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
  • F16H1/2809—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels
  • F16H1/2845—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels by allowing limited movement of the sun gear
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
  • F16C19/545—Systems comprising at least one rolling bearing for radial load in combination with at least one rolling bearing for axial load
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
  • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
  • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
• • 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
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
  • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
  • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
  • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
  • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
  • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
  • F16C19/166—Four-point-contact ball bearings
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C2361/00—Apparatus or articles in engineering in general
  • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

Definitions

• Transmission device comprising at least one housing and a planetary drive
• the planetary drive is at least formed of a rotatably mounted about a central axis of the transmission device in the housing planet carrier and a rotatable about the axially aligned central axis sun gear meshing with planetary gears, and wherein the sun gear with a
• the invention also relates to a drive unit with an electric drive and that of a transmission device in which the sun gear is connected to a rotor shaft of the electric drive
• Such a transmission device is disclosed in JP2011208758 A2.
• the transmission device is part of a hybrid drivetrain having an internal combustion engine and two electrodynamic machines.
• the electrodynamic machines can be used either as drive or generator.
• the rotor shaft of one of the drives is mounted with ball bearings in the housing of the drive unit and is operatively connected to a planetary drive via a friction clutch in the manner of a multi-plate clutch.
• the planetary drive has a planet carrier, a set of planets, a ring gear and a sun gear.
• the multi-plate clutch consists of an outer plate carrier and an inner plate carrier The hub of the outer plate carrier is provided with a serration, which is in a positive connection with a serration of the rotor shaft.
• axially displaceable outer disks which alternate with inner disks of the disk clutch, are seated on the outer disk carrier.
• the inner fins sit outside on the inner plate carrier whose hub is the sun gear of the planetary drive.
• the shaft of the sun gear and the inner plate carrier are firmly connected to one another.
• the sun gear is mounted radially on the rotor shaft at a bearing point by means of a sliding bearing and axially mounted on the planet carrier at another bearing point by means of an axial bearing.
• the planet carrier is mounted radially on a needle bearing on a shaft and the shaft radially via a ball bearing on the housing of the drive unit
• the sun gear must be able to freely radially center on the planetary gears even to the central axis of the planetary drive, so that the power is transmitted evenly over all with the sun gear in meshing planetary gears.
• the provided with a helical gear sun gear is supported axially via the thrust bearing on the planet carrier.
• a disadvantage of such arrangements is that the form-fitting connections and center shifts of rotating components or of their bearings hinder self-centering. This creates unwanted constraining forces in the gears and bearings, which can lead to premature failure of the drive unit.
• the components and their fits must therefore be made very accurately with the appropriate effort and high costs.
• To counteract this often the positive connections are made with a much larger game to compensate for these disadvantages.
• this larger game again leads to relative movements in the connection, especially in the connections in which there is unwanted displacement. These relative movements can cause noise and unwanted wear.
• the object of the invention is therefore to provide a transmission device and in particular an electrically driven transmission device of a drive unit with electric drive can be avoided in the tension between components in which the sun can center freely and takes up little space.
• the invention provides that the thrust bearing for the sun gear in the transmission device is a ball bearing.
• Another claim provides a drive unit with such a transmission device.
• the sun gear is supported by means of the ball bearing axially supported on the component.
• the component may be, for example, a transmission shaft, an adjacent planet carrier or a housing.
• An embodiment of the invention provides that the component is the planet carrier of the transmission device.
• the ball bearing is of the type a radial bearing and provided with at least one of the sun gear rotationally fixed first Wälzlaufbahn and at least one formed on an outer ring second Wälzlaufbahn and arranged radially between the Wälzlaufbahnen balls.
• the second Wälzlaufbahn on the outer ring surrounds the first Wälzlaufbahn concentric on the sun gear circumferentially.
• the inner Wälzlaufbahn is formed on a seated on / on the sun gear inner ring.
• the special feature of the invention is that the outer ring of the ball bearing is free to move radially relative to the component, so that the ball bearing is used against its original purpose only as a thrust bearing.
• the central axis of the transmission device is axially aligned. Radial is therefore transverse to the central axis.
• the outer ring of the ball bearing is preferably axially secured on both sides of the component, so that the sun gear is advantageously mounted axially in both axial directions.
• Conventional thrust bearing with effect in opposite axial directions consist in transmissions of two Axialnadel- or roller bearings, which are arranged on the left and right sides of the component to be stored. Accordingly, there are costs for the manufacture and installation of two bearings in the transmission. It must be provided space for two camps. In contrast, only installation space for a bearing is required in the transmission device according to the invention. The costs for the manufacture and assembly of the transmission device are considerably reduced due to the use of only one bearing. The internal friction of ball bearings is lower than that of thrust bearings. The expense of lubrication and cooling in the transmission device can be reduced by the use of ball bearings.
• the ball bearings can advantageously be offered as mass-produced catalog parts. They are well suited for use at high speeds. Since the outer ring is exposed, the ball bearing can not absorb radial forces but the axial forces are evenly distributed to all balls. The sun gear can center freely despite the use of a radial bearing, since the outer ring is released from the component. The permissible rated speeds of the ball bearings are much higher than those of axial needle roller bearings.
• the thrust bearings usually used for axial bearing are of the type of an axial needle bearing, which is formed from two axial discs and a needle ring.
• the rolling elements of the needle bearing are known to needles, which are guided in an axial cage. The rolling contact is accordingly designed as a line contact.
• these bearings have a relatively high axial load capacity.
• the internal friction of the thrust bearing is correspondingly high.
• the speeds of Axialnadel- or roller bearings due to the speed differences between the radial inside of the Axiallaufbahnen and the radial outer side of the Axiallaufbahnen limits.
• the coupled to the rotor shaft input shaft of the planetary gear is 1: 1 exposed to the drive speeds of the electric motors. Since the input shaft is the sun gear in this case, according to the prior art, an axial needle bearing must be designed accordingly for the high rotational speeds. This may be very difficult for the reasons mentioned above.
• the thrust bearing is very vulnerable because its load limits are already exhausted by speed limits. Axial loads resulting from tooth forces, which become even higher due to axial forces resulting from misalignment or tension, can therefore inevitably lead to premature failure of the bearings of the axial needle bearing type.
• the ball bearings used in the transmission device according to the invention preferably have one or more rows circumferentially adjacent balls. The ball centers of the balls of a row are at the same radial distance from the rotational axis of the ball bearing in a center-radial plane which is pierced perpendicularly by the rotational axis of the ball bearing and the central axis of the transmission shaft.
• the Wälzlaufbahnen the ball bearings are extending around the axis of rotation grooves which are formed axially between two annularly extending around the axis of rotation Borden.
• the grooves are shown in any longitudinal sections along the axis of rotation of the ball bearing as curves.
• the curves are curved on the shaft side of the inner Wälzlaufbahnen seen from the ball center from concave in the direction of rotation axis / shaft or housing side on the outer Wälzlaufbahnen viewed from the spherical center in the direction of housing concave curved.
• the curves are described in the simplest case each by a radius. This radius is larger than the sphere radius.
• the ratio of radius to spherical radius is called osculation.
• the grooves can be viewed in such longitudinal sections not only by a single radius, but with arbitrary curvature curves, for example by a plurality of subsequent curve sections with different chen radii described.
• the curves each have a vertex.
• the vertex is understood to be the point on the curve in the nominal state in the direction of loading, at which the curved line changes direction in its course.
• the type of ball bearings can be described on the basis of the intended orientation at rated load and on the number of its contact points and the resulting load direction during operation. A distinction is made between a nominal state with unloaded ball bearings and a loaded state with loaded ball bearings.
• the ball bearings are characterized by point contact of the balls with the Wälzlaufbahnen.
• the convexly curved surface of the ball is supported in the respective concave groove of the inner Wälzonnebahn and the outer Wälzlaufbahn each at least one contact point.
• the contact points of the two Wälzlaufbahnen are opposite to the ball center and can be connected to each other with an imaginary line.
• the pressure line runs through the center of the sphere.
• the angle formed in the nominal state of the ball bearing between the respective pressure line and the mid-point radial plane is called the nominal pressure angle.
• the supplementary angle to a 90 ° angle between the midpoint radial plane is accordingly the angle assumed between the pressure line and the central axis.
• a bearing load (force) resulting from radial and axial components is considered, which runs along this pressure line in the loaded state.
• one of the components may be zero.
• point contact changes to surface contact, which is idealized as a pressure ellipse.
• the extent of the pressure ellipse is dependent, among other things, on the height of the load and the dimension of the ball as well as the geometry of the rolling track.
• the respective pressure line passes through the area centroids of the elliptical surface of the two pressure ellipses and through the center of the sphere.
• the pressure line is inclined to the midpoint radial plane with an operating pressure angle that can deviate from the nominal pressure angle.
• the extent to which the operating pressure angle deviates from the nominal pressure angle depends on criteria such as the direction of action of the resultant, the operating clearance of the support, elastic deformations, the change in direction of the loads and the type of ball bearing.
• at least two types of the type radial ball bearings are provided, however, which are used for the axial mounting of the sun gear on the planet carrier.
• the invention provides for the use of at least one radial ball bearing, which may be a ball bearing with two-point contact and which is widely referred to as radial deep groove ball bearings or radial ball bearings.
• the pressure lines in the nominal state are initially aligned radially to the axis of rotation and intersect the axis of rotation in a common point.
• the inner Wälzlaufbahn and the outer Wälz- runway are concentrically arranged one inside the other, that the apexes of the concave curves of the two Wälzlaufbahnen face each other radially in the nominal state of the ball bearing in the center-radial plane, in which the ball centers are.
• the contact points lie in the radial plane on the vertices of the curves of Wälzlaufbahnen.
• the nominal pressure angle is 0 ".
• the resultant of the bearing load in radial ball bearings with two-point contact is directed perpendicular to the axis of rotation.
• This bearing load is distributed in radial ball bearings proportionally to only a few circumferentially adjacent balls of the ball bearing while others remain virtually unloaded.
• the pressure lines in the loaded balls are further aligned radially perpendicular to the axis of rotation and all extend in a radial plane.
• the respective operating pressure angle which is formed between the respective pressure line and the radial plane, corresponds to the nominal pressure angle and is 0 °.
• the Wälzlaufbahnen can move axially to each other and / or tilt relative to each other.
• the ball centers of the individual balls can be moved from the common radial plane into different adjacent radial planes.
• the resulting bearing load will lie on a pressure line which, depending on the load direction, is inclined on one side by an operating pressure angle greater than 0 ° to the radial plane and in the other direction by the corresponding supplementary angle between 0 ° and less than 90 ° to the axis of rotation.
• the axial component is distributed proportionally to the balls of the ball bearing.
• the radial component is distributed more or less proportionally to only a few circumferentially adjacent balls or due to the axial preload of the ball bearing by a sufficiently large axial component on all balls.
• the vertices the concave curves of the Wälzlaufbahnen shift axially depending on the bearing clearance, the osculation and the elastic deflection to each other such that the vertex of the inner Wälzlaufbahn another vertically pierced by the axis of rotation radial plane, as the respective vertex of the outer raceway. Accordingly, the pressure ellipse and its center of gravity shifts out of the common radial plane and the vertex and up at each board of the Wälzlaufbahn.
• a ball bearing with two-point contact can absorb only limited axial bearing loadings, Since the groove ball bearing is only axially loaded in the use according to the invention, the load is increased
• the groove ball bearing can be used at high speeds and has only low internal friction due to the two-point contact, but the groove ball bearing can only be used if the Expected axial forces are relatively low.
• a further and preferred embodiment of the invention therefore provides for the use of four-point ball bearings.
• the inner and outer Wälzlaufbahnen are divided in arbitrary longitudinal sections along the axis of rotation by the ball bearing and each described by two concave curves and two vertices. This may in each case be at a groove of an undivided bearing ring or at a "split" groove formed by two rings of a bearing ring, whereby the contact of the respective ball results in four points of contact at least in the nominal state
• the outer rolling raceway has two of these and two contact points provided on the inner Wälzlaufbahn.
• the grooves are arranged radially concentrically with one another such that in each longitudinal section through the ball bearing along the axis of rotation one vertex of the outer Wälzlaufbahn both a further vertex of the outer Wälzlaufbahn axially opposite and a vertex on the inner Wälzlaufbahn radially in a plane or slightly offset axially.
• the vertices of the inner Wälzlaufbahn have in the nominal state and the load state, the same radial distance from the axis of rotation, but are axially spaced from each other in different radial planes. These radial planes are adjacent axially to the midpoint radial plane. The same applies to the outer Wälzlaufbahn.
• each inner one Wälzlaufbahn and a vertex of the outer Wälzlaufbahn in a common radial plane which is pierced perpendicularly from the axis of rotation of the ball bearing.
• the vertices are contact points.
• the contact geometry is formed such that on each ball of the four-point ball bearing in each case a pressure line passes through a lying in a first radial plane contact point with the outer Wälzlaufbahn and a contact point with the inner Wälzlaufbahn in a second radial plane and a pressure line through a lying in the second radial plane Contact point with the outer Wälzlaufbahn and passes through a lying in the first radial plane of contact with the inner Wälzlaufbahn.
• the respective pressure line penetrates by definition the respective sphere center in the midpoint radial plane.
• the pressure lines emanating from one side intersect the axis of rotation of the four-point ball bearing or the central axis of the transmission device into a common point of intersection.
• the internal friction of the four-point ball bearings is normally relatively high, that is, under radial load or combined radial-axial load due to the four-point contact.
• exclusive axial load however, the two-point contact in the manner of an angular contact ball bearing results in the four-point ball bearing due to the operating clearance, so that this disadvantage is due to the use of the four-point ball bearing according to the invention can be excluded. It combines the advantages of high permissible rated speeds, lower internal friction of the two-point contact deep groove ball bearings with the high rigidity of a four-point radial bearing.
• FIG. 1 shows the drive unit 1 schematically simplified in a longitudinal section along the central axis 3 of the transmission device 2.
• FIG. 2 does not show to scale the detail Z of the transmission device 2 from the representation according to FIG. 1.
• the drive unit 1 has an electric motor drive 4, the rotor shaft 5 is operatively connected to a sun gear 6 of the transmission device 2 via a positive connection.
• the positive connection is e.g. produced by a spline, so that the sun gear 6 relative to the rotor shaft 5 is limited axially displaceable. This ensures that the bearing 28 of the rotor shaft 5 can not be acted upon by axial forces of the sun gear 6.
• the transmission device 2 is shown incomplete. Visible are a housing 7 and partially a planetary drive 8.
• the planetary drive 8 is formed at least from a planet carrier 10, from the sun gear 6 and a set planetary gears 9.
• the planet carrier 10 has two carrier plates 10a and 10b on which planet pins 9a are carried.
• the planet gears 9 sit on the planet pins 9a.
• the rotational axes of the sun gear 6 and the planet carrier 10 are each the central axis 3
• the sun gear 6 is axially supported or mounted with a thrust bearing 11 in the same direction with the central axis 3 on a component 34 of the transmission device 2.
• the thrust bearing 11 is seated on a shaft end of the sun gear 6 which is axially remote from the rotor shaft 5 and in the component 34.
• the component 34 is the planet carrier 10 in this exemplary embodiment.
• the planet carrier 10 has in a support plate 9b a housing bore 18 which is drilled in the material of the planet carrier 10, punched or introduced any other way.
• the thrust bearing 11 is a ball bearing 12.
• the ball bearing 12 has an inner Wälzlaufbahn 13 on an inner ring 14.
• the inner ring 14 is split and firmly seated on a stub shaft 6a of the sun gear 6.
• an inner Wälzlaufbahn 13 is formed, which is divided.
• the inner Wälzlaufbahn is introduced directly into the surface of the stub shaft 6a!
• the ball bearing 12 is provided with an outer ring 15 on which an outer Wälzlaufbahn 16 is formed.
• the outer ring 15 surrounds the inner ring 14 circumferentially about the central axis 3.
• the Wälzlaufbahnen 13 and 16 are arranged concentrically with each other.
• balls 17 are arranged in a row around the central axis 3 on the Wälzlaufbahnen 13 and 16 in a row. The axis of rotation of the ball bearing 12 and the central axis 3 are adjacent to each other.
• the outer ring 15 is radially free relative to the component 34 and axially fixed within a radial play S radially relative to the inner cylindrical surface 18 a movable axially but in both directions of the central axis 3 between a hedging ring 19 and a housing shoulder 18 b.
• the radial clearance S is composed according to the representation in Figure 2 from the gap dimensions S1 and S2 of an annular gap 20, each of which is ideally half of the radial clearance S.
• the sun gear 6 is centered on the planetary gears 9 so that its axis of rotation coincides exactly concentric with the central axis 3.
• the sun gear 6 is supported at only one bearing point in the transmission device 2, which has the ball bearing 12 as the only bearing. The advantage is that the sun gear 6 can thus center freely by tilting and / or parallel displacement to the central axis 3 in the context of the game.
• the ball bearing 12 is a four-point ball bearing, in which the ball centers 23 of the balls lie in a direction perpendicular to the image plane in the midpoint radial plane ME.
• the four-point ball bearing is in in the illustrated and along the central axis 3 extending longitudinal sections (see in particular Figure 2) by two imaginary, intersecting in the ball center 23 and thereby in each case a first contact point 24 of the ball with the inner Wälzlaufbahn 13 and a second contact point 25 with the outer Wälzlaufbahn 16 penetrating contact lines 21 and 22 characterized.
• E1 or E2 is a contact point 24 and 25.
• each of the contact lines is at an angle 90 °> ⁇ > 0 ° to the central axis, preferably at an angle 90 °> ⁇ > 55 ° inclined.
• the sun gear 6 depending on the loading direction by axial forces in an axial direction on the shaft shoulder 26 on the inner ring 14 and along the contact lines 22 via the outer ring 15 and support the locking ring 19 in the housing bore 18 or in the other axial direction via the locking ring 27 on the inner ring 14 and along the contact lines 21 via the outer ring 15 on the housing shoulder 18b.
• the selected angular range ensures that a standard four-point ball bearing, for example a catalog, can be used as the axial bearing and that the axial load capacity at high speeds is in optimum ranges.
• FIG. 1 The planet carrier 10 is rotatably mounted about the central axis 3 at a first bearing point 29 and a second bearing point 30 axially spaced from the first bearing point, and fixedly supported on the housing 7 in opposite axial directions.
• Each of the bearings 29 and 30 has an angular contact ball bearings 31 and 32.
• the respective angular contact ball bearings 31 and 32 is characterized in the longitudinal section of Figure 1 by contact lines 33 which are inclined at an angle 90 °> ⁇ > 0 ° to the central axis 3.
• the angular contact ball bearings 31 and 32 are set against each other so that the contact lines 33 intersect the central axis 3 in each case at an intersection point 35 which lies axially between the two bearing points 29 and 30.
• the ball bearing 12 is arranged concentrically to one of the angular contact ball bearings 32 so that it is surrounded by the angular ball bearing 32, so that the claimed by both ball bearings 12 and 32 axial space is advantageously reduced to the space requirement of only one ball bearing.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Rolling Contact Bearings (AREA)
• General Details Of Gearings (AREA)

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• 2016
  • 2016-11-07 DE DE102016221708.9A patent/DE102016221708B4/de active Active
  • 2016-11-07 CN CN201680073011.XA patent/CN108368933B/zh active Active
  • 2016-11-07 WO PCT/DE2016/200498 patent/WO2017101920A1/de active Application Filing

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