DE102013206681A1 - Helical differential with radially expanded rolling bearing - Google Patents

Abstract

The invention relates to a planetary gear (1), such as a differential gear (2), with a planet carrier (4) to which at least one planet gear (7) is rotatably connected, with at least one sun gear (8, 9) which is in meshing operative engagement with the at least one planet gear (7) stands or can be brought, the planet carrier (4) being mounted on a housing (13), such as a gear housing (14), by means of at least one bearing (11), the bearing (11) being a rolling element bearing (12) is formed, wherein a radially inner rolling element running surface (16) of the rolling bearing (12) is present on a component fixed to the housing and a radially outer rolling element running surface (17) of the rolling bearing (12) is present on a component fixed to the planet carrier, the rolling elements (15 ) of the roller bearing (12) are arranged radially further outwards than a pitch circle diameter determined by the toothing (21) of the at least one sun gear (8, 9).

Description

Field of the invention

The invention relates to a planetary gear, such as a differential gear, with a planet carrier to which at least one planet gear is rotatably connected, with at least one sun gear, which is in meshing engagement with the at least one planet or is engageable, the planet carrier by means of at least one bearing a housing, such as a transmission housing is mounted.

The planet carrier may also be referred to as a basket, in particular it may be formed as a differential cage.

From the prior art, different planetary gear are already known, so for example. From the EP 0156067 ,

Basically, differential gear for motor vehicles from the DE 101 568 90 C1 known. There is disclosed a differential for a motor vehicle with a mounted in a housing wall, a drive sprocket having differential housing, in which a balancing pin is arranged with at least one rotatably mounted Ausgleichskegelrad, which is in engagement with a drive shaft of a drive shaft mounted in the differential drive shaft. The drive shaft is supported by means of at least one first bearing in the housing wall of the differential gear and / or the differential housing by means of at least one second bearing on the drive shaft and the drive shaft has a common bearing bush for the formed as a shaft bearing first bearing of the drive shaft and the housing bearing of the differential housing.

A differential order based on bevel gears is also apparent from the document US 7,775,928 B2 known.

Furthermore, from the DE 10 2009 017 397 A1 a gear arrangement known which uses planet gears. The presented there gear arrangement relates to a differential gear, with a drive-side disc part, a first drive member which is non-rotatably connected to a first driven axle in communication, and a second drive member which is non-rotatably in communication with a second driven axle, wherein between the first drive member and the second drive part is provided with a gear arrangement for transmitting torque from the drive-side disk part to the first drive part and the second drive part. The first drive part has the shape of a first drive pulley and has a bulge radially spaced from the first driven axle. The second drive part further has the shape of a second drive shaft extending radially outward from the second driven second drive pulley. The bulge further points away from the second drive pulley. The gear arrangement is arranged in a space formed by the bulge of the first drive pulley and the opposite region of the second drive pulley.

Such planetary gear, which are designed as differential gear, may be formed as a Stirnraddifferenzialgetriebe, as for example. From the WO 2010/112366 A1 are known. The present invention Stirnraddifferenzgetriebeanordnung discloses the operational capability in a motor vehicle. In each case helical gears, planet gears and a ring gear are so used by a surrounding housing with supported bearings that the parallel sun gears are each coupled to parallel output shafts. It is provided in this document that between the parallel sun gears and / or between the sun gears and the surrounding housing each friction surfaces are arranged.

Also known are planetary gear from the US 3,943,780 A as well as combined axial radial rolling bearings from the US Pat. No. 3,809,444 ,

However, the previously known planetary gear disadvantages in terms of space utilization. It should be offered here an improvement, which is not only durable, but also inexpensive and easy to assemble.

Disclosure of the invention

This object is achieved in that the bearing is designed as a rolling body bearing roller bearing having a radially inner Wälzkörperlauffläche of the rolling bearing on a housing-fixed component and having a radially outer Wälzkörperlauffläche of the rolling bearing on a planetenträgerfesten component. Furthermore, the rolling elements of the rolling bearing are arranged radially further outside than a pitch circle diameter determined by the toothing of the at least one sun gear.

Advantageous embodiments are claimed in the subclaims and are explained in more detail below.

So it is advantageous if two sun gears are included and the rolling elements of the bearing radially outside both defined by the teeth of the sun gears pitch circle diameter are arranged. A particularly tilt-proof planetary gear storage can then be realized.

It is also expedient if the rolling bodies are arranged on the radial position of one or more bolts or sleeves supporting the at least one planetary gear. It is also advantageous if the rolling elements are even arranged radially further outside of the bolt or the sleeve.

Tilting can then be effectively counteracted.

If the planetary gear is designed as Stirnraddifferenzial, so the space can be used very efficiently and even in a small space, the weight can be reduced. It is advantageous if, in addition or alternatively, the bearing has a support pot. Especially by the provision of a separate or integrated support pot, the design freedom, in adaptation to different drive trains in motor vehicles, can be improved.

This object is achieved cumulatively or alternatively also by the fact that the bearing is supported on a cohesively mounted on the planet carrier support pot.

The cohesive connection is designed insoluble and can be configured as a welding, soldering, adhesive or Vulkanisierverbindung. In addition, of course, non-positive and / or positive connection types can be added supportive. The use of laser, friction and / or inert gas welding is advantageous.

The support pot does not necessarily have a stage, but can be configured as a simple ring without a stage. The designation as sleeve or hollow cylinder, can be used equally.

Advantageous embodiments are also claimed in the subclaims and are explained in more detail below.

Thus, it is advantageous if the bearing is supported on the support pot axially and / or radially. Tilting or displacement of the planetary gear within the transmission can then be effectively excluded and / or at least one of the sun gears is sealed with a shaft seal against the transmission housing.

For longevity it is beneficial if the bearing is designed as a rolling bearing. Also can then be resorted to a hodgepodge of standard elements that are tested on the one hand and on the other hand are inexpensive.

On the forces applied to the planetary gear and existing conditions, it can be particularly targeted react when the rolling bearing is designed as a combined axial-radial roller bearing, as angular contact ball bearings, tapered roller bearings or spherical roller bearings. Combined axial-radial roller bearings are basically, for example, from the US Pat. No. 3,809,444 known.

The installation can be simplified if the bearing has its own, separate outer bearing shell and / or an inner bearing shell. A bearing with two shells can be easily pre-assembled and requires no transport safety. Furthermore, it is advantageous if the bearing outer shell or the inner bearing shell rests on the support pot or alternatively is an integral part thereof. In the latter case, the number of parts can be reduced and the weight of the overall planetary gear can be minimized.

As already explained, it is advantageous if the support pot is welded to the planet carrier. In particular, proven welding methods, such as friction welding, plasma welding or laser welding methods can then be used inexpensively with good success.

If the support pot rises with one end on a substantially radially aligned footprint and there, preferably circumferentially and / or continuously, welded, so the fit can be increased on the one hand and on the other hand a particularly good weld can be achieved, whereby the load capacity is improved.

An advantageous embodiment is also characterized in that the contact surface is present on the front side of the planet carrier, wherein extending at its radial end an axially aligned flange extension. In this way, the bearing may extend radially in the radial direction. In this way, the bearing can be spent in the radial direction to the outside, in which the overall construction and the planetary gear can be kept narrow or the support surfaces can be brought axially closer to each other.

It is also expedient if the planetary gear is designed as a spur gear differential with two sun gears and two Planetenradsätzen, preferably such that the planetary gears of the two planetary gear mesh with each other, preferably further combing the planet gears of a planetary gear with one sun gear and the planetary gears of the other planetary comb with the other sun gear.

If two bearings between the planet carrier and the housing, preferably axially on both sides of the sun gears, are present, and more preferably, the two bearings are designed identically or differently, so an efficient storage can be ensured. It is advantageous if the two bearings are designed as each combined axial-radial roller bearings, or are each designed as angular contact ball bearings (X or O arrangement), or a combination of these two types of rolling bearings, so designed a rolling bearing as a combined axial-radial roller bearing is and the other is designed as angular contact ball bearings. The position of the respective angular contact ball bearings can therefore be exchanged.

A special feature of the arrangement with different rolling bearings, such as a roller sleeve bearing on one side of the planet carrier and a thrust bearing on the same side to generate a combined axial-radial roller bearing is that the thrust bearing with a welding neck or the footprint close range of the support pot out is.

In other words, the bearing assembly of the invention is reversed, as normally, namely, the bearing outer ring takes on the signposted as a differential cage planet carrier and the bearing inner ring is seated on a pin of the housing. The bearing ring or a support for the bearing ring is welded directly to the planet carrier.

This object is achieved cumulatively or alternatively in that the support pot is supported on a radial outer side of the planet carrier.

Advantageous embodiments are claimed in the subclaims and are explained in more detail below.

Thus, it is advantageous if the support pot has an axially protruding collar, which is supported on a peripheral surface of the planet carrier. The assembly can then be simplified, in particular if the bearing constructed as a rolling bearing is pre-assembled in the support pot as a pre-assembly unit.

It is advantageous if the collar is supported on the peripheral surface in the region of an axially extending flange of the planet carrier. A sufficiently large contact surface can then be made available and a good tilting security can be achieved.

It is useful if a frictional and / or positive connection between the support pot and the planet carrier is created via the collar, preferably using a press fit. Especially when using a non-positive connection, an efficient transport lock can be achieved and a falling apart of the individual components can be avoided. Press seats are also available for exact dimensioning and design.

The length of the press fit is matched by the pressing force, which then has an advantageous effect when the axial length of the press fit is selected in dependence on the pressing force to be transmitted.

If the second raceway is formed on the support pot, so can be dispensed with an additional element, such as an outer bearing shell. However, it is also advantageous if the raceway is formed on a support cup separate outer bearing shell or bearing ring, since then the pre-assembly can be simplified. Also can be used on a variety of identical parts, which minimizes the cost.

Also as conducive to the cost reduction, it has been found when the first raceway is formed on the housing, since then the number of items can be reduced, or if the first raceway is formed on a separate inner bearing shell or bearing ring to the housing, then a modular Assembly of the planetary gear is facilitated.

An advantageous embodiment is also characterized in that the bearing is designed as a combined axial-radial roller bearing or as angular contact ball bearings, as tapered roller bearings, or as spherical roller bearings. As a combined axial-radial roller bearing, on the one hand can be understood a Axiallagerkombination with a superimposed in the radial direction roller sleeve bearing. It should be noted that the radial bearing can also be done without a roller sleeve, especially if the formed in the region of the bearing flange of the housing is hardened and the axial securing of the roller ring is ensured.

When the collar is supported on the smallest or largest outer diameter of the planet carrier, a force deflection is achieved, which is conducive to the compact design of the planetary gear.

Finally, the invention also relates to a planetary gear formed as Stirnraddifferenzial with two sun gears and two Planetenradsätzen, wherein the planetary gears of the two planetary gear mesh with each other and mesh the planetary gears of a planetary gear with one sun gear and the planetary gears of the other planetary with the other sun gear comb. In this way can be dispensed with heavy and large-scale cone differentials.

One aspect of the invention is also directed to the fact that the outer ring is centered on the outside of a collar of the differential cage and not inside. In contrast to the usual practice, the arrangement in the area of the bearing is the other way round, ie. the bearing outer ring receives the differential cage / planet carrier and the bearing inner ring sits on a pin of the housing.

The invention will be explained in more detail below with the aid of a drawing, in which different embodiments are shown. Show it:

1 A first embodiment of a planetary gear according to the invention in a longitudinal section,

2 the enlargement of an area II of the in 1 illustrated first embodiment,

3 a second embodiment of a planetary gear according to the invention in a to 1 comparable representation, wherein a support pot is welded to the planet carrier,

4 an enlarged view of the area IV 3 .

5 a singular, perspective view of the in the 3 and 4 illustrated embodiment used Stützopfs,

6 a longitudinal section through the support pot 5 .

7 an alternative inventive planetary gear with two angular contact ball bearings on both sides of the planet carrier composed of two planet carrier halves, in a to 1 comparable presentation,

8th a variant of the planetary gear 7 when using, on the one hand, the planetary carrier of a combined axial-radial bearing and, on the other hand, on the other side of the planetary carrier, an angular contact ball bearing,

9 a likewise inventive planetary gear in a for 8th and 1 comparable representation, but the position of the combined axial-radial roller bearing and angular contact ball bearing of the 8th is reversed,

10 another inventive planetary gear in a for 1 comparable representation, whereby two combined axial-radial bearings are used,

11 an enlargement of the range XI 10 .

12 another planetary gearbox variant with two angular contact ball bearings, in one for 1 comparable presentation,

13 and 14 two variants to the in 12 illustrated embodiment, in a comparable manner, wherein combined axial-radial roller bearings are combined with angular contact ball bearings, on each of different sides of the planet carrier.

The figures are merely schematic in nature and are only for the understanding of the invention. The same elements are provided with the same reference numerals.

In 1 is a first embodiment of a planetary gear according to the invention 1 shown. The planetary gear 1 is as a differential gear 2 , in particular as Stirnraddifferenzgegetriebe 3 configured.

It has a planet carrier 4 on, consisting of a first and second planet carrier half 5 and 6 composed. Between the two planet carrier halves 5 and 6 two planetary gear sets are included, each planetary gear set one or more planet gears, preferably 2 . 3 . 4 . 5 . 6 . 7 (or more) has planetary gears. Exemplary is a planetary gear with the reference numeral 7 Mistake. This planet wheel 7 can mesh with another planetary gear of the other planetary gear set, but at the same time meshes with one of two sun gears 8th and 9 , In the present case, the planetary gear meshes 7 with the first sun gear 8th ,

Between the two sun wheels 8th and 9 can be a sliding washer 10 to be available.

The planet carrier 4 is about a camp 11 as a rolling bearing 12 is formed on a housing 13 namely a transmission housing 14 stored. It is realized a radial and / or axial bearing. The warehouse 11 has rolling elements 15 on that on an inner rolling element tread 16 and an outer rolling element tread 17 unroll during operation.

The inner rolling element tread 16 is on a housing-fixed inner bearing shell 18 educated. The outer rolling element tread 17 is at a support pot 19 designed as an outer bearing shell 20 acts. The function of an outer bearing shell 20 is in the support pot 19 integrated. It is a one-piece component. The rolling elements 15 are in present embodiment formed as balls, but they can also be designed as tons, cones or needles. The rolling elements 15 are radially further outside one through a toothing 21 on the radial outside of the respective sun gear 8th or 9 defined pitch diameter arranged. The support pot 19 points one in the direction of the housing 13 pointing and axially aligned collar 22 on. The Bund 22 is on a flange 23 of the planet carrier 4 pressed.

In 2 is again shown enlarged that the outer ring of the angular contact ball bearing can be omitted. Axial space is saved. The support pot 19 may also be referred to as a bearing flange and is produced by a deep-drawing process, in particular using a steel sheet. A ball track is integrated in it. The inner diameter of the bearing inner ring (inner ring) or the inner bearing shell 18 can be enlarged. The warehouse 11 can thus continue to move radially outward, thereby improving the support. An X or O arrangement is possible.

The length of the press fit between the waistband 22 and the flange 23 is determined by the pressing force.

In the in the 3 . 4 . 7 . 8th and 9 illustrated variants, is the support pot 19 always cohesively with the planet carrier 4 connected, namely via a welded joint, so a permanent connection. While in the 3 and 4 Embodiments with two combined axial-radial bearings 24 are shown in the in 7 illustrated embodiment, two angular contact ball bearings 25 used.

In the 5 and 6 is the support pot 19 shown enlarged. The support pot 19 has at least two stages 26 on. At every stage 26 is the wall, which has a constant wall thickness, flanged by 90 °.

In the in the 8th and 9 Illustrated embodiments will each be a combined axial-radial roller bearing 24 and an angular contact ball bearing 25 used.

Unlike in the 1 illustrated embodiment is in the in the 10 and 11 illustrated embodiment of two combined axial-radial roller bearings 24 instead of an angular contact ball bearing 25 set.

In the in 12 Although illustrated embodiment is an angular contact ball bearing 25 , similar to the one in 1 illustrated embodiment, but is in addition to the support pot 19 also a separate outer bearing shell 20 used.

A combination of an angular contact ball bearing 25 with a combined axial roller bearing assembly 24 is in the 13 and 14 played.

LIST OF REFERENCE NUMBERS

1

 planetary gear

2

 differential gear

3

 Stirnraddifferenzialgetriebe

4

 planet carrier

5

 first planet carrier half

6

 second planet carrier half

7

 planet

8th

 first sun gear

9

 second sun wheel

10

 sliding disk

11

 camp

12

 roller bearing

13

 casing

14

 gearbox

15

 rolling elements

16

 inner rolling element tread

17

 outer rolling contact surface

18

 inner bearing shell

19

 support pot

20

 outer bearing shell

21

 gearing

22

 Federation

23

 flange

24

 Combined axial-radial roller bearing

25

 Angular contact ball bearings

26

 step

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

• EP 0156067 [0003]
• DE 10156890 C1 [0004]
• US 7775928 B2 [0005]
• DE 102009017397 A1 [0006]
• WO 2010/112366 A1 [0007]
• US 3943780A [0008]
• US 3809444 A [0008, 0022]

Claims (5)

Planetary gear ( 1 ), like a differential gear ( 2 ), with a planet carrier ( 4 ), on which at least one planetary gear ( 7 ) is rotatably connected, with at least one sun gear ( 8th . 9 ) in meshing engagement with the at least one planetary gear ( 7 ) is or can be brought, wherein the planet carrier ( 4 ) by means of at least one bearing ( 11 ) on a housing ( 13 ), such as a transmission housing ( 14 ), the bearing ( 11 ) as rolling element bearing rolling bearing ( 12 ), wherein a radially inner Wälzkörperlauffläche ( 16 ) of the rolling bearing ( 12 ) is provided on a housing-fixed component and a radially outer Wälzkörperlauffläche ( 17 ) of the rolling bearing ( 12 ) is present on a planet carrier solid component, wherein the rolling elements ( 15 ) of the rolling bearing ( 12 ) radially further outward than a through the toothing ( 21 ) of the at least one sun gear ( 8th . 9 ) are arranged certain pitch diameter. Planetary gear ( 1 ) according to claim 1, characterized in that two sun gears ( 8th . 9 ) and the rolling elements ( 15 ) of the warehouse ( 11 ) radially outside both by the toothing ( 21 ) of the sun wheels ( 8th . 9 ) defined pitch circle diameter are arranged. Planetary gear ( 1 ) according to claim 1 or 2, characterized in that the rolling bodies ( 15 ) at the radial position of one or more planetary gears ( 7 ) bearing bolt or sleeve are arranged. Planetary gear ( 1 ) according to one of claims 1 to 3, characterized in that the planetary gear ( 1 ) as a spur gear differential ( 3 ) and / or the bearing ( 11 ) a support pot ( 19 ) having. Planetary gear according to one of claims 1 to 4, characterized in that at least one of the sun gears ( 8th . 9 ) with a shaft seal against the transmission housing ( 14 ) is sealed.

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