate is given.
  • Fig. 2 shows a variant I of the inventive toothing according to the detail "X" in Fig. 1 , In the Fig. 1 shown large impact force F3 (radial force) and the small circumferential force F4 must be transmitted. In this toothing, the tooth head 11 and the tooth root 12 are included in the rolling process, ie, the rolling of the toothed planetary rotor 4 on the toothed inner rotor curve. At the in Fig. 2 shown toothing, the surface portions of the teeth were chosen so that they correspond to the distribution of forces.
  • The largest portion, the arcuate portion 14 of the toothing thus consists of the tooth base 12 and tooth tip 11, which transmit the impact force F3 between the toothed inner rotor 5 and the toothed planetary rotor 4. Only a small proportion of the toothed surfaces consists of sliding surfaces in the region of the tooth flanks 15, which convert the circumferential force F4 into a rotational movement of the toothed planetary rotor 4.
  • The tooth head 11.1 of the toothed inner rotor 5 is calculated so that it applies exactly in the tooth root 12.2 of the toothed planetary rotor 4, and ensures trouble-free rolling. Conversely, the tooth tip 11.2 of the toothed planetary rotor 4 engages in the tooth root 12.1 of the toothed inner rotor 5. Here, it comes through the convex-shaped tooth tip 11.1 of the toothed inner rotor 5 and the concave tooth root 12.2 of the toothed planetary rotor 4 to a contact surface and not to a contact line. Due to this rolling pairing, therefore, the Hertzian pressure is greatly reduced.
  • This also applies to the tooth flanks of the toothed inner rotor 5 and the toothed planetary rotor 4. By including a backlash 17 between tooth of the planetary rotor 4 and tooth gap of the inner rotor 5 ensures that the large impact force F3 is transmitted only about the tooth tip 11 and tooth root 12. This prevents that act on the tooth flanks 15 large wedge forces that can lead to the destruction of the flank surfaces. In addition, due to the backlash 17, the pumped medium can flow out of the tooth spaces, otherwise squeezing oil occurs, which can lead to very high pressure build-up.
  • Fig. 3 shows a second variant of the toothing according to the invention. In the above-described relative stoppage of the planetary rotors 4 and the simultaneous transmission of a large force, there is a risk that the lubricating film between the planetary gear head 11 and bearing ring 2 collapses. This is prevented by the planetary rotor tooth heads 11 being flattened. The size of the flattening 13 depends on the field of application of the toothed rotor. At low speeds and high pressures a strong flattening 13 must be provided. At a high speed and low pressures, a moderate flattening 13 is sufficient to build up continuous lubricating film. For the transition from the tooth tip 11 of the planetary rotor 4 to the flattening 13, a cycloid 20 was used, which favors the lubricating film structure more than a simple transition radius.
  • By the flattening 13 of the planet tooth heads 11 and an improvement of the power transmission (Hertzian pressure) from the planetary rotor 4 is effected on the bearing ring 2.
  • Fig. 4 shows a third variant of the toothing according to the invention, wherein the tooth flanks 15 of the toothed inner rotor 5 and the toothed planetary rotors 4 are formed by an involute 18. The tooth tip of the planetary rotor 4, however, is formed as a cycloid 19. In this embodiment, however, there is a greater likelihood that engagement interference will occur.
  • Furthermore, all known gearing types are only suitable for the transmission of circumferential forces (torques), for example in gear transmissions. In almost all transmissions, except for gears with periodically variable translations (elliptical gears), the gears are firmly positioned by the center distance. The peripheral forces are transmitted only via the tooth flanks which touch in the pitch point C. In these rolling processes, the tooth head and the tooth root are excluded from the unrolling processes.
  • In all known types of gears can be transmitted only conditionally small or medium-sized radial forces. If radial forces act on a gear pair, the tooth of wheel 1 is pressed like a wedge into the tooth gap of wheel 2, whereby a very large flank pressure arises, whereby it can come to premature wear or to the tooth break.
  • This problem is solved by the involvement of the foot and tooth head in the rolling process. The radial forces (impact force F3) are transmitted in this case only by the foot and tooth head. By means of a special design of the root and tooth tips of the toothing, whereby the convexly curved tooth head 11 engages with a concavely curved tooth root 12, it is possible to reduce the edge pressure by up to 80%.
  • According to Fig. 5 For example, the stress on the contact line of the tooth flanks is calculated as the compressive stress of two parallel rollers which coincide with the tooth pairing in the following points: length b of the contact line, radius of curvature r1 and r2 in the cutting plane normal to the contact line, material pairing and surface quality.
    (rl and r2 are measured at the point of contact of the unloaded flanks)
  • For such rolling pairings Fg 2, the related load (k value after Stribeck). k = P / 2 * r * b kg / mm 2 Here is r = r 1 * r 2 / r 1 + r 2
    Figure imgb0001
    for concave flanks, r2 must be used negatively.
  • Calculation of tooth flanks (cycloids)
  • Only a small part of the tooth geometry consists of sliding surfaces, which convert the circumferential force F4 into a rotational movement of the toothed planetary rotor 4, wherein the size of the tooth flank is dependent on the application of the wheelset.
  • The toothing of the planetary rotor 4 is designed as zero toothing and that of the inner rotor 5 includes a negative profile displacement.
  • Calculation of the planetary rotor 4
  • pitch circle 1 t 1 = Pitch circle of the planetary rotor 4
    Figure imgb0002
    module = pitch circle 1 t 1 / Number of teeth of the planetary rotor 4
    Figure imgb0003
    tooth thickness = module * π / 2
    Figure imgb0004
  • Generation of tooth flanks 15
  • pitch circle 1 r 1 = pitch circle 2 r 2 = pitch circle t 1 1 * 0 . 3
    Figure imgb0005
  • Tooth base and tooth head design of planetary rotor 4
  • Pitch circle 3 (r3) of tooth head 11.2 (epi-cycloid); Turret 4 (r4) of tooth head 12.2 (hypocycloids) Division t = pitch circle 1 * π / Number of teeth of the planetary rotor 4 pitch circle 3 r 3 = pitch circle 4 r 4 = t / 2 / π
    Figure imgb0006
  • Calculation of inner rotor 5
  • pitch circle 2 t 2 = Pitch circle of the inner rotor curve 5 Grobverzhnung
    Figure imgb0007
    Division t = scope Inner rotor curve 5 / number of teeth
    Figure imgb0008
    Tooth thickness d = t / 2 - 2 * FLSP ,
    Figure imgb0009
    gap 1 = t / 2 + 2 * FLSP ,
    Figure imgb0010
    FLSP. = Backlash
  • Generation of tooth flanks
  • Generation as planetary rotor 4, but depending on the size of the variable pitch circle.
  • Tooth base - tooth head design of the inner rotor
  • pitch circle 5 r 5 tooth root 12.1 = t / 2 + 2 * FLSP , / π
    Figure imgb0011
    pitch circle 6 r 6 addendum 11.1 = t / 2 - 2 * FLSP , / π
    Figure imgb0012
  • In Fig. 4 If only the tooth flanks are designed as involute, all other calculation quantities are in accordance with the calculation listed above.
  • As a result of this design of the toothing, the curvature relationships between the tooth head 11 and the tooth root 12 (convex, concave) are very similar, as a result of which it comes almost to pure surface contact and thus the Hertzian pressure is reduced. Furthermore, in this optimized design during rolling the added sliding movement (tangential friction force) is very low.
  • The inventive toothing can also be used in elliptical wheels, general non-circular wheels and Roots blowers.

Claims (10)

  1. A toothed rotor set (1), comprising a rotatable bearing ring (2) with bearing recesses (3) in which are arranged planetary rotors (4) which are mounted so as to be rotatable and which form an internal set of teeth, with an inner rotor (5) mounted eccentrically with respect to the bearing ring (2) and having a substantially star-shaped external contour which is provided with an external set of teeth (6), wherein the external set of teeth (6) has one tooth fewer than the internal set of teeth and the set of teeth of at least one of the two rotor systems has an arcuate portion (14) at least in partial regions of the tooth shape of the set of teeth, wherein the arcuate portion (14) is constructed at least in part in the form of a cycloid (19) and
    a) the planetary rotor 4 is designed in accordance with the following formulae:
    pitch circle 1 (t1) = rolling circle of the planetary rotor 4
    module = pitch circle 1 (t1) / number of teeth of the planetary rotor 4
    tooth thickness = module * π / 2
    Production of the tooth flanks 15
    roll circle 1 (r1) = roll circle 2 (r2) = pitch circle (t1) 1 * 0·3
    Design of the bases and the tips of the teeth of the planetary rotor 4
    roll circle 3 (r3) of the tooth tip 11.2 of the planetary rotor; roll circle 4 (r4) of the tooth tip 12.2 of the planetary rotor
    pitch t = pitch circle 1 (t1) * π/ number of teeth of the planetary rotor 4
    roll circle 3 (r3) = roll circle 4 (r4) = t / 2 /π
    and
    b) the inner rotor 5 is designed in accordance with the following formulae:
    pitch circle 2 (t2) = rolling circle of the curve of the inner rotor 5
    pitch t = periphery (curve 6 of the inner rotor) / number of teeth
    tooth thickness d = (t / 2 - 2 * Flcl.)
    tooth gap 1 = (t / 2 + 2 * Flcl.) Flcl. = flank clearance
    Production of the tooth flanks
    Production as in the case of the planetary rotor 4, but in a manner dependent upon the size of the variable rolling circle.
    Design of the bases and the tips of the teeth of the inner rotor 5
    roll circle 5 (r5) (tooth base 12.1 of the inner rotor) = (t / 2 + 2 * Flcl.) / π
    roll circle 6 (r6) (tooth tip 11.1 of the inner rotor) = (t / 2 - 2 * Flcl.) / π
  2. A toothed rotor set (1) according to Claim 1, characterized in that the tooth shape is designed in the form of a cycloid, in particular in the region of the tooth tip (11) and/or the tooth base (12).
  3. A toothed rotor set (1) according to one of Claims 1 or 2, characterized in that the tooth base of the fine set of teeth is designed in the form of a hypocycloid and the tooth tip is designed in the form of an epicycloid.
  4. A toothed rotor set (1) according to any one of Claims 1 to 3, characterized in that the tooth flanks are designed in the form of a cycloid.
  5. A toothed rotor set (1) according to any one of Claims 1 to 4, characterized in that the tooth shape is designed in the form of an involute (18) at least in the region of the tooth flanks.
  6. A toothed rotor set (1) according to any one of Claims 1 to 5, characterized in that the tooth shape has a flattened portion (13), in particular [in] the region of the tip (11) and/or of the base (12) of the teeth.
  7. A toothed rotor set (1) according to any one of Claims 1 to 6, characterized in that the set of teeth has a low-wear surface.
  8. A toothed rotor set (1) according to any one of Claims 1 to 7, characterized in that at least one fluid duct (16) is provided in the region of the bearing recesses (3).
  9. A toothed rotor set (1) according to any one of Claims 1 to 8, characterized in that the bearing ring (2) and/or the planetary rotors (4) and/or the inner rotor (5) has or have a continuous web on at least one end face.
  10. A process for producing a toothed rotor set according to any one of Claims 1 to 9, characterized in that the toothed rotor set (1) is produced in a shaping process, preferably by means of powder-metallurgical processes, plastics-material injection moulding, impact extrusion, die-casting, in particular aluminium die-casting, and stamping processes.
EP20000941957 1999-05-18 2000-05-17 Toothed rotor set Active EP1180217B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE1999122792 DE19922792A1 (en) 1999-05-18 1999-05-18 Geared pump rotor assembly e.g. for lubricating oil on internal combustion engine, comprises planet gears in outer ring round star-shaped rotor
DE19922792 1999-05-18
PCT/EP2000/004474 WO2000070228A1 (en) 1999-05-18 2000-05-17 Toothed rotor set

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EP1180217A1 EP1180217A1 (en) 2002-02-20
EP1180217B1 true EP1180217B1 (en) 2008-04-30

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US (1) US6540637B2 (en)
EP (1) EP1180217B1 (en)
JP (1) JP3670215B2 (en)
CN (1) CN1179129C (en)
AT (1) AT393881T (en)
AU (1) AU5674300A (en)
BR (1) BR0010627A (en)
CA (1) CA2372883C (en)
DE (2) DE19922792A1 (en)
MX (1) MXPA01011453A (en)
WO (1) WO2000070228A1 (en)

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AU5674300A (en) 2000-12-05
CA2372883A1 (en) 2000-11-23
JP3670215B2 (en) 2005-07-13
CA2372883C (en) 2009-09-15
US20020159905A1 (en) 2002-10-31
CN1351694A (en) 2002-05-29
BR0010627A (en) 2002-02-19
US6540637B2 (en) 2003-04-01
CN1179129C (en) 2004-12-08
DE19922792A1 (en) 2000-11-23
JP2002544442A (en) 2002-12-24
AT393881T (en) 2008-05-15
MXPA01011453A (en) 2002-11-07
EP1180217A1 (en) 2002-02-20
WO2000070228A1 (en) 2000-11-23

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