WO2013156290A1

WO2013156290A1 - Planet carrier

Info

Publication number: WO2013156290A1
Application number: PCT/EP2013/056647
Authority: WO
Inventors: Thorsten Biermann; Harald Martini
Original assignee: Schaeffler Technologies AG & Co. KG
Priority date: 2012-04-19
Filing date: 2013-03-28
Publication date: 2013-10-24
Also published as: CN104379970A; CN104379970B

Abstract

The invention relates to a planetary gearbox (1, 43, 47) such as a differential, comprising a planet carrier (3), to which planet wheels (5, 6) that are in functional contact with at least one sun gear (9, 10, 11) are rotatably attached, said planet carrier (3) being connected to a drive wheel (15).

Description

Name of the invention

PLANET RAGER

description

Field of the invention

The invention relates to a planetary gear, such as a differential gear, with a planet carrier, are rotatably connected to the planet gears, which are at least one sun gear in torque-transmitting active contact, wherein the planet carrier is connected to a drive wheel, such as a spur gear.

The planet carrier can also be designed as a differential cage.

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

Basically, differential gear for motor vehicles from DE 10156890 C1 are known. There is disclosed a differential for a motor vehicle with a mounted in a housing wall, a drive sprocket aufwei- exhibiting compensating housing, in which a balancing pin is arranged with at least one rotatably mounted Ausgleichkekegelrad, which is in engagement with a drive shaft of a bearing in the differential housing 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 which is based on bevel gears is also known from document US Pat. No. 7,775,928 B2. Furthermore, a gear arrangement is known from DE 10 2009 017 397 A1, which uses planetary 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 Stirnraddifferenzialgetriebe, as they are, for example, from WO 2010/1 12366 A1 known. The spur gear differential gear arrangement presented there discloses the operational capability in a motor vehicle. In each case helical gears and planetary gears are used by a surrounding housing with supported bearings so that the parallel sun gears are each coupled with 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. However, the known planetary gear have the disadvantage that they require a lot of Axialbauraum. It is the object of the present invention to remedy this situation and to create a space-saving, in particular axialbau space-saving improvement that is durable and at least cost-neutral executable or optimally even cost-reducing effect.

DISCLOSURE OF THE INVENTION This object is achieved according to the subject matter of claim 1. The planet carrier is connected via a separate connection part with a bearing, such as a rolling bearing. In this way, the bearing can build wider and move closer to the sun gears. An advantageous O-arrangement of the bearing preferably on both sides of the planetary gear bearing can then be easily realized. Also, the bearings can be made smaller, as set optimal leverage. The inner diameter of rolling bearings can then be increased so far that set optimal balance of power. Nevertheless, such a planetary gear builds extremely compact.

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

Thus, it is advantageous if the connecting part is designed as a sheet metal part, preferably as a sheet metal sleeve. Especially the use of sheet metal parts or formed as sheet metal sleeves elements, allows further reducing the cost.

The assembly can be facilitated if the sheet-metal sleeve has two cylindrical flange sections connected by a connecting section. It is advantageous if the connecting portion is formed either exclusively radially extending or at least partially transverse to Radial direction and extends to the axial direction, more preferably is formed cranked.

An advantageous embodiment is also characterized in that the connecting part with an inner ring or an outer ring of a bearing is in force-transmitting, abstützendem contact. The planet carrier can then be rotatably connected to a fixed housing via the connecting part and the bearing. When the one flange portion has a first interface that abuts the planetary carrier and is spaced less far from an axis of rotation about which the planetary carrier rotates, than a second interface of the other flange portion that engages the inner ring or outer ring in the bearing is in plant, so the respective sun gear can be easily mounted. Also set up a nearly optimal distribution of forces and moments in the planetary gear.

It has proven to be particularly advantageous if the distance of the first boundary surface from the axis of rotation is only 1.25 times to 2 times the section of the second boundary surface to the axis of rotation, more preferably 1.75 times that.

A particularly long-lived planetary gear variant can be achieved if the connecting portion rests on the planet carrier extending in the radial direction.

It is also advantageous if the connecting part is secured on the inner ring or on the outer ring of the bearing by caulking. It sets a higher stability with less suspension. It is also easier to use special forming techniques, such as the "smart fit bearing." It also makes it easier to use standard sizes, and it is also advantageous because a defined anchor point is available during assembly. If the planetary gear is designed as Stirnraddifferenzial having two sun gears, which are each located in meshing engagement with a planetary at least one planetary gear, so it is possible to realize a particularly compact design planetary gear, which is also high load capacity and cost.

In order to realize positive Selbsthemmeffekte, it is advantageous if a friction disc is located between the sun gears. It is also advantageous if the connecting part is designed as a cover which closes an opening between the planet carrier and a sun gear. In this way, on the one hand realize a sealing effect and on the other hand realize a support effect. An embodiment of the invention relates to a designed as a differential gear planetary gear with a planetary carrier designed as a differential carrier, are rotatably connected to the planetary gears. The planet gears are in meshing engagement with at least one sun gear, wherein the planet carrier is connectable to a hollow drive wheel, further comprising a bearing with a bearing inner ring and a bearing outer ring, such as a rolling bearing, the planet carrier in a stationary housing, such as a transmission housing, axially and / or radially position determined rotatably supports.

An embodiment of the invention provides that the bearing outer ring is rotatably connected to the planet carrier and the bearing inner ring is connected to the stationary housing. A traction in such an embodiment is much cheaper to achieve than in the known solutions in which the planet carrier has an axially outwardly facing collar on which the bearing inner ring is pressed. A cheaper, lighter and more durable planetary gear can be realized thereby.

A further embodiment of the invention provides that the bearing outer ring form and / or positively and / or cohesively directly with the planet carrier is tied or connected via a separate component to both components connecting part. In the first alternative, the individual parts can be reduced, which thus reduces the assembly costs and further reduces the weight of such a planetary gear. The second variant therefore provides that the bearing ring is the connecting part and has the advantage that it can be responded to different requirements with respect to the usable geometry as needed.

It is provided with a further embodiment of the invention that the bearing is designed as a ball bearing, preferably as angular contact ball bearings or as a needle, roller or tapered roller bearings.

Finally, it is provided with an embodiment of the invention that the planet carrier and / or acting on the outside of the bearing part, such as the bearing outer ring or the connecting part, has a sun gear-aligned collar portion which is preferably located with the sun gear in Appendix or are, wherein the respective collar is configured hardened. The invention will be explained in more detail with different drawings, in which various embodiments are shown.

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

2 shows a second embodiment of a planetary gear according to the invention in a longitudinal sectional view,

Fig. 3 shows a third embodiment of a planetary gear design according to the invention in a longitudinal sectional view, and Fig. 4 shows a detail of a fourth embodiment in a partial longitudinal sectional view.

Fig. 5 shows another embodiment of the invention in a longitudinal section and

Fig. 6 shows another embodiment in a longitudinal section.

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 Fig. 1, a first embodiment of a planetary gear 1 according to the invention is shown. The planetary gear 1 is designed as a differential gear, in particular as Stirnraddifferenzialgetriebe 2. It has a planet carrier 3, which can be referred to as a basket, in particular differential cage. The planet carrier 3 may also be referred to as a planet carrier. At the planet carrier 3 are Planetenradsätze 4, each with a first planetary gear 5 and a second planetary gear 6 via a respective bolt 7, which is located in a bearing sleeve 8, stored. The planet gears 5 and 6 are in operative contact with a sun gear 9. Here, the first planetary gear 5 is in meshing engagement with a first sun gear 10 and the second planetary gear 6 with a second sun gear 1 1 in meshing operative contact. The bolt 7 is formed as a hollow bolt.

There are advantageously three, four, five, six or seven planetary gear sets 4, each with a first planetary gear 5 and a second planetary gear 6 used.

The planet carrier 3 has a first half 12 and a second half 13 which, via a connecting element 14, such as a rivet on a drive wheel 15, which is formed as a spur gear 16, are connected. The spur gear 16 has an outer helical toothing 17.

The planet carrier 3 is connected via a separate connecting part 18 with a bearing 19, which is designed as a rolling bearing 20. The rolling bearing 20 is designed as angular contact ball bearings. At both the first half 12 of the planet carrier 3, and the second half 13 of the planet carrier 3 is in each case an angular contact ball bearing located. The connecting part 18 in this case has a first flange portion 21, which is connected via a connecting portion 22 with a second flange portion 23. The first flange portion 21 forms a first boundary surface 24, which is located in contact with an inner surface 25 of the planet carrier 3. The second flange section 23 also forms a second boundary surface 26, which is in contact with an outer surface 27 of the bearing 19. In this case, the second interface 26 bears against an outer ring 28 of the roller bearing 20.

A bearing inner ring 29 is connected to a stationary housing, not shown, located radially inside the bearing 19 and displaced axially substantially to the right, for example via a positive and / or non-positive fit, in particular using a press fit. A shoulder 40 of the inner ring 29 then abuts against a radially extending surface of this stationary housing, which also acts as a gear housing.

However, it is possible that, as shown in Fig. 2, an inner ring 29 of the rolling bearing 20 bears with an inwardly facing inner ring surface 30 at the second interface 26. While in the embodiment shown in FIG. 1, only a certain portion of the connecting portion 25 rests radially on the planet carrier 3, in the embodiment shown in FIG. 2, the entire or nearly the entire connecting portion 22 axially, extending in the radial direction, at the planet carrier 3. The connecting part 18 is in this case as a sheet metal part, in particular as ger 3. The connecting part 18 is formed as a sheet metal part, in particular as a sheet metal sleeve.

While in the embodiment shown in FIG. 1, both the planet carrier 3, and the connecting member 18 form a collar 31 and in the embodiment of FIG. 1, both the planet carrier 3 rests with a collar portion 32 on the first sun gear 10 and the connecting member 18 with a Bund portion 33 rests against the first sun gear 10, is in the embodiment of FIG. 2, only the collar portion 33 of the connecting part 18 to the sun gear 9 at.

As also shown in FIG. 2, external teeth, for example via a ring gear 34, are provided on at least one of the sun gears 9. In the embodiment according to FIG. 3, the connecting part 18 is designed as a pot-like cover 35, which is configured thin-walled compared to the planet carrier, in particular only half the wall thickness or advantageously only one third to one quarter of the wall thickness of the planet carrier 3. It is located in a recess 36 there, a friction washer 37, which is located in contact with the sun gear 9, in particular the first sun gear 10 or the second sun gear 1 1.

The cover 35 has an outer surface 38 which extends in the axial direction and which is in contact with both the planetary carrier 3 and the inner ring 29, in particular the inner surface 30 of the inner ring 29, at the same height measured in the radial direction.

As can be seen in Fig. 4, a caulking 39 is mounted in an axially spaced from the sun gears 9 region of the bearing. It can also be seen on the left side of the spur gear differential gear 2 that the second flange section 23 is aligned obliquely or transversely to the radial direction as well as obliquely or transversely to the axial direction on the outer ring 41 of the rolling bearing 20 designed as a tapered roller bearing. In the embodiment according to FIG. 4, the inner ring 29 is formed as a flow-pressed inner ring 29, whereas the outer ring 41 is formed on the left side as a drawn bearing outer ring. The variant is also characterized in that the connecting part 18 has a flange portion 23, which is additionally provided with a raceway 42 for a rolling bearing 20.

FIG. 5 shows a further exemplary embodiment of a planetary gear 43 according to the invention. The planetary gear 43 is designed as a differential gear, in particular as Stirnraddifferenzialgetriebe 2. It has a planet carrier 3, the differential cage can be designated. The planet carrier 3 may also be referred to as a planet carrier. At the planet carrier 3 are Planetenradsätze 4, each with a first planetary gear 5 and a second planetary gear 6 via a respective bolt 7, which is located in a bearing sleeve 8, stored. The planet gears 5 and 6 are in operative contact with a sun gear 9. Here, the first planetary gear 5 with a first sun gear 10 in meshing engagement and the second planetary gear 6 with a second sun gear 11 in meshing contact. The bolt 7 is formed as a hollow bolt.

Advantageously, three, four, five, six or seven planetary gear sets 4 each having a first planetary gear 5 and a second planetary gear 6 are used.

The planet carrier 3 has a first half 12 and a second half 13, which are connected via a connecting element 14, such as a rivet, to a drive wheel 15, which is designed as a spur gear 16. The spur gear 16 has an outer helical toothing 17.

The planet carrier 3 is connected via a separate connecting part 18 with a bearing 19, which is designed as a rolling bearing 20. The rolling bearing 20 is as Angular contact ball bearings formed. At both the first half 12 of the planet carrier 3, and the second half 13 of the planet carrier 3 is in each case an angular contact ball bearing located. The angular contact ball bearings are set in O arrangement against each other.

The connecting part 18 is at the same time outer ring 45 of the roller bearing 20 in this case has a first flange portion 21 which is connected via a connecting portion 22 with a second flange portion 23. The first flange portion 21 forms a first boundary surface 24, which is located in contact with an inner surface 25 of the planet carrier 3. The second flange portion 23 also defines a second interface 26 which is the inner surface and raceway 44 for rolling elements 46.

A bearing inner ring 29 is connected to a stationary housing, not shown, located radially inside the bearing 19 and displaced axially substantially to the right, for example via a positive and / or non-positive fit, in particular using a press fit. A shoulder 30 then abuts a radially extending surface of this stationary housing, which also acts as a transmission housing.

FIG. 6 shows a further exemplary embodiment of a planetary gear 47 according to the invention. The planetary gear 47 is designed as a differential gear, in particular as Stirnraddifferenzialgetriebe 48. In the embodiment shown in Fig. 6, no separate connection member 18 between a planet carrier 3 and the respective left or right rolling bearing 53 more available, but the bearing outer ring 49 of the respective rolling bearing 53 is modified to a connecting part 18 that he not only one conical tread 51 for the rolling elements 50 of the rolling bearing forms, but also firmly connected to the planet carrier 3. At the planet carrier 3 are planetary gear sets, each with a first planetary gear 5 and a second planetary gear 6 via a respective bolt 7, which is located in bearing sleeves 8, stored. The planet gears 5 and 6 are each provided with a special Ninth wheel 9 in operative contact. Here, the first planetary gear 5 with a first sun gear 10 in meshing engagement and the second planetary gear 6 with a second sun gear 11 in meshing contact. The bolt 7 is formed as a hollow bolt. In this embodiment, a collar portion 52 of each connecting part 18 and the bearing outer ring 49 axially further inward in the direction of the respective sun gear 10 or 11, as the collar portion 54 of the planet carrier 3. The bearing outer ring 49 is on its outer surface außenkonisch. Furthermore, the bearing outer ring 49 is formed as a pulled bearing outer ring. Between the sun gears 10 and 11, a friction disc 55 is arranged.

LIST OF REFERENCE NUMBERS

1 planetary gear

2 spur gear differential cups

3 planet carrier

4 planetary gear set

5 first planetary gear

6 second planetary gear

7 bolts

8 storage rings

9 sun wheel

10 first sun gear

1 1 second sun wheel

12 first half

13 second half

14 connecting element

15 drive wheel

16 spur gear

17 external helical toothing

18 connecting part

19 bearings

20 rolling bearings

21 first flange portion

22 connecting section

23 second flange portion

24 first interface

25 inner surface

26 second interface

27 outer surface

28 outer ring

29 inner ring

30 inner ring surface

31 fret 32 collar section of the planet carrier

33 collar portion of the connecting part

34 sprocket

35 lid

36 recess

37 friction disc

38 outer surface

39 caulking

40 shoulder

41 outer ring

42 career

43 planetary gear

44 career

45 outer ring

46 rolling elements

47 planetary gear

48 spur gear differential

49 bearing outer ring

50 rolling elements

51 tread

52 waistband section

53 rolling bearings

54 waistband section

55 friction disc

Claims

claims

1. planetary gear (1, 43, 47), such as a differential gear, with a planet carrier (3) on the planet gears (5, 6) are rotatably connected, which are in operative contact with at least one sun gear (9, 10, 11) the planet carrier (3) is connected to a drive wheel (15), characterized in that the planet carrier (3) is connected to a bearing (19) via a connection part (18) which is separate from it.

2. Planetary gear (1) according to claim 1, characterized in that the connecting part (8) is formed as a sheet metal part, preferably as a sheet metal sleeve, 3rd planetary gear (1) according to claim 2, characterized in that the sheet metal sleeve two by a connecting portion (22 ) connected cylindrical flange portions (21, 23).

4. planetary gear (1) according to one of claims 1, 2 or 3, characterized in that the bearing (19) is a rolling bearing (20, 53), wherein the connecting part (18) with an inner ring (29) or an outer ring ( 5. planetary gear (1) according to claim 4, characterized in that the one flange portion (21) has a first interface (24) which is connected to the planet carrier (3) and less far from a rotation axis about which rotates the planet carrier (3) is radially spaced, as a second interface (26) of the other flange portion (23) with the inner ring (29) or the outer ring ( 28) of the bearing (19) is in abutment. Planetary gear (1) according to claim 3, characterized in that the connecting portion (22) on the planet carrier (3) rests extending in the radial direction.

Planetary gear (1) according to claim 4, characterized in that the connecting part (18) on the inner ring (29) or on the outer ring (28) of the bearing (19) by a caulking (39) is secured.

Planetary gear (1) according to claim 1, characterized in that the connecting part (18) as a cover (35) is formed, which closes an opening between the planet carrier (3) and a sun gear (9, 10, 11).

9. planetary gear (1) according to claim 1, characterized in that the planetary gear (1) as Stirnraddifferenzial (2) is formed, the two sun gears (9, 10, 11), each with a planetary gear (5, 6) at least a planetary gear set (4) are in meshing engagement.

10. piano mesh according to claim 9, characterized in that the bearing (19) is a roller bearing (20, 53) with an inner ring (29) and an outer ring (28, 45, 49), wherein the connecting part of the outer ring (28,45 , 49).

11. Planetary gear according to claim 9, characterized in that the bearing (19) has an inner ring (29) and an outer ring (28, 45, 49), wherein the outer ring (28) rotatably connected to the planet carrier (3) and the bearing inner ring (29) is connected to a stationary housing

12. Planetary gear according to one of claims 1, 9, 10 or 11, with two bearings (19) wherein the bearings (19) angular contact bearings each having an inner ring (29) and an outer ring (28, 45, 49) and rolling elements between see the respective inner ring (29) and outer ring (28, 45, 49), wherein the arranged on both sides of the planetary gear angular contact bearings are arranged in an O arrangement.