EP3631245A1 - Roue dentée pour un train d'engrenages - Google Patents

Roue dentée pour un train d'engrenages

Info

Publication number
EP3631245A1
EP3631245A1 EP18722939.8A EP18722939A EP3631245A1 EP 3631245 A1 EP3631245 A1 EP 3631245A1 EP 18722939 A EP18722939 A EP 18722939A EP 3631245 A1 EP3631245 A1 EP 3631245A1
Authority
EP
European Patent Office
Prior art keywords
gear
spring ring
spur
recess
spur gear
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.)
Withdrawn
Application number
EP18722939.8A
Other languages
German (de)
English (en)
Inventor
Rene Schwarze
Christian Stephan
Marc Schieß
Ulrich Mair
Lars Schories
Karl Benkler
Carsten Stamm
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.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP3631245A1 publication Critical patent/EP3631245A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/2863—Arrangements for adjusting or for taking-up backlash
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • F16H55/18—Special devices for taking up backlash
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/12—Arrangements for adjusting or for taking-up backlash not provided for elsewhere
    • F16H2057/126—Self-adjusting during operation, e.g. by a spring
    • F16H2057/127—Self-adjusting during operation, e.g. by a spring using springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion

Definitions

  • the invention relates to a gear for a gear transmission according to the preamble of patent claim 1.
  • Planetary gears are used in various fields of technology, these being so-called epicyclic gears, i. Gearboxes which, in addition to a housing-fixed shaft, also have axles which revolve on a circular path in the housing. In planetary gears, the revolving axes are parallel to the shaft fixed to the housing, with the gears rotating on the revolving axes orbiting around a central wheel - much like planets orbiting the sun.
  • roll stabilizer In vehicle technology, there are different applications for planetary gear. To increase vehicle stability and driving comfort, it is known per se to equip vehicles with a so-called roll stabilizer. In the simplest version, this is a substantially C-shaped torsion bar spring, which is mounted in the central region relative to the body and whose outer, opposite ends are each connected to a wheel suspension. Due to this construction, the roll stabilizer ensures that the body of the vehicle does not only spring in on the outside of the curve when cornering (due to the centrifugal force), but also that the inside wheel is slightly lowered (copying behavior).
  • the roll stabilizer comprises an actuator and is divided into two by means of the actuator relative to each other rotatable stabilizer halves. By rotation of the stabilizer halves to each other, a rolling motion of the vehicle body is selectively generated or deliberately counteracted caused by external influences rolling motion of the vehicle body.
  • roll stabilizers in which an electric motor serves as a drive of the actuator.
  • such a roll stabilizer usually has a mechanical transmission, in particular in the design of one (or more in stages Nander arranged) planetary gear (s) for the translation of the torque or the rotational speed of the electric motor used.
  • such planetary gear essentially have a centrally disposed sun gear, a set of planetary gears and a ring gear.
  • the planet gears each designed as a toothed wheel, are rotatably mounted about their own axis of rotation relative to a planet carrier. All planetary gears are in meshing engagement and roll off the centrally located sun gear. At the same time the planetary gears are in meshing engagement and roll off an outer ring gear, which is usually fixed to the housing in the application of a roll stabilizer, that is designed as part of the housing of the actuator.
  • the pair of spur gears is arranged on a common axis of rotation, wherein the first spur gear and the second spur gear are axially spaced from each other. Furthermore, the gear has an axially disposed between the two spur gears open spring ring.
  • the spring ring has a first end which is supported in a circumferential direction relative to the first spur gear on a cam formed thereon, and a second end which is supported in the opposite direction relative to the second spur gear on a cam formed thereon.
  • the twisting of the Spur gears to each other thus generates a bias, which ensures in the installed state of the gear within the planetary gear in an advantageous manner that create opposite flanks of both spur gears clearance on the opposite edges of the counter teeth of the outer ring gear and / or the inner sun gear.
  • the bracing of the spur gears against each other thus causes a reduction in the game within the planetary stage.
  • a toothed wheel having the features of patent claim 1. It is a gear for a gear transmission, in particular for a planetary gear, which is divided into at least a first spur gear and a second spur gear.
  • the spur gears are axially spaced apart on a common axis of rotation, wherein the gear further comprises an open spring ring.
  • the spring ring is a first end which is supported in a circumferential direction relative to the first spur gear, and associated with a second end, which is supported in the circumferential direction in the opposite direction relative to the second spur gear.
  • the support is designed such that by turning the spur gears can be clamped against each other about the common axis of rotation of the spring ring to exert on the spur gears a restoring moment.
  • the axial size of the toothed wheel can advantageously be reduced by forming a recess for receiving the spring ring in sections on at least one of the spur gears.
  • the spring ring arranged between the two spur wheels virtually equals the axial size of the toothed wheel about its own axis. Enlarged a depth, ensures in the inventive gear formed on at least one of the spur gears recess that the spring ring in this at least partially or - in the presence of opposing recesses in both spur gears - in total even completely submerge.
  • the axial space of the gear is thus advantageously reduced.
  • the usable tooth flank width is thus increased in relation to the axial height of the gear wheel, which has an overall advantageous effect in view of the high torques to be transmitted.
  • gear of the already mentioned spring ring is advantageously arranged axially between the first spur gear and the second spur gear.
  • the inventively provided recess for receiving sections of the spring ring can be designed in different ways. Appropriately, this takes on at least one end of the spring ring and has a contact surface on which the received end of the spring ring is supported.
  • the contact surface may advantageously be pocket-shaped to receive the complementary preferably nose-shaped end of the spring ring. Due to the pocket-shaped design of the contact surface advantageously a positive connection between the spur gear and spring ring is formed in this way, which is intended to prevent slippage of the spring ring, in particular in the radial direction.
  • the contact surface has a radius which is the same as or at least slightly larger than a radius of the preferably nose-shaped end of the spring ring.
  • a large contact surface whereby advantageously only a small surface pressure in the material of the spur gear and / or the spring ring is formed.
  • the radius of the pocket is chosen at least slightly larger than the radius of the nose-shaped end of the spring ring, it is ensured that the spring ring under load - and thereby Conditional deformation - linear (ie, forming a line contact) can roll on the pocket-shaped contact surface of the spring ring. In the case of only linear contact, the surface friction and thus the risk of stick-slip ("stick-slip") between the spur gear and the spring ring are reduced.
  • the recess has a circular arc-shaped course. Since the open spring ring also has a circular arc-shaped form, the recess can thus receive the open spring ring at least in sections, wherein the spring ring can fill the recess to a high degree.
  • the spur gears for storage on a common axis of rotation in particular on a the spur gears axially penetrating bearing pin, each having a passage, which is preferably formed approximately cylindrical.
  • the recess adjacent to the radial extent of the spur gear directly adjacent to the preferably approximately cylindrical passage is therefore formed in this case at a radially inner region of the spur gear, whereby advantageously the tooth root of the spur gear is weakened only to a very small extent or not at all by the recess.
  • the gear of the spring ring has a smaller inner diameter than the passage formed in the spur gears, the spring ring - in addition to its function of generating a restoring torque - also be used for axial securing in particular a bearing the spur rolling bearing.
  • the recess may be formed as an introduced into the material of the spur gear groove.
  • a groove offers the advantage that the spring ring can be supported both radially inwardly and radially outwardly on the respective groove wall. Quite independently of the other design of the gear, it can be provided that the recess has a constant over the course of their axial depth. A course of the recess with constant axial depth is particularly advantageous from a manufacturing point of view, since this can be produced inexpensively and with little effort.
  • the recess starting from the contact surface for the respective end of the spring ring, has a preferably continuously decreasing axial depth in the sense of a ramp.
  • the spring ring has an axial slope, it can then be supported at least in sections flat in the axial direction of the respective spur gear.
  • the spring ring used on the toothed wheel can be designed differently with respect to its circumferential course. According to an advantageous embodiment, this has less than one turn. With reference to the axis of rotation, the two ends of the open spring ring are thus removed from one another by less than 360 °.
  • the spring ring has more than one turn, preferably about one and a half turns. Relative to the axis of rotation, the two ends of the open spring ring are thus removed from each other by about 540 ° arcuately. Conveniently, the spring ring on more than one turn on an axial slope.
  • the spring ring in the relaxed state quite generally an axial pitch to axially push apart the spur gears in the installed state of the gear, in particular in a housing of a planet carrier of a planetary gear, for the purpose of clearance compensation and / or based on the to tilt common axis of rotation against them.
  • the spring ring thus comes in this design to another function; it is used for clearance compensation in the installed state of the gear. It may be a clearance compensation in the circumferential direction, in the axial direction and / or in the radial direction.
  • FIG. 1 is a gear for a planetary gear according to a first embodiment of the invention in exploded view
  • FIG. 3 shows the gear according to the first embodiment in a sectional view from the side, a gear for a planetary gear according to a second embodiment of the invention in the assembled state in side view,
  • FIG. 8 is a schematic view of an adjustable roll stabilizer articulated to opposing wheel suspensions of a vehicle, a planetary carrier which may be incorporated as part of a planetary gear in an adjustable roll stabilizer as shown in FIG. 8 and incorporating a plurality of gears according to the present invention
  • Fig. 10 is a detail view of the gear according to the second embodiment shown in FIGS. 4 to 7.
  • Figure 1 shows a gear 1 according to a first embodiment of the invention in an exploded view.
  • the gear 1 consists of a first spur gear 3 and a second spur gear 4, which are axially spaced from each other on a common axis of rotation 2.
  • Each of the two spur gears 3, 4 has an external toothing (not shown).
  • the spur gears 3, 4 can mesh in particular with a sun gear and a ring gear of a planetary gear.
  • the gear 1 further comprises an open spring ring 5.
  • the spring ring 5 one and a half turns, therefore, a first end 6 of the spring ring 5 according to the circular arc shape of the spring ring 5 by one and a half turns relative to the axis of rotation 2 spaced from a second end 7 of the spring ring 5.
  • the spring ring 5 is made of metal, so it is in the spring ring 5 is an inherently elastic body.
  • the spring ring 5 is designed in particular for bending stress, which may be caused in particular by circumferentially acting on the first end 6 and the second end 7 forces.
  • a recess 9 is formed in each case. This is an inserted into the material of the spur gear 3, 4 groove with a circular arc course. At a peripheral end of the recess 9 each have a contact surface 10 is formed, wherein the recess 9, starting from this contact surface has a continuously decreasing axial depth in the sense of a ramp. The recess 9 thus decreases starting from the contact surface 10 along its arcuate course in terms of the axial depth to run out after about half a turn (about the axis of rotation 2) with reaching a depth of zero.
  • the recess 9 on each of the two spur gears 3, 4 thus has an approximately semi-circular arc-shaped course to form a continuously decreasing groove bottom. It is Note that, unlike the embodiment shown, the recess 9 may be formed fully.
  • the formed on the two spur gears 3, 4 recesses 9 are formed on the mutually facing axial surfaces of the spur gears 3, 4.
  • the first end 6 of the open spring ring 5 is supported - in the installed state - in the circumferential direction 8 relative to the spur gear 3 at the local contact surface 10.
  • the second end 7 of the open spring ring 5 is supported - again in the assembled state - in the direction opposite to the circumferential direction 8 opposite to the bearing surface 10 formed on the second spur gear 4.
  • each of the spur gears 3, 4 has a cylindrical passage 15 in the form of a pin bore, so that a bearing pin can pass through the spur gears 3, 4 along the axis of rotation 2, on which the spur gears 3 , 4 can be rotatably supported for example by means of rolling or sliding bearings.
  • the spring ring 5 is recessed at least partially in the recess 9 of the first spur gear 3 or in the recess 9 of the second spur gear 4.
  • the gear 1 thus has, despite the presence of the spring ring 5, a relatively small axial depth, which is useful for transmitting torque usable tooth flank width relative to the axial depth of the gear 1 is relatively large.
  • the first end 6 is supported in the circumferential direction 8 relative to the first spur gear 3 and the second end 7 is supported in the opposite direction relative to the second spur gear 4, by turning the spur gears 3, 4 against each other around the common Tighten the axis of rotation 2 of the spring ring 5 so as to exert on the spur gears 3, 4 an opposing restoring moment.
  • the first spur gear 3 is rotated according to the illustration of Figure 1 against the circumferential direction 8 about the rotation axis 2 when the second spur gear 4 remains in its rotational position shown.
  • the basic structure of the gear 1 according to the second embodiment is similar to that of the gear 1 of the first embodiment. To avoid repetition, reference should therefore be made to statements already made, as applicable. It should also be mentioned that features provided with the same reference numerals of the second embodiment are similar to those of the first exemplary embodiment, as far as no deviating description follows.
  • Figure 4 shows the gear 1 according to the second embodiment in the assembled state in plan view from the side.
  • the gear 1 consists of a first spur gear 3 and a second spur gear 4, which are axially spaced from each other on a common axis of rotation 2.
  • a bearing pin 12 which is guided by the cylindrical bore 15 designed as a pin bore of the first spur gear 3 and the second spur gear 4.
  • the bearing pin 12 has a greater axial extent than the gear 1 and thus protrudes from the gear 1 at each of its ends in the axial direction.
  • a toothing 14 formed on the spur gears 3, 4 is symbolically indicated by a bold line in each case.
  • FIG. 5 shows the gear 1 according to the second embodiment now in a sectional view.
  • the installation state of the gear 1 is indicated within a planet carrier, to a housing 1 1 of the planet carrier is partially drawn, wherein the bearing pin 12 is pressed into axially opposite holes of the housing 1 1 of the planet carrier.
  • Each of the spur gears 3, 4 is mit- Supported by a needle bearing 13 rotatably mounted relative to the bearing pin 12.
  • a spring ring 5 is disposed between the first spur gear 3 and the second spur gear 4. In the material of the spur gears 3, 4 to a respective recess 9 is formed.
  • the recess 9 is, however, arranged in the gear 1 according to the second embodiment, each of which, in relation to the radial Warre- ckung of the spur gear 3, 4 directly adjacent to the cylindrical passage 15.
  • the recess 9 in the spur gears 3, 4 is thus not designed as a groove in the strict sense, because it is not radially bounded on the inside by the material of the respective spur gear 3, 4.
  • the spring ring 5 has a smaller inner diameter than the passage 15 formed in the spur gears 3, 4.
  • the spring ring 5 adjoins the bearing pin 12 with its inner peripheral surface. The design makes it possible that the spring ring 5 for axial securing of the needle bearing 13 of the first spur gear 3 and second spur gear 4 is available.
  • Figure 6 shows the gear 1 according to the second embodiment in a section B- B of Figure 4 from above.
  • the second spur gear 4 can be seen in the left-hand part of FIG. 6, while in the image area on the right the cutting step (indicated by the broken line on the left of the center line) can be seen outside the first spur gear 3 is.
  • the open spring ring 5 is designed differently than in the first embodiment. It is an open ring body, which, unlike the first embodiment, however, has less than one turn.
  • a first end 6 of the spring ring 5 is supported relative to the first spur gear 3 on a bearing surface 10 formed there, which is formed approximately complementary to the nose-shaped end 6 of the spring ring 5.
  • the engagement of the nose-shaped end 6 of the spring ring in the pocket-shaped contact surface 6 of the first spur gear can also be seen in FIG. 7, which shows the gear 1 according to the second exemplary embodiment in a perspective view obliquely from above, the second spur gear 4 being omitted for reasons of illustration.
  • the figure 7 can be seen that the spring ring 5 - in the shown, relaxed state - has a certain axial slope. That is, the first end 6 of the spring ring relative to the axis of rotation 2 is offset in the axial direction relative to the second end 7 of the spring ring 5.
  • the second end 7 of the spring ring 5 reaches a position in the axial direction , in which this protrudes from the first spur gear 3.
  • the spring ring 5 is partially immersed in a recess 9 formed on the second spur gear 4 on the side facing the first spur gear 3.
  • the second end 7 of the spring ring 5 is like the first end 6 of the spring ring 5 also nose-shaped.
  • the second end 7 of the spring ring 5 is supported on a pocket-shaped contact surface 10, which is designed to be complementary to the end 7 of the spring ring 5 on the second spur gear 4.
  • the function and operation of the gear 1 according to the second embodiment is similar to the gear 1 of the first embodiment. Also in the gear 1 according to the second embodiment can be rotated by turning the spur gears 3, 4 against each other about the common axis of rotation 2 of the spring ring 5 to exert on the spur gears 3, 4 a restoring moment.
  • the spring ring 5 has a substantially constant radial width over its circumferential course. Only in the region of the first end 6 and the second end 7, the radial width of the spring ring 5 decreases.
  • the radial width of the spring ring 5 decreases.
  • a load-optimized design of the spring ring 5 could therefore be carried out deviating from the representation of Figure 6, namely, only in one of the opening (ends 6, 7) facing away from the central region has a maximum radial width, starting from there, however, with a the ends 6, 7 towards continuously decreasing radial width is provided.
  • the axial slope of the spring ring 5 continues to effect advantageously an achievable with the gear 1 clearance compensation.
  • the gear 1 namely exerts the spring ring 5 between the first spur gear 3 and second spur gear 4 axial pressure.
  • This is effected by the fact that the spring ring 5 abuts at least in the region of its first end 6 in the axial direction on the first spur gear 3, while the second end 7 of the spring ring in the axial direction abuts the second spur gear 4.
  • the formed in the spur gears 3, 4 recesses 9 and the spring ring 5 are dimensioned so that in the installed state of the gear 1 in a housing 1 1 of a planet carrier (see Figure 5) of the spring ring 5 is slightly compressed in the axial direction. Due to its elasticity, the spring ring 5 develops a corresponding restoring force and thus pushes the spur gears 3, 4 spielredufugd or even spielaufariad outward against the housing 1 1 of the planet carrier.
  • the restoring force of the spring ring 5 acting in the axial direction additionally causes a (slight) tilting of the first spur gear 3 and the second spur gear 4 with respect to the rotation axis 2.
  • this tilting can advantageously be present in the needle bearing 13 bearing clearance reduced or even eliminated.
  • FIG. 10 shows further details of the toothed wheel of the second exemplary embodiment. To see is a detail section, which describes in particular the contact situation between the open spring ring 5 and a spur gear, here the first spur gear 3. The second spur gear 4 of the gear is not visible in the view.
  • the first end 6 of the spring ring 5 is supported relative to the first spur gear 3 on the abutment surface 10 formed there.
  • the first end 6 of the spring ring 5 is formed nose-shaped.
  • the contact surface 10 contacting nose at the first end 6 of the spring ring 5 has a radius and runs tangent to the radially inner.
  • the trained on the spur gear 3 contact surface 10 forms with respect to the first end 6 of the spring ring 5 to an approximately complementary pocket, which receives the nose.
  • the pocket also has a radius and also runs tangentially to the radially interior.
  • the tangential outlet of the pocket to the radially inner forms a contour 33 in the sense of an undercut. This undercut prevents slipping of the first end 6 spring ring 5 in the radial direction (radial securing of the nose-shaped end 6).
  • the radius of the pocket formed on the spur gear 3 should be at least equal to or greater than the radius of the nose at the first end 6 of the spring ring 5.
  • the radii of pocket and nose are the same.
  • a large (curved) contact surface is formed between the spur gear 3 and spring ring 5, whereby advantageously only a small surface pressure in the material of the spur gear 3 and the spring ring 5 is formed.
  • the radius of the pocket could be chosen to be at least slightly larger than the radius of the nose-shaped end of the spring ring. This would ensure that the spring ring under load - and consequent deformation - linear (ie, forming a line contact) can roll on the pocket-shaped contact surface of the spring ring.
  • a purely linear contact minimizes the surface friction and thus the stick-slip risk ("stick-slip") between the spur gear and the spring washer.
  • the surface pressure does not reach a critical value and no plastic deformation occurs. Rather, the design should then allow elastic deformation to result in a larger contact area, which would lower the surface pressure.
  • Figure 10 shows that the circular arc-shaped recess 9, which receives the spring ring 5, has a slightly larger diameter than the spring ring 5 on its outer periphery. A thus resulting, in Fig. 10 partially visible ring section-shaped space allows that the spring ring 5 can bend open under load.
  • the spring ring 5 is axially adjacent to the needle bearing 13, the needle bearing cage 32 is partially seen in Figure 10.
  • the spur gear 3 In the circumferential direction of the spring ring 5 contacted the spur gear 3 exclusively with its first end 6 in the region of the contact surface 10. With its second end 7 contacted the spring ring 5 in the circumferential direction exclusively the spur gear 4 (see Fig .. 4 to 7).
  • FIG 8 shows a schematic view of an adjustable roll stabilizer 20.
  • the roll stabilizer 20 is part of a not fully shown chassis of a (not shown) vehicle.
  • a first wheel 21 a and arranged on the opposite side of the vehicle wheel 21 b are each connected via a wishbone 22 a and 22 b and further, not shown for reasons of simplification chassis components with the structure of the vehicle.
  • Wheel 21 a and wishbone 22 a and 21 b and wishbone 22 b thus each form a suspension.
  • Each of these suspensions is coupled to one end of a respective one of the stabilizer halves 23a and 23b of the variable roll stabilizer 20.
  • the two stabilizer halves 23a and 23b are connected to each other in the center of the vehicle via an actuator 24.
  • the roll stabilizer 20 is rotatably mounted about an axis 25 relative to the vehicle body (not shown).
  • the actuator 24, shown here in simplified form as a cylindrical body, essentially comprises a housing, an electric motor and a gear arrangement. About the electric motor and the gear assembly, the stabilizer half 23a and the stabilizer half 23b are in drive connection. When the electric motor is stationary, the two stabilizer halves 23a, 23b are rigidly connected to one another in the region of the actuator 24. By operation of the electric motor, the stabilizer halves 23a, 23b can be rotated about the axis 25 depending on the direction of rotation of the electric motor against each other. Thus, the roll stabilizer 20 can be adjusted in known manner per se.
  • the existing in the actuator 24 gear assembly typically includes several stages of planetary gears.
  • the output-side planetary gear which is thus rotatably connected to one of the two stabilizer halves, mechanically exposed to high torques.
  • FIG. 9 shows by way of illustration a planet carrier 30, which may be part of an output-side planetary stage of an adjustable roll stabilizer 20, as schematically shown in FIG.
  • an input pinion 31 is arranged on the axis 25, which corresponds to the axis of rotation of the roll stabilizer 20 according to FIG. 8, an input pinion 31 is arranged.
  • This input pinion 31 is made in one piece with a sun gear arranged within the planet carrier 30, which is hidden in the illustration of FIG. 9 by the planet carrier 30.
  • a total of four toothed wheels 1 are arranged around the sun gear (alternatively three or more than four toothed wheels could be arranged around the sun wheel), which are each mounted so as to be rotatable relative to the planet carrier 30 about a rotation axis 2.
  • the gears 1 are each in meshing engagement with the central sun gear.
  • the four gears 1 are also in meshing engagement with a ring gear formed by the inner housing wall.
  • the four toothed wheels 1 of the planet carrier 30 are in each case toothed wheels which are divided into first and second spur gears which are axially spaced from each other on a common axis of rotation 2.
  • the planet carrier 30 with inventive, as previously described gears 1 equipped. can be configured, for example, according to the first embodiment (FIGS. 1-3) or according to the second embodiment (FIGS. 4-7).

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gears, Cams (AREA)
  • Retarders (AREA)

Abstract

La présente invention concerne une roue dentée (1) pour un train d'engrenages, en particulier pour une boîte de vitesses à trains épicycloïdaux d'un système d'aide au châssis, la roue dentée (1) étant divisée en au moins une première roue dentée droite (3) et une deuxième roue dentée droite (4), qui sont axialement espacées l'une de l'autre sur un axe de rotation commun (2), la roue dentée (1) comprenant en outre une rondelle à ressort (5) ouverte comportant : une première extrémité (6), qui prend appui dans une direction circonférentielle (8) par rapport à la première roue dentée droite (3) ; et une deuxième extrémité (7), qui prend appui dans la direction à l'opposée de la direction circonférentielle (8) par rapport à la deuxième roue dentée droite (4), de telle sorte que, en tournant les roues dentées droites (3, 4) l'une contre l'autre autour de l'axe de rotation commun (2), il est possible de tendre la rondelle à ressort (5) pour exercer sur les roues dentées droites (3, 4) un moment redresseur, caractérisé en ce que sur au moins une des roues dentées droites (3, 4) un évidement (9), destiné à recevoir par sections la rondelle à ressort (5), est conçu.
EP18722939.8A 2017-05-24 2018-04-26 Roue dentée pour un train d'engrenages Withdrawn EP3631245A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017208800.1A DE102017208800B3 (de) 2017-05-24 2017-05-24 Zahnrad für ein Planetengetriebe
PCT/EP2018/060786 WO2018215162A1 (fr) 2017-05-24 2018-04-26 Roue dentée pour un train d'engrenages

Publications (1)

Publication Number Publication Date
EP3631245A1 true EP3631245A1 (fr) 2020-04-08

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP18722939.8A Withdrawn EP3631245A1 (fr) 2017-05-24 2018-04-26 Roue dentée pour un train d'engrenages

Country Status (5)

Country Link
US (1) US11486468B2 (fr)
EP (1) EP3631245A1 (fr)
JP (1) JP6997808B2 (fr)
DE (1) DE102017208800B3 (fr)
WO (1) WO2018215162A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018220836A1 (de) * 2018-12-03 2020-06-04 Zf Friedrichshafen Ag Geteiltes Zahnrad mit mehreren in Umfangsrichtung verspannbaren Zahnradteilen

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4189951A (en) * 1978-06-27 1980-02-26 Bulova Watch Company, Inc. Anti-backlash gear
JPS60177366U (ja) * 1984-05-04 1985-11-25 トヨタ自動車株式会社 無背隙式シザ−ズギヤ
JPH02129434A (ja) * 1988-11-07 1990-05-17 Koyo Seiko Co Ltd 遊星ギヤ減速機
RU2020338C1 (ru) * 1991-06-28 1994-09-30 Всероссийский научно-исследовательский институт "Сигнал" Способ сборки зубчатых колес
JPH11153210A (ja) * 1997-11-19 1999-06-08 Toyota Motor Corp シザーズギヤ
DE102005041357A1 (de) * 2004-09-07 2006-04-06 Honda Motor Co., Ltd. Scherzahnrad und spielfreier Mechanismus
CN2729432Y (zh) * 2004-09-12 2005-09-28 郑州华萦化纤科技有限责任公司 具有消除齿轮副侧隙功能的齿轮
EP1837558A1 (fr) * 2006-03-20 2007-09-26 Kwang Yang Motor Co., Ltd. Mécanisme pour éviter du bruit pour un engrenage d'équilibrage d'un vilebrequin d'un moteur
DE102007006470A1 (de) * 2007-02-09 2008-01-10 Audi Ag Zahnrad mit Temperaturgangkompensation
TWI454625B (zh) * 2011-12-13 2014-10-01 Ind Tech Res Inst 行星齒輪組之齒隙消除裝置
DE102011122136A1 (de) * 2011-12-22 2013-06-27 PMG Füssen GmbH Zahnradanordnung
AT513613B1 (de) 2013-02-08 2014-06-15 Miba Sinter Austria Gmbh Zahnradanordnung
NL2012082C2 (en) * 2014-01-14 2015-07-16 Vcst Ind Products Bvba Scissor gear assembly.
DE102015202236A1 (de) * 2015-02-09 2016-08-11 Schaeffler Technologies AG & Co. KG Zahnradanordnung
DE102015206063B4 (de) 2015-04-02 2017-03-16 Schaeffler Technologies AG & Co. KG Zahnrad für ein Zahnradgetriebe
DE102016207966A1 (de) * 2016-05-10 2017-11-16 Schaeffler Technologies AG & Co. KG Zahnradanordnung

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US11486468B2 (en) 2022-11-01
JP6997808B2 (ja) 2022-01-18
US20200217413A1 (en) 2020-07-09
WO2018215162A1 (fr) 2018-11-29
JP2020521091A (ja) 2020-07-16
DE102017208800B3 (de) 2018-10-31

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