DE202016103794U1 - Transmission unit for a motor vehicle - Google Patents

Abstract

Transmission unit for a motor vehicle, with a about an axis of rotation (D) rotatable worm shaft (2) which cooperates in a along a distance axis (A) of the rotation axis (D) spaced engaging portion (4) with a worm wheel (3) and at a Housing (60) on the one hand of the engagement region (4) via a pivotable pivot bearing (7, 17, 27, 37) and on the other hand by a in the direction of the distance axis (A) biased loose pivot bearing (5) is mounted, wherein the pivotable pivot bearing (7 , 17, 27, 37) via a supporting device (10, 20, 30, 40) at least in the direction of the axis of rotation (D) on the housing (60) is supported, characterized in that the pivotable pivot bearing (7, 17, 27, 37) about a pivot axis (D) perpendicular to the axis of rotation (D) and the pivot axis (A) relative to the housing (60) is pivotable, and a Ausstützschwerpunkt (P1, P2) of the supporting device (10, 20, 30, 40) relative to the axis of rotation ( D) along the distance axis (A) to the engagement area (4) h is in offset.

Description

The invention relates to a transmission unit for a motor vehicle having the features of the preamble of claim 1, with a about an axis of rotation rotatable worm shaft which cooperates in a spaced along a distance axis from the axis of rotation engaging portion with a worm wheel and on a housing on the one hand of the engaging portion via a pivotable pivot bearing and on the other hand is supported by a biased in the direction of the distance axis loose rotary bearing, wherein the pivotable pivot bearing is supported via a supporting device at least in the direction of the axis of rotation of the housing.

Modern motor vehicles are usually equipped with a power steering, in which the steering movements of the driver are supported on the vehicle side or possibly even on the vehicle side a certain steering torque can be generated, which indicates the driver to a recommended steering movement. In addition to hydraulic power steering motor-driven power steering systems are used above all. In the latter, usually an electric servomotor with a drive shaft acts on a worm shaft, which in turn interacts with a worm wheel. The worm wheel sits on the actual steering shaft, which acts, for example. Via a pinion and a rack on a tie rod. Similar systems with servo motor, worm shaft and worm come in motor vehicles in other areas, such. B. in window regulators used.

Although theoretically under ideal conditions, even with a worm shaft rotating about a fixed axis, optimal engagement with the worm wheel would be possible, in practice it may be affected by manufacturing or assembly inaccuracies, wear effects, contamination and environmental influences such as humidity and temperature. That is, the o.g. Influences, alone or in combination, may cause the engagement between the worm shaft and worm wheel to be too loose and / or too tight. Too close engagement is problematic because it leads to increased friction, makes the gearbox stiff and increases wear.

A known prior art method of alleviating the problems presented is to support the worm shaft on a side facing the drive shaft via a first rolling bearing (normally a ball bearing) which allows some tilting movement transverse to the axial direction, while it is supported at the opposite end via a second rolling bearing, which is connected to a gear housing or the like via a spring which acts in the direction of the worm wheel. Thus, the worm shaft can pivot as needed about the first roller bearing to remain in an approximately constant engagement with the worm wheel.

The disadvantage here, however, that the pivoting is usually possible only over a larger game in the first bearing, which in turn leads to the fact that there vibrations and rattle associated with these can occur, which are undesirable under NVH aspects. Also, the precision of the transmission is impaired by the fact that in the region of the first rolling bearing, the axial and radial position of the worm shaft can not be set exactly. Reducing backlash in the area of the rolling bearing usually results in increased friction which can affect the precision of the control and also lead to increased wear. Furthermore, it is problematic that the point of application and the line of action of the force resulting from engagement with the worm wheel are offset to the worm shaft to its central axis. As a result, depending on the direction of rotation of the worm shaft results in a different degree of friction and efficiency of the transmission.

The US 2016/0031473 A1 discloses a bearing assembly for a transmission of a power steering. It is provided that a motor coupled to a worm shaft, which cooperates with a worm wheel, is mounted at an engine end by means of this bearing assembly, while it is supported at the opposite end by a loose ball bearing, that is acted upon by a spring element so that the Worm shaft is biased against the worm wheel. The bearing arrangement comprises a ball bearing, which is surrounded in the radial direction by a jacket element, which has a certain radial deformability and radially inwardly or outwardly has a convex cross section. About this jacket element and optionally via an intermediate elastic element, the ball bearing is supported on a transmission housing, whereby the worm shaft can be tilted together with the ball bearing against a transmission housing. Axially on both sides of the ball bearing between each pair of circumferential rings elastic elements are arranged.

At one in the US Pat. No. 7,490,695 B2 shown gear unit for a power steering a worm shaft is mounted at a motor distal end via a fixed bearing on a housing and tangentially biased by a bias pad and a torsion spring so that it remains in engagement with an associated worm wheel. At a close to the motor end, the worm shaft is over fixed ball bearing mounted on the housing, wherein the connection between the worm shaft and the ball bearing is given by a series of elastic elements which allow both an axial and a radial movement of the worm shaft. Furthermore, a tilting movement of the worm shaft relative to the housing is possible.

In the US 8,459,402 B2 a power steering is disclosed in which also a motor shaft is coupled to a worm shaft. The coupling is in this case given via a dog clutch, in which an elastic element between the two coupling parts is arranged. The worm shaft, which cooperates with a worm wheel, is supported at one end by a common ball bearing, which in turn is elastically mounted on a housing. At the other, the motor shaft end facing the worm shaft is mounted on a tilting bearing, which in turn is firmly connected to the housing. The balls of the tilting bearing run here in grooves whose inner radius is greater than the radius of the balls.

The US 6,725,964 B2 discloses a power steering system in which a rotor of a servomotor is coupled to a worm shaft, which in turn drives a worm wheel. According to one embodiment, the rotor engages with one end of a central shaft in a cup-like recess which is connected to the worm shaft. Furthermore, the rotor and the worm shaft are coupled to each other via a flexible coupling which serves to transmit a torque. The worm shaft is in this case mounted adjacent to the rotor via an associated coupling part and a first ball bearing on the gear housing and at an opposite end via a second ball bearing, which is biased by a spring in the direction of the worm wheel.

The US 7,201,075 B2 shows a further worm gear for a power steering, in turn, a worm shaft is mounted on a motor-side end and at a motor remote end via ball bearings on a transmission housing. At the remote end of the ball bearing is in turn connected via an eccentric mechanism with the gear housing. This mechanism allows adjustment of the position of the ball bearing transversely to the axial direction. This can be used, for example, to compensate for temperature or age-related changes in the dimensions of an associated worm wheel by adjusting the end remote from the worm gear to or away from it.

In view of the cited prior art, a gear unit with a worm gear provides room for improvement. This applies in particular to the engagement between the worm shaft and the worm wheel in terms of precision, wear and noise of the transmission.

The invention has for its object to optimize the engagement between a worm shaft and a worm wheel.

According to the invention the object is achieved by a gear unit with the features of claim 1, wherein the dependent claims relate to advantageous embodiments of the invention.

It should be noted that the features listed in the following description as well as measures in any technically meaningful way can be combined with each other and show other embodiments of the invention. The description additionally characterizes and specifies the invention, in particular in connection with the figures.

The invention provides a transmission unit for a motor vehicle. As motor vehicles are especially cars and trucks in question.

In particular, it may be a transmission unit for a power steering, although other applications, eg. For windows, electric seat adjustment or other eligible.

The gear unit has a worm shaft which is rotatable about an axis of rotation and which cooperates with a worm wheel in an engagement region spaced along a distance axis from the axis of rotation. The worm shaft is normally intended to be coupled directly or indirectly to a drive shaft of a servomotor to which it is approximately coaxial. In this case, a clutch arrangement can transmit a torque from the drive shaft to the worm shaft. The worm shaft in turn meshes with the worm wheel, whereby a reduction of the rotational movement of the drive shaft is usually achieved. Since the worm shaft and in particular a worm formed thereon have a certain diameter, the engagement region, ie the region in which the actual force transmission from the worm shaft to the worm wheel takes place, is spaced transversely to the axis of rotation thereof. The direction of the distance here defines the said distance axis. It is understood that a center of the worm wheel along this distance axis is spaced from the axis of rotation. Normally, the distance axis is perpendicular to the axis of rotation.

The worm shaft is in this case mounted on a housing on the one hand of the engagement region via a pivotable pivot bearing and on the other hand by a biased in the direction of the distance axis loose rotary bearing, wherein the pivotable pivot bearing is supported via a support device at least in the direction of the axis of rotation of the housing. The housing in this case forms a reference frame which is normally stationary relative to the vehicle and over which the relative positions of the movable gear parts are at least partially defined. The housing may be formed one or more parts. It may be more or less open, in which case it could also be called a "frame" or the like. It is also possible that the transmission components mentioned here, possibly together with other transmission components, are largely enclosed by the housing. The rotation of the worm shaft is of course given to the housing and is realized via the pivotable pivot bearing and the loose pivot bearing. The pivot bearings are usually rolling bearings, in particular ball bearings. If appropriate, however, at least one of the rotary bearings could also be designed as a sliding bearing. The two pivot bearings are on the one hand and on the other hand of the engagement region, that is, the engagement region is located along the worm shaft between the two pivot bearings. Normally, the pivot bearings are at opposite ends or in the area of opposite ends of the worm shaft.

On the one hand, the worm shaft is therefore mounted via a pivotable pivot bearing, which is supported on the housing via a support device at least in the direction of the axis of rotation. The support device is in this case arranged at least partially between the pivotable pivot bearing and the housing and serves to absorb forces acting at least in the direction of the axis of rotation. D. h., The support in the direction of the axis of rotation refers to the direction of the forces acting in the support forces and does not necessarily mean that the support device must be arranged in the direction of the axis of rotation between the pivotable pivot bearing and the housing. If one defines an axial direction over the axis of rotation, one can also speak of the fact that the supporting device absorbs at least axial forces. In this respect, the support device determines the axial rigidity of the connection of the worm shaft to the housing to a considerable extent.

On the other hand, the worm shaft is mounted on the loose pivot bearing on the housing. Here, the loose pivot bearing is biased in the direction of the spacer axis, which can be done, for example, via an elastic biasing element, which is arranged between the housing and the loose pivot bearing. This may be a spring made of metal or fiber-reinforced plastic or else an element consisting of an elastomer. Due to the bias of the pivot bearing bias of the worm shaft is given in the direction of the worm wheel out. The corresponding bias acts to ensure that the worm shaft remains in engagement with the worm wheel, wherein a corresponding biasing element due to its elastic property can simultaneously allow a certain deflection of the worm shaft, whereby the frictional forces between the worm shaft and worm wheel can be limited. The loose pivot bearing may in particular be designed as a movable bearing, which can move within a certain range at least in the direction of the distance axis.

According to the invention, the pivotable pivot bearing is pivotable relative to the housing about a pivot axis perpendicular to the axis of rotation and to the distance axis and a support center of gravity of the support device is offset from the axis of rotation along the distance axis to the engagement region. About the pivoting movement of the pivotable pivot bearing and the worm shaft on which the pivotable pivot bearing is arranged, tilted relative to the housing. Instead of "panning" you can of course also speak of "tilting". The worm shaft can perform a necessary pivoting movement, if it follows, for example, a temporally and / or locally uneven outer radius of the worm wheel on the one hand and the bias voltage by the biasing member on the other hand. Since the pivotable pivot bearing can pivot with respect to the housing as a whole, it is unnecessary in contrast to the prior art, for this purpose, for example, to provide a ball bearing, which must be equipped with appropriate clearance to allow the pivoting. In the present case, the rotary bearing can be configured without clearance, which improves the precision of the transmission and eliminates a possible source of noise. It is understood that the pivoting of the pivotable pivot bearing relative to the housing is wholly or partially realized via the support device. In other words, the support device is at least designed such that it allows the described pivoting. Depending on the type of connection between the pivotable pivot bearing and the housing or depending on the design of the support device, it may be that the position of the pivot axis is not clearly defined by this.

According to the invention, the center of gravity of the support device is offset relative to the axis of rotation, along the spacing axis in the direction of the engagement region. This includes in particular the possibility that the support center of gravity lies along the distance axis at the level of the engagement region. Of the Abstützschwerpunkt results as the focus of all points over which the support device is supported in the direction of the axis of rotation. D. h., In the case of a circular and planar supporting support device of the Abstützschwerpunkt would, for example, in the middle of the circular area. For example, if the support is given over four points lying on the corners of an imaginary square, the center of gravity of support would be in the middle of the square. In all cases where the support is symmetrical to a certain point, this point is the center of gravity. For a non-symmetrical support, a centroid may need to be determined. Although a center of gravity is mentioned here, it is necessary in many cases to differentiate two center of gravity, one of which is decisive for a force acting in the direction of the axis of rotation in one direction and the other for a force acting in the direction of the axis of rotation in the opposite direction. In these cases, the above statements apply to each of the two support focuses.

It is preferred that the pivot axis (along the distance axis) is at the level of the center of gravity. D. h., In this case, the pivotable pivot bearing and thus the worm shaft does not tilt or pivot about an axis which intersects the axis of rotation, but this is offset. Due to the interaction of worm and worm wheel, an axial force component (parallel to the axis of rotation) and a radial force component (perpendicular to the axis of rotation) act in the engagement region. The radial force component must be compensated by the bias of the biased loose pivot bearing. The total force leads with respect to the pivot axis in each case to a torque whose direction is dependent on the direction of rotation. Runs the pivot axis through the axis of rotation as in the prior art, resulting in magnitude greatly different torques, since the distance of the line of action of each force differs significantly from the pivot axis. If, however, the pivot axis is offset in the direction of the engagement region and is located in particular along the distance axis at the height of the engagement region, the lever arms of the forces arising in the engagement region are the same and there are torques of the same size. Thus, the radial force component is the same for both directions of rotation, causing the vehicle to behave symmetrically in right and left turns (or on street stimuli, eg, cobblestones). Thus, it is also possible in this way to avoid uneven loading and thus uneven wear depending on the direction of rotation of the worm shaft.

In order to support the pivotability of the pivotable pivot bearing and at the same time to suppress the formation or propagation of noise, the support device is preferably formed at least partially elastic. D. h., At least parts or portions of the support device are elastic and thus allow a degree of flexibility.

In many cases, for reasons of production technology alone, it makes sense to form the supporting device symmetrically. In this case, it is preferable for an axis of symmetry and / or plane of symmetry of at least part of the supporting device to extend through the engagement region. This may be an axis of symmetry or plane of symmetry of the entire supporting device or possibly only those parts of the supporting device which have a significant influence on the position of the supporting centers. In other words, such parts that transmit, for example, only forces transverse to the axis of rotation or serve only the connection of the support device to the pivot bearing can be disregarded in this respect. It is understood that in such a symmetrical arrangement of the Ausstützschwerpunkt along the distance axis is at the level of the engagement region. It can be said here that the symmetrical support device is displaced eccentrically to the axis of rotation in the direction of the engagement region.

There are a variety of ways to realize the support device. Some of these options, which may possibly be combined with each other, are discussed below.

According to one embodiment, the supporting device comprises at least one rubber-elastic ring. Such a rubber-elastic ring, which may be inexpensively made of a corresponding elastomer, can be arranged between the pivotable pivot bearing and the housing, wherein its center is not on the axis of rotation, but is displaced in the direction of the engagement region. In particular, as already indicated above, the axis of symmetry of the ring, which runs through its center, extend through the engagement region.

Advantageously, the support device comprises at least one rubber-elastic ring in the direction of the axis of rotation on both sides of the pivotable pivot bearing. These two rings can be dimensioned the same and their centers or axes of symmetry are preferably arranged eccentrically to the same extent with respect to the axis of rotation. In this way, the support is the same regardless of the direction of the force acting along the axis of rotation. While the rings mentioned define or at least significantly influence the axial rigidity, ie the stiffness along the axis of rotation, the stiffness in the radial direction can additionally be influenced by the fact that the Supporting device comprises a rubber-elastic ring transverse to the axis of rotation on the outside of the pivotable pivot bearing. Such an outside ring does not influence the position of the center of gravity or only insignificantly and can therefore also be arranged coaxially to the axis of rotation in the context of the invention. In order to ensure the correct positioning of the rubber-elastic rings, grooves may be provided for receiving the same. Such a groove can be formed on the sides of the pivot bearing (for example, in an outer bearing ring of a ball bearing) and / or on the sides of the housing. It is understood that in the case of eccentrically arranged rings and the corresponding groove must be formed eccentrically to the axis of rotation.

Alternatively to the embodiment with the rubber-elastic ring arranged on the outside, the pivotable rotary bearing has a spherical outer contour which is offset eccentrically with respect to the axis of rotation. The outer contour, which thus forms part of a spherical surface, is in this case rotationally symmetrical with respect to an axis of symmetry which is offset along the distance axis in the direction of the engagement region and preferably extends through the latter. The symmetry axis of the outer contour is preferably identical to the axis of symmetry of the rings arranged in the direction of the axis of rotation on both sides of the pivotable pivot bearing. The spherical, convex outer contour of the rotary bearing preferably corresponds with a spherical, concave inner contour of the housing.

According to a further embodiment, the pivotable pivot bearing has an outer contour eccentrically offset with respect to the axis of rotation, wherein the supporting device engages in the region of the outer contour on the pivotable pivot bearing. In one embodiment, in which the pivotable pivot bearing is designed as a roller bearing, an outer bearing ring of the same with respect to the axis of rotation eccentrically offset outer contour and the support device engages in the outer contour on the outer bearing ring. D. h., While the inner contour of the outer bearing ring (or in the more general case of the pivotable pivot bearing), of course, for concentricity concentric with the axis of rotation, the outer contour is eccentrically offset, whereby in this case the eccentric displacement of the support device is favored. This engages in the region of the outer contour of the bearing ring (or on the pivotable pivot bearing). The outer contour may in this case have a groove, a projection, a flange or the like, which serve the positive connection with the support device. In order to avoid an unwanted misalignment of the pivot bearing, this is preferably arranged rotationally fixed relative to the housing.

In particular, in this case, the support device comprise two annular spring elements which are arranged in the direction of the axis of rotation on both sides of a flange of the pivotable pivot bearing. The flange may extend in this case in particular within a plane transverse to the axis of rotation. The outer contour of the flange can basically be shaped differently, in particular, it can be circular. In the case of a roller bearing described above, the flange is formed on the outer bearing ring. The spring elements may in particular be plate springs or corrugated springs, by means of which the flange can be acted upon on both sides. It should be noted that in principle here as well as in the embodiments to be described below in principle combinations are conceivable that, for example, on one side of the flange, a plate spring (or other spring) is provided, while on the other side of the pivot bearing a rubber-elastic ring is provided.

According to a further embodiment, the supporting device comprises an elastic metal clamp, which partially surrounds the pivotable pivot bearing. The metal clip may in this case be made of sheet metal and / or of wire. In order to secure the position of the metal clip with respect to the pivotable pivot bearing, a positive connection can be made directly or indirectly (via an intermediate element). For this purpose, the metal clip may, for example, have inwardly directed projections, which may be formed by a bend of the wire or sheet. In this case, the projections preferably lie in a plane which runs parallel to the axis of rotation and to the pivot axis and which lies along the distance axis at the level of the engagement region. It is also possible that the metal clip in a material-saving manner rather has the shape of a clasp and extends in total only in said plane. In this way, the points in which the pivot bearing is supported by the metal bracket on the housing, also in the said plane, which thus of course also applies to the or the Ausstützschwerpunkte. Insofar, as the worm shaft must be passed through the metal clamp, this surrounds the pivotable pivot bearing in each case only partially. The metal clip may be formed in one or more parts. In particular, it may consist of two identical halves, which are placed together during assembly.

It is possible that the metal clip with the above-described projections in grooves or recesses of the pivotable pivot bearing, for example. The first outer bearing ring, engages. In particular, when a standard bearing is to be used, the pivotable pivot bearing may be surrounded by an inelastic capsule unit against which the metal clamp rests on the outside. The Capsule unit preferably surrounds the pivotable rotary bearing at least partially positively and may have on its outer side a number of continuous or non-continuous recesses into which the metal clip can engage positively. The essential purpose of the capsule unit is to form a kind of adapter between a standard bearing and the metal clip.

According to a further, normally alternative embodiment, the supporting device comprises a holding arrangement lying on the outside of the pivotable pivot bearing, from which elastic connecting sections extend along the pivot axis, via which the clamping arrangement is connected to the housing. Such a holding arrangement can, for example. Made of sheet metal and form-fitting border the pivotable pivot bearing. In the case of a rolling bearing, the holding arrangement bears against the outer bearing ring. The connecting portions may be integrally formed therefrom of sheet metal. Preferably, the connecting portions form the only connection with the housing and thus also define the Ausstützschwerpunkte. They are therefore arranged offset from the axis of rotation in the direction of the engagement region. The part of the holding arrangement that produces the actual positive connection with the pivot bearing can - as well as the pivot bearing itself - be formed concentrically to the axis of rotation.

Preferably, the holding arrangement comprises a first and a second holding part, which bear against each other in the region of the connecting portions. The connecting portions may be integrally formed with one of the two holding parts, or each one part of a connecting portion may be integrally formed with the first holding part and another part may be formed integrally with the second holding part. The two holding parts can be connected to each other, for example by a positive connection or by a material connection. Each holding part may have an axially extending and tangentially circulating around the axis of rotation semicircular holding portion, followed by the radially inwardly directed flange portions. In particular, the connecting sections may be sheet metal sections which extend in a plane with the axis of rotation and the pivot axis. The stiffness of the staple assembly in different directions can be adjusted via various measures.

According to a preferred embodiment, tapered sections are formed in a region of the connecting sections facing the rotary bearing, wherein an incision is formed in the axial direction on at least one side of a tapered section. This allows the elasticity to increase about the pivot axis. According to a further embodiment, in the region of the connecting sections facing the rotary bearing, stiffening webs are formed which are either molded into the metal sheet or z. B. soldered or welded thereto. Such stiffening webs may in particular extend transversely to the axis of rotation. By this measure, the rigidity in the direction of the distance axis can be increased. The rigidity of the holding arrangement in the radial direction (that is to say transversely to the axis of rotation) can be increased by forming an inwardly directed bead into the metal sheet in a section of the holding arrangement arranged on the outside of the rotary bearing.

Further advantageous details and effects of the invention are explained in more detail below with reference to exemplary embodiments illustrated in the figures. Show it:

1 a schematic partial sectional view of a first embodiment of a transmission unit according to the invention;

2 a schematic partial sectional view of a second embodiment of a transmission unit according to the invention;

3 a schematic partial sectional view of a third embodiment of a transmission unit according to the invention;

4 a schematic partial sectional view of a fourth embodiment of a transmission unit according to the invention;

5 a sectional view of a part of the transmission unit 4 according to the line VV;

6 a perspective view of a portion of a fifth embodiment of a transmission unit according to the invention; such as

7 a sectional view of the part of the transmission unit 6 , In the different figures, the same parts are always provided with the same reference numerals, which is why these are usually described only once.

1 shows in a partial sectional view of a first embodiment of a transmission unit according to the invention 1 , which can be used for example in a power steering of a car. The illustration is partially simplified and schematic.

The gear unit 1 has a about a rotational axis D rotatably mounted worm shaft 2 and a worm wheel 3 on, as well as the worm shaft 2 opposite a housing 60 is rotatably mounted. Although the case 60 Here, in one piece, it may in reality consist of several parts that are rigidly connected. A snail 2.3 the worm shaft acts in this case in an engagement area 4 with a sprocket 3.1 of the worm wheel 3 together. The engagement region is spaced apart from the axis of rotation D along a distance axis A perpendicular to the axis of rotation. The worm shaft 3 is at a first end 2.1 via a coupling shown here only schematically 62 with a drive shaft 61 connected to a servomotor, not shown.

Furthermore, the worm shaft 3 in the area of the first end 2.1 over a first ball bearing 7 and a support device 10 on the housing 60 stored. The first ball bearing 7 includes an inner bearing ring 8th and an outer bearing ring 9 , Both bearing rings 8th . 9 are formed substantially concentric with the axis of rotation D. However, in the outer bearing ring 9 on opposite ends two circumferential grooves 9.1 . 9.2 formed, which are arranged offset in the direction of the distance axis A eccentric to the rotation axis D, so that its axis of symmetry S1 through the engagement region 4 runs. On an outside of the outer bearing ring 9 is another groove 9.3 educated. In all grooves 9.1 . 9.2 . 9.3 are rubber-elastic rings 11 . 12 . 13 introduced, which is the supporting device 10 form. It is understood that a support against axial forces, ie forces acting parallel to the axis of rotation D, almost exclusively by the eccentrically arranged rings 11 . 12 he follows. This results in Ausstützschwerpunkte P1, P2, which lie on the axis of symmetry S and thus along the distance axis A at the level of the engagement region 4 , Although the first ball bearing 7 is formed essentially free of play, the worm shaft 2 together with the ball bearing 7 (To a small extent) are pivoted about the specified pivot axis K.

Due to the elastic storage by the rubber-elastic rings 11 . 12 . 13 is the first ball bearing 7 opposite the housing 60 pivotable about a pivot axis K, which is perpendicular to the axis of rotation D and the distance axis A.

Although the course of the pivot axis K is not completely clearly defined, this is approximately, as shown in the figure, at the height of the axis of symmetry S1 and thus also at the height of the engagement region 4 , It should be noted that the rings arranged at the end faces 11 . 12 of course, also affect the rigidity of the connection in the direction of the axis of rotation D, while the externally arranged ring 13 Significant influence on the rigidity of the connection transverse to the axis of rotation D, ie in the radial direction, has.

At one the first end 2.1 opposite second end 2.2 is the worm shaft in a second ball bearing 5 stored, via a spring shown here schematically 6 with a housing 60 connected is. By the spring 6 is the worm shaft 2 against the worm wheel 3 biased. As a result, in cooperation with the pivotable mounting of the worm shaft 2 ensured that there is always an optimal engagement between the worm shaft 8th and the worm wheel 11 consists.

During normal operation of the gear unit 1 the snail acts 2.3 with the sprocket 3.1 together, resulting in a parallel to the axis of rotation D acting force component, depending on the direction of rotation (clockwise, counterclockwise) on the first end 2.1 or the second end 2.2 is directed. As the intervention area 4 offset in the direction of the distance axis A relative to the rotational axis D, these forces would lead to a torque with respect to a pivot axis which intersects the axis of rotation D. However, because of the eccentric arrangement of the rings 11 . 12 the Ausstützschwerpunkte P1, P2 at the level of the engagement area 4 lie, results in the present transmission unit 1 no such torque. This leads to a transmission efficiency that is independent of the direction of rotation and to a uniform wear of the respective sides of the worm 2.3 and sprocket 3.1 ,

2 shows a second embodiment of a transmission unit according to the invention 1 , which predominantly with the in 1 corresponds embodiment shown and will not be explained again. In this case, the worm shaft 2 at the first end 2.1 over a ball bearing 47 stored, that a symmetrical to the rotation axis D inner bearing ring 48 includes and an outer bearing ring 49 , which is rotationally symmetrical on the inside and constructed coaxially to the axis of rotation D, but a spherical outer contour offset therefrom 49.3 having. This is rotationally symmetrical to the symmetry axis S2, through the engagement area 4 runs. In contrast to 1 has the outer bearing ring 49 only two frontal grooves 49.1 . 49.2 on where rubber-elastic rings 11 . 12 are arranged, which are arranged rotationally symmetrical to the axis of symmetry S2. It is understood that the support centers S1, S2 here as in 1 are arranged. The convex, spherical outer contour 49.3 is in a concave, spherical inner contour 60.1 of the housing 60 added.

3 shows a third embodiment of a transmission unit according to the invention 1 , which predominantly with the in 1 corresponds embodiment shown and will not be explained again. In this case, the worm shaft 2 at the first end 2.1 over a ball bearing 17 mounted, the one symmetrical to the rotation axis D inner bearing ring 18 includes and an outer bearing ring 19 , which is also rotationally symmetrical on the inside and constructed coaxially with the axis of rotation D, but an outer contour offset therefrom 19.1 having. This is also rotationally symmetrical overall, but to an axis of symmetry S2, by the engagement area 4 runs. At this outer contour 19.1 is a radially extending flange 19.2 educated. The flange 19.2 is in turn via a supporting device 20 on the housing 60 supported, consisting of two annular disc springs 21 . 22 is formed. The disc springs 21 . 22 are of course arranged symmetrically to the symmetry axis S2. In this way, in turn result Ausstützschwerpunkte P1, P2, along the distance axis A at the level of the engagement area 4 lie. Approximately between the center of gravity in P1, P2, a pivot axis K is located around which the first ball bearing 17 opposite the housing 60 is pivotable. Instead of the cup springs 21 . 22 also corrugated springs can be used.

While in the embodiment in 1 the outer bearing ring 9 apart from the grooves 9.1 . 9.2 . 9.3 It is of course alternatively possible to provide an eccentrically offset outer contour there as well, which is concentric to the grooves 9.1 . 9.2 runs.

The 4 and 5 show a further embodiment of a transmission unit according to the invention 1 , which in turn are predominantly identical to the one in 1 illustrated embodiment. However, in this case, the worm shaft 2 over a first ball bearing 27 stored, that of an inelastic capsule unit 33 is enclosed. The capsule unit 33 in turn is about a designed as a metal bracket support device 30 on the housing 60 supported. As in the sectional view according to 5 can be seen, is the support device 30 essentially two pieces of wire 31 . 32 formed, which are identical, but arranged rotated by 180 ° to each other. You could also speak of a clip or the like instead of a metal clip. Each of the pieces of wire 31 . 32 engages with a series of inward protrusions 31.1 . 32.1 in this provided recesses 33.1 the capsule unit 33 and establishes a positive connection. As in 4 can be seen, resulting in total support centers P1, P2, which lie in a direction parallel to the axis of rotation D and to a pivot axis K symmetry plane S3 of the support device 30 lie. Alternatively to the embodiment shown here could also on the capsule unit 33 be omitted and it could instead recesses within the outer race 29 be provided, in which the pieces of wire 31 . 32 intervention. Due to the elasticity of the metal clip, on the one hand, the pivotability is supported and, on the other hand, impact loads can be cushioned.

6 and 7 show a part of a further embodiment of a transmission unit according to the invention, with respect to the parts not shown substantially the embodiment in 1 equivalent. Here is a first ball bearing 37 provided that an inner bearing ring 38 and an outer bearing ring 39 includes, which are formed rotationally symmetrical to the rotation axis D. The outer bearing ring 39 is positively in a supporting device 40 taken, which has the form of a holding arrangement. It consists of a first holding part 41 and a second holding part 42 , which are each configured approximately omega-shaped. Both holding parts 41 . 42 are formed of sheet metal. An approximately semicircular holding section 41.1 . 42.1 , on the front side flange portions 41.2 . 42.2 are arranged, serves for the positive reception of the ball bearing 37 , The two holding parts abut one another in a region in which planar connecting sections 41.3 . 42.3 are formed, which abut each other. These connection sections 41.3 . 42.3 are offset from the axis of rotation D along the distance axis A such that they are at a level with the (not shown here) engagement region 4 lie. They serve the housing-side connection or support of the support device 40 , A pivot axis K extends between the connecting portions 41.3 . 42.3 therethrough. The pivot axis K and a parallel to the axis of rotation D through the engagement area 4 extending symmetry axis S4 form approximately symmetry axes of the through the connecting sections 41.3 . 42.3 formed part of the supporting device 40 , At the intersection of the pivot axis K with the axis of symmetry S4 is the Ausstützschwerpunkt P1. In order to increase the elasticity with respect to a pivoting action about the pivot axis K, are in the connection area between the connecting portions 41.3 . 42.3 to the holding sections 41.1 . 42.1 tapered sections 41.4 formed by incisions 41.5 flanked. In order to simultaneously increase the rigidity against displacements in the direction of the distance axis A are at the tapered portions 41.4 Stege 41.6 soldered or molded. As in the sectional view in 7 can be seen, the radial stiffness of the holding portions 41.1 be improved by having a radially inwardly extending bead 41.7 is formed.

LIST OF REFERENCE NUMBERS

1

 gear unit

2

 worm shaft

2.1

first end

2.2

second end

2.3

slug

3

 worm

3.1

sprocket

4

 engagement area

5, 7, 17, 27, 37, 47

 ball-bearing

6

 feather

8, 18, 28, 38, 48

 inner bearing ring

9, 19, 29, 39, 49

 outer bearing ring

9.1, 9.2, 9.3, 49.1, 49.2

 groove

10, 20, 30, 40, 50

Support device

11, 12, 13

 rubber-elastic ring

19.1, 49.3

 outer contour

19.2

 flange

21, 22

 Belleville spring

31, 32

 piece of wire

31.1, 32.1

 head Start

33

 capsule unit

33.1

 recess

41, 42

 holding part

41.1, 42.1

 holding section

41.2, 42.2

 flange

41.3, 42.3

 connecting portion

41.4

 tapered section

41.5

 incision

41.6

 web

41.7

 Beading

60

 casing

60.1

 inner contour

61

 drive shaft

62

 clutch

A

 distance axis

D

 axis of rotation

K

 swivel axis

P1, P2

 Abstützschwerpunkt

S1, S2, S4

 axis of symmetry

S3

 plane of symmetry

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• US 2016/0031473 A1 [0006]
• US 7490695 B2 [0007]
• US 8459402 B2 [0008]
• US 6725964 B2 [0009]
• US 7201075 B2 [0010]

Claims (10)

Gear unit for a motor vehicle, with a about a rotational axis (D) rotatable worm shaft ( 2 ), which in an engagement region spaced along a distance axis (A) from the rotation axis (D) (US Pat. 4 ) with a worm wheel ( 3 ) and that on a housing ( 60 ) on the one hand the engagement area ( 4 ) via a pivotable pivot bearing ( 7 . 17 . 27 . 37 ) and on the other hand by a in the direction of the distance axis (A) biased loose pivot bearing ( 5 ), wherein the pivotable pivot bearing ( 7 . 17 . 27 . 37 ) via a supporting device ( 10 . 20 . 30 . 40 ) at least in the direction of the axis of rotation (D) on the housing ( 60 ), characterized in that the pivotable pivot bearing ( 7 . 17 . 27 . 37 ) about an axis of rotation (D) and to the distance axis (A) vertical pivot axis (K) relative to the housing ( 60 ) is pivotable, and a supporting center of gravity (P1, P2) of the supporting device ( 10 . 20 . 30 . 40 ) relative to the axis of rotation (D) along the distance axis (A) to the engagement area ( 4 ) is offset. Transmission unit according to claim 1, characterized in that an axis of symmetry (S1, S2, S4) and / or plane of symmetry (S3) of at least part of the supporting device ( 10 . 20 . 30 . 40 ) through the engagement area ( 4 ) runs. Transmission unit according to claim 1 or 2, characterized in that the supporting device ( 10 . 20 . 30 . 40 ) at least one rubber-elastic ring ( 11 . 12 . 13 ). Transmission unit according to one of the preceding claims, characterized in that the pivotable pivot bearing ( 7 . 17 . 27 . 37 ) with respect to the axis of rotation (D) eccentrically offset outer contour ( 19 .1), wherein the supporting device ( 10 . 20 . 30 . 40 ) in the area of the outer contour ( 19.1 ) on the pivotable pivot bearing ( 7 . 17 . 27 . 37 ) attacks. Transmission unit according to one of the preceding claims, characterized in that the supporting device ( 10 . 20 . 30 . 40 ) two annular spring elements ( 21 . 22 ), which in the direction of the axis of rotation (D) on both sides of a flange ( 19.2 ) of the pivotable pivot bearing ( 7 . 17 . 27 . 37 ) are arranged. Transmission unit according to one of the preceding claims, characterized in that the supporting device ( 10 . 20 . 30 . 40 ) an elastic metal clip ( 30 ) comprising the pivotable pivot bearing ( 7 . 17 . 27 . 37 ) partially surrounds. Transmission unit according to one of the preceding claims, characterized in that the pivotable pivot bearing ( 7 . 17 . 27 . 37 ) of an inelastic capsule unit ( 33 ) is surrounded, on which the metal bracket ( 30 ) on the outside. Transmission unit according to one of the preceding claims, characterized in that the supporting device ( 10 . 20 . 30 . 40 ) an outside on the pivotable pivot bearing ( 7 . 17 . 27 . 37 ) adjoining holding arrangement ( 40 ), of the along the pivot axis (K) elastic connecting portions ( 41.3 . 42.3 ), via which the holding arrangement ( 40 ) is connected to the housing. Transmission unit according to claim 8, characterized in that the holding arrangement ( 40 ) a first ( 41 ) and a second holding part ( 42 ), which in the region of the connecting sections ( 41 .3, 42 .3) abut each other. Transmission unit according to claim 9 or 10, characterized in that in a pivotable pivot bearing ( 7 . 17 . 27 . 37 ) facing portion of the connecting portions ( 41.3 . 42.3 ) tapered sections ( 41.4 ) are formed, wherein in the axial direction on at least one side of a tapered portion ( 41.4 ) an incision ( 41.5 ) is trained.

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