DE102016211715A1 - Transmission unit for a motor vehicle - Google Patents

Abstract

The invention relates to a transmission unit (1) for a motor vehicle, having a worm shaft (2) which is rotatable about an axially extending axis of rotation (D) and which is mounted on a housing (30) via a pivot bearing (5) pivotable about a pivot axis (S) , which is received with a spherical outer surface (7.1) in a stationary pivot ring (4). In order to optimize the engagement between a worm shaft and a worm wheel, the transmission unit (1) has a tangentially at least partially about the axis of rotation (D) around extending spring element (8, 9) extending in the axial direction on the one hand on the housing (30) and on the other hand with two mutually in the direction of the pivot axis (S) opposite, axially projecting abutment sections (8.2, 9.2) on the pivot bearing (5) is supported.

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 axially extending axis of rotation rotatable worm shaft which is mounted on a housing via a pivotable about a pivot axis pivot bearing, which with a spherical outer surface in a stationary pivot ring recorded,

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 case, 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 in the prior art method to alleviate the problems presented, is to support the worm shaft on a side facing the drive shaft via a first rolling bearing (usually a ball bearing), which allows a certain pivotal movement transverse to the axial direction, while on is mounted on a second roller bearing, which is connected to a transmission housing or the like via a spring, which acts on it 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. An alternative solution is to use a pivot bearing, wherein the actual rolling bearing has a spherical outer surface and is received in a stationary attached to the housing pivot ring, which has a concave, usually also spherical inner surface. Although this allows a pivoting realize without the actual rolling bearing must have unnecessary play, however, due to the design of the pivot bearing, the pivot axis is not exactly defined. In addition, the rigidity of the system to axial displacements is generally low and can not be targeted. This in turn suffers the precision of the transmission and the engagement of the worm shaft with the worm wheel is not optimal. The engagement of the teeth under load is usually not optimal and by the corresponding gear play audible and unwanted rattling noises.

The US 2014/0029884 A1 discloses a bearing assembly for a power steering. A worm shaft, which meshes with a worm wheel, is connected to transmit torque to a motor shaft. The motor shaft is mounted on a housing via two ball bearings. On a side facing the worm shaft, an annular wave spring is arranged between the housing and the ball bearing, which biases the outer bearing ring of the ball bearing of the worm shaft. The wave spring is located on the inside of the motor shaft and has a plurality of outwardly directed convex projections, with which it rests on the outside of the housing.

The US 7,575,090 B2 shows a transmission for a power steering, in which a worm shaft cooperates with a worm wheel. The worm shaft is in each case mounted in end areas via ball bearings on a housing. In several embodiments shown, a threaded portion of the worm shaft is biased on both sides in the axial direction via disc springs against the inner bearing rings of the respective ball bearings, so that elastically received during interaction with the worm wheel forces can be. The disc springs each have inwardly directed, slightly inclined relative to the radial direction portions, followed by the radially extending abutment portions, with which the plate spring rests against the inner bearing ring.

The US 6,179,473 B1 shows a rolling bearing, for example. For the steering column of motor vehicles, with an outer ring and an inner ring, between which a number of rolling elements are arranged. Furthermore, a compensation ring is provided, via which the inner ring is connected to the steering shaft of the steering column, and a lock washer, which acts on the one hand on the steering shaft and on the other hand, the rolling bearing acts on the balance ring in the axial direction. Optionally, a wave spring may be interposed between the lock washer and the balance ring, or the lock washer may in turn have elastic structures pointing in the direction of the balance ring.

The US 8,539,849 B2 shows a transmission for a power steering with a worm wheel and a worm shaft. The worm shaft is supported at an end facing a motor shaft via a pivot bearing in which an outer bearing ring has a spherical convex outer surface received in a corresponding concave inner surface of a pivot ring. At an opposite end, the worm shaft is biased toward the worm shaft via an ordinary ball bearing, which is designed as a force-loaded floating bearing. In order to reduce axial play within the pivot bearing, an annular spring element is provided on one of the motor shaft side facing between the pivot bearing and the gear housing having a radially inwardly directed and axially projecting nose, exerted on the axial axial bias on the outer bearing ring becomes.

The US 8,667,858 B2 shows a steering gear in which a motor acts on a worm wheel via a worm shaft. The worm shaft is mounted at a motor remote end via a floating bearing and at a near-motor end via a ball bearing, which is accommodated in a holder, which in turn is attached to the transmission housing. In order to enable a pivoting movement of the worm shaft and the ball bearing thereon, the holder has a receiving portion which engages around the ball bearing and which is connected via web-shaped sections elastically connected to a radially outer connecting portion. In this case, two web-shaped sections are arranged opposite one another in the direction of the intended pivot axis.

In the US 2014/0083794 A1 a power steering is disclosed in which also a motor shaft is coupled to a worm shaft. The worm shaft, which cooperates with a worm wheel, is mounted on an end facing the motor shaft via a pivot bearing whose outer bearing ring has a spherical outer contour which is mounted in an annular receiving element. At the opposite end remote from the motor shaft, the worm shaft is supported by an ordinary ball bearing, which in turn is accommodated in a cup-like receptacle, which in turn is supported by a circumferential rubber ring on the housing. At the same time, this receptacle is acted upon via a corresponding spring element such that the worm shaft is biased in the direction of the worm wheel.

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. There is also a need to minimize gear play.

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 screw shaft rotatable about an axially extending axis of rotation. By the axial direction of the axis of rotation each of the below-mentioned radial and tangential direction is defined. The worm shaft is normally provided directly or indirectly coupled to a drive shaft of a servomotor to be, to which it runs approximately coaxially. In this case, a clutch or clutch arrangement transmit torque from the drive shaft to the worm shaft. The worm shaft in turn cooperates in the operating state with a worm wheel, which can also be regarded as part of the gear unit. In this case, a reduction of the rotational movement of the drive shaft is usually achieved.

The worm shaft is mounted on a housing, via a pivotable about a pivot axis pivot bearing, which is received with a spherical outer surface in a stationary pivot ring. The housing forms a reference frame, normally stationary relative to the vehicle, via 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.

The pivotable pivot bearing has a spherical outer surface, with which it is arranged in a stationary pivot ring. While the spherical, so spherical portion-like outer surface is convex, the pivot ring has an inner surface which is also spherical, but concave. There may be some play between the inner surface and the outer surface. The swivel ring itself is stationary, that is, it is fixed in position relative to the housing. Alternatively, it can also be understood as part of a multi-part housing. In principle, designs are also conceivable in which the swivel ring is formed in one piece with a larger component and, to that extent, is mainly defined by its annular inner surface. By the outer surface of the pivot bearing slides past the inner surface of the pivot ring, the pivot bearing is pivotable relative to the pivot ring. The pivot axis runs through the center of the (virtual) sphere, which corresponds to the spherical outer surface. The pivot axis can in particular run perpendicular to the axis of rotation. Normally, it cuts the axis of rotation, but it may also be offset to this.

Normally, the pivotable pivot bearing on the one hand of the worm wheel is arranged, while the worm shaft is on the other hand supported by a loose pivot bearing, which is acted upon in such a way that the worm shaft is biased against the worm wheel. The application can be made via a suitable elastic biasing element, which is arranged between the housing and the loose pivot bearing. 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 pivot bearings are usually rolling bearings, in particular ball bearings. Possibly. but could also be designed as a sliding bearing pivot bearing.

According to the invention, the gear unit has a tangentially extending at least partially around the axis of rotation spring element, which is supported in the axial direction on the one hand on the housing and on the other hand with two opposite each other in the direction of the pivot axis, axially projecting abutment portions on the pivot bearing. The spring element, which may be referred to as a ring-like or at least ring-like portion, is arranged at least partially circumferentially about the axis of rotation. As the term "spring element" implies, it is an at least partially elastic element. The spring element is supported in the axial direction on the one hand on the housing, which includes the possibility that the support is given indirectly via an intermediate component. The support is given in the axial direction, which means that forces can be transmitted at least in this direction. In addition, of course, a support in the radial direction and / or be given in the tangential direction.

On the other hand, the spring element is supported in the axial direction with the abutment sections on the pivot bearing. These abutment sections project in the axial direction, d. H. you could also call them projections. If the rotary bearing is a roller bearing having an outer and an inner bearing ring, the spring element is supported by the bearing sections on the outer bearing ring. Overall, at least a power flow from the housing via the spring element with the contact sections is given to the pivot bearing. The abutment portions face each other in the direction of the pivot axis, whereby they form a bearing region extending in the direction of the pivot axis between the spring element and the pivot bearing. Preferably, each abutment section is restricted to a relatively narrow angular range around the axis of rotation, for example at most 20 ° or at most 10 °.

The fact that the total elastic spring element is locally supported in this area on the pivot bearing, on the one hand given an axial bias of the pivot bearing, which adjusts the axial elasticity or rigidity of the system, on the other hand, the pivot bearing is relatively strong fixed in the area of the contact sections, while it can move more easily in other areas. As a result, the abutment sections ultimately define the pivot axis. In other words, pivoting about an axis, which is clearly offset from the connecting line of the abutment sections, is hardly possible. However, due to the axial extent of the pivot bearing, the actual pivot axis may deviate slightly from the position of the abutment sections. While at least the abutment sections must be arranged axially with respect to the pivot bearing, embodiments are conceivable in which other parts of the spring element are arranged not axially, but for example. Radially outside with respect to the pivot bearing.

It is possible within the scope of the invention that the pivot bearing is supported on the housing via an ordinary plate spring on a side opposite the spring element described axially. However, it is preferred that two spring elements are supported on axially opposite sides of the pivot bearing on this. The setting of the axial rigidity and the definition of the pivot axis can thereby be significantly improved. Here, each spring element is supported in the manner described above, on the one hand on the housing and on the other hand with two abutment sections on the pivot bearing. The direction of the force exerted by the abutment sections of the one and the other spring element on the pivot bearing force is of course opposite. At least the contact portions of the two spring elements are arranged along opposite sides of the pivot bearing along the axial direction. In order to simplify the production, the two spring elements may be formed identically and are mounted mirror-symmetrically to each other in the transmission unit, so that abut the abutment portions of the two spring elements from opposite sides of the pivot bearing.

Preferably, at least one spring element is designed as a shaped sheet metal part. The sheet metal part may be formed in particular from spring steel. In this way, the spring element can optionally be produced with a few forming and / or separating steps from a sheet metal blank. The preparation is particularly appropriate, since the spring element can be predominantly flat. Alternatively to a production as a sheet metal part, however, it would also be conceivable to use a component similar in shape to that made of fiber-reinforced plastic or spring steel wire.

Preferably, at least one spring element has a transverse to the axial direction, at least partially tangentially extending around the axis of rotation ring portion. The ring portion extends in a plane which is transverse to the axial direction, which is thus spanned by the radial and the tangential direction. It may preferably extend as a closed ring tangentially completely around the axis of rotation around, so be formed completely encircling, but it is also conceivable to design the ring portion non-closed. The ring section may in particular be concentric with respect to the axis of rotation. In particular, the spring element can be supported by the ring section on the housing. According to one embodiment, the spring element is supported in the axial direction on the one hand on the housing and on the other hand on the pivot ring. One could also say that the ring section is received positively between the housing and the pivot ring.

Advantageously, the abutment sections extend radially inward from the ring section. Here, the ring portion is preferably arranged radially outside the pivot bearing. It could also be said that the ring section is arranged outside a pivoting range of the pivot bearing. Thus, it is avoided that the ring portion hinders the pivotal movement of the pivot bearing or influenced in any way. The contact sections, however, must come to rest with the pivot bearing and therefore extend radially inward, ie in the region in which the pivot bearing is arranged. In the case of an embodiment made of sheet metal, the abutment sections may be formed on inwardly directed tongues or lugs which originate from the ring section.

In particular, the abutment sections may be formed by bulges of a sheet. Such bulges can be generated by a simple deformation of a sheet, for example by pressing, stamping or deep drawing, wherein the material thickness changes only insignificantly. Ie. on a side facing the pivot bearing a protrusion is formed, while on the side facing away from the pivot bearing side a corresponding recess is formed.

According to one embodiment, at least one spring element at least one radially outwardly arranged, limited in the tangential direction positioning element for rotationally fixed positioning on the housing. By such a positioning element, which is limited tangentially to a certain angular range, the spring element is not rotationally symmetrical on the outside. Thus, via a positive connection with a matching, for example. Complementary structure on the side of the housing a positive connection in tangential direction are produced, which prevents rotation relative to the housing. In this way it can be ensured that the position of the abutment sections remains unchanged relative to the housing, whereby the pivot axis can not change.

The positioning elements can be designed in many different ways. For example. this may be at least one incision or a recess into which engages a projection or the like present on the housing side. According to a preferred embodiment, at least one radially outwardly directed positioning nose is formed as a positioning element. Such a positioning nose may extend outwardly from a ring portion described above. In particular, two positioning noses may be present, which are opposite each other. An advantage of such an outwardly directed positioning nose over, for example, an incision is that the structure of the spring element, for example of the ring portion, is not weakened thereby, which under certain circumstances may have an advantageous effect on the spring properties.

While the pivot axis can be defined on the one hand by the abutment sections according to the invention and on the other hand the rigidity of the system can be influenced in the axial direction, it is additionally possible to influence a stiffness or elasticity in relation to pivoting movements. To achieve this, according to one embodiment, at least one spring element has elastic spring sections arranged on different sides of the pivot axis and extending radially inwards from the ring section. By means of these spring sections, a restoring force or a restoring torque can be exerted on the pivot bearing during a pivoting movement. The spring sections can, for example, be integrally formed from the same sheet-metal part as the ring section. According to one embodiment, the spring portions protrude axially relative to the ring portion, so that they constantly abut the pivot bearing and are optionally biased against this. Alternatively, however, there could also be a certain axial distance between the spring sections and the pivot bearing, so that this comes into contact only with a certain deflection with the spring sections. In order to achieve a restoring effect independently of the pivoting direction, the spring sections are arranged on different sides of the pivot axis. For example, exactly two spring sections can be present, which lie opposite one another and are thus offset by 180 ° along the ring section. The spring sections can each be offset by 90 ° to the contact sections. However, more than two spring sections are conceivable. In particular, the arrangement of the spring sections need not be symmetrical with respect to the pivot axis. It is even conceivable that a different elasticity is adjusted depending on the pivoting direction via an asymmetrical arrangement.

The elasticity of the individual spring sections can be influenced by different parameters, for example their material, their thickness or their tangential expansion. According to one embodiment, the annular portion has adjacent to a spring portion at least one radially outwardly extending incision. By such an incision, so to speak, the radial length of the spring portion is increased, without further extending radially inwardly. In particular, such incisions may be present on both sides adjacent to the spring section. Particularly advantageous may be arranged on a side opposite the at least one incision side of the ring portion a positioning nose described above. In this way, it can be achieved that the local weakening of the ring section is compensated in part by the at least one incision via a reinforcement by the positioning nose.

Further advantageous details and effects of the invention are explained in more detail below with reference to an embodiment shown in the figures. Show it:

1 a schematic representation of a transmission unit according to a first embodiment of the present invention;

2 a view of the transmission unit 1 according to the direction II;

3 a schematic representation of a spring element of the transmission unit 1 ; such as

4 a sectional view taken along the line IV-IV in 3 including an outer race of a ball bearing.

1 and 2 each show 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 30 is rotatably mounted. The course of the rotation axis D corresponds to an axial direction. Although the case 30 represented here in one piece, in reality it can consist of several parts, which are rigidly connected. A snail 2.3 The worm shaft acts here with a sprocket 3.1 of the worm wheel 3 together. The worm shaft 3 is at a first end 2.1 via a coupling shown here only schematically 32 with a drive shaft 31 connected to a servomotor, not shown.

Furthermore, the worm shaft 2 in the area of the first end 2.1 over a first ball bearing 5 and a swivel ring 4 on the housing 30 stored. The swivel ring 4 is stationary on the housing 30 arranged. The first ball bearing 5 includes an inner bearing ring 6 and an outer bearing ring 7 , Both bearing rings 6 . 7 are formed concentrically to the rotation axis D. The outer bearing ring 7 has a convex, spherical outer surface 7.1 on, in a concave, also spherical inner surface 4.1 of the swivel ring 4 is included. The first ball bearing 5 can thus around its center within the swivel ring 4 be panned. In particular, a pivoting about a pivot axis S is possible, which intersects the axis of rotation D and perpendicular to this.

At one the first end 2.1 opposite second end 2.2 is the worm shaft in a second ball bearing 11 stored, via a spring shown here schematically 33 with a housing 30 connected is. By the spring 33 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 2 and the worm wheel 3 consists.

Axial on both sides of the swivel ring 4 are two annular spring elements 8th . 9 arranged, one of which in 3 together with the first ball bearing 5 is shown isolated. Both spring elements 8th . 9 are formed of spring steel sheet and can be made for example by punching and embossing from a circuit board. They are each axially between the housing 30 and the swivel ring 4 recorded, so that there is a positive connection in this direction. In particular, each spring element is supported 8th . 9 axially in from the swivel ring 4 turned away direction on the housing 30 from. As in 2 . 3 and 4 can be seen, has each spring element 8th . 9 two investment sections 8.2 . 9.2 on, with which it is axially on the outer bearing ring 7 supported.

As in 3 shown isolated a spring element 8th represents the investment sections protrude 8.2 radially inward of a ring section 8.1 . 9.1 from, which extends within a plane perpendicular to the rotation axis D level. As in 2 as well as in the sectional view in 4 (in addition to the spring element 8th also schematized the outer bearing ring 7 shows) recognizable, are the investment sections 8.2 . 9.2 in this case formed by bulges of the spring steel sheet, which is axially opposite the ring section 8.1 . 9.1 protrude. They are arranged opposite one another in the direction of the pivot axis S. Through them, the outer bearing ring 7 each locally applied and biased to some extent, which has two effects. First, this is the rigidity of the first ball bearing 5 reinforced and better defined relative to displacements in the axial direction, wherein the rigidity to pivotal movements is substantially unaffected. On the other hand, this the pivot axis S is clearly defined. The ring section 8.1 . 9.1 itself is outside the swing radius' of the ball bearing 5 arranged.

To adjust the stiffness or elasticity against pivoting movements about the pivot axis S, are two spring sections 8.3 . 9.3 provided along the ring section 8.1 . 9.1 by 90 ° with respect to the abutment sections 8.2 . 9.2 are offset. They are thus arranged symmetrically on both sides of the pivot axis S. The spring sections 8.3 . 9.3 protrude opposite the ring section 8.1 radially inward, wherein, as in 1 recognizable, slightly in the axial direction on the outer bearing ring 7 are inclined towards. The spring sections 8.3 . 9.3 lie here on the outer bearing ring 7 and can be biased against this. In any case, a pivoting movement of the first ball bearing leads 5 to a restoring torque or a restoring force, the deflection of each of two of the four spring sections 8.3 . 9.3 arises.

To the elasticity of the spring sections 8.3 . 9.3 Increase are on both sides adjacent each incisions 8.4 provided, extending radially outward into the ring section 8.1 . 9.1 extend. Optionally, the incisions 8.4 but also omitted. On an outside of the ring section 8.1 . 9.1 , the cuts 8.4 opposite, is in each case a positioning nose 8.5 . 9.5 formed, which is radially outward from the ring portion 8.1 . 9.1 projects. On the one hand, the additional material of the positioning nose 8.5 . 9.5 that in the area of the incisions 8.4 missing material partially compensated, reducing the structure of the spring element 8th . 9 stabilized in this area. Every positioning nose 8.5 . 9.5 is in a complementary recess of the housing 30 added. Due to the resulting positive locking each spring element 8th . 9 rotatably positioned to the housing, whereby the position of the pivot axis S is secured.

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

 swivel

4.1

 palm

5, 11

 ball-bearing

6

 inner bearing ring

7

 outer bearing ring

7.1

 outer surface

8, 9

 spring element

8.1, 9.1

 ring section

8.2, 9.2

 contact section

8.3, 9.3

 spring section

8.4

 incision

8.5

 positioning nose

30

 casing

31

 drive shaft

32

 clutch

D

 axis of rotation

S

swivel axis

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 2014/0029884 A1 [0006]
• US 7575090 B2 [0007]
• US 6179473 B1 [0008]
• US 8539849 B2 [0009]
• US 8667858 B2 [0010]
• US 2014/0083794 A1 [0011]

Claims (10)

Gear unit ( 1 ) for a motor vehicle, with a about an axially extending axis of rotation (D) rotatable worm shaft ( 2 ), which are attached to a housing ( 30 ) via a pivotable about a pivot axis (S) pivot bearing ( 5 ) which is provided with a spherical outer surface ( 7.1 ) in a stationary swivel ring ( 4 ), characterized by a spring element running tangentially at least partially around the axis of rotation (D) ( 8th . 9 ), which in the axial direction on the one hand on the housing ( 30 ) and on the other hand with two mutually in the direction of the pivot axis (S) opposite axially projecting abutment sections ( 8.2 . 9.2 ) at the pivot bearing ( 5 ) is supported. Transmission unit according to claim 1, characterized in that two spring elements ( 8th . 9 ) on axially opposite sides of the pivot bearing ( 5 ) on this support. Transmission unit according to claim 1 or 2, characterized in that at least one spring element ( 8th . 9 ) is formed as a sheet metal part. Transmission unit according to one of the preceding claims, characterized in that at least one spring element ( 8th . 9 ) a transverse to the axial direction, tangentially at least partially around the rotation axis (D) extending around the ring portion ( 8.1 . 9.1 ) having. Transmission unit according to one of the preceding claims, characterized in that the contact sections ( 8.2 . 9.2 ) from the ring section ( 8.1 . 9.1 ) extend radially inwardly, wherein the ring portion ( 8.1 . 9.1 ) radially outside of the pivot bearing ( 5 ) is arranged. Gear unit according to one of the preceding claims, characterized in that the abutment sections ( 8.2 . 9.2 ) are formed by bulges of a sheet. Transmission unit according to one of the preceding claims, characterized in that at least one spring element ( 8th . 9 ) at least one radially outwardly arranged, limited in the tangential direction positioning element ( 8th .5) for non-rotatable positioning on the housing ( 30 ) having. Transmission unit according to claim 7, characterized in that as a positioning element at least one radially outwardly directed positioning nose ( 8.5 ) is trained. Transmission unit according to one of the preceding claims, characterized in that at least one spring element ( 8th . 9 ) on different sides of the pivot axis (S) arranged elastic spring sections ( 8.3 . 9.3 ) extending from the ring portion ( 8.1 . 9.1 ) extend radially inwards. Transmission unit according to one of the preceding claims, characterized in that the ring section ( 8.1 . 9.1 ) adjacent to a spring section ( 8.3 . 9.3 ) at least one radially outwardly extending incision ( 8.4 ) having.

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