DE102013206969A1 - Planetary gear bearing in a planetary gearbox - Google Patents

Abstract

The invention relates to a planetary gear bearing in a planetary gear, which essentially consists of a planetary gear carrier (1) with two side walls (2, 3) arranged parallel to one another, which have a plurality of planetary gear bolts (6) in a plurality of axial bores (4, 5) which are respectively axially opposite one another. Record on which a plurality of planet gears (7) are rotatably mounted via radial lubrication bearings (11, 12) permanently lubricated in the planet gear bores (8) and via axial and radial lubricant feed lines (9, 10) within the planet gear bolts (6). Between the side walls (2, 3) of the planet gear carrier (1) and the axial sides (13, 14) of the planet gears (7), ring-shaped thrust elements (15, 16) are arranged, which act as wear protection for the planet gear carrier (1) against the planet gears (7 ) and as an axial run-up for the radial roller bearings (11, 12) of the planet gears (7). According to the invention, the thrust elements (15, 16) between the side walls (2, 3) of the planet gear carrier (1) and the axial sides (13, 14) of the planet gears (7) are designed as low-friction axial needle bearings (17, 18), each of which consists of an axial angle disk (19, 20) with an outboard (21, 24), a flat raceway section (22, 25) and an inboard (23, 26) as well as two axial needle rings (27, 28, 29) arranged side by side in each axial angle disc (19, 20) , 30), which are each formed by an axial needle cage (31, 32, 33, 34) and a row of bearing needles (35, 36, 37, 38) held therein.

Description

Field of the invention

The invention relates to a Planetenradlagerung in a planetary gear according to the preamble forming features of claim 1, which is particularly advantageous to the arranged in car automatic transmissions planetary driven feasible.

Background of the invention

The most common embodiment of passenger car automatic transmissions are so-called converter transmissions, which differ from conventional and automated manual transmissions, above all by a traction-free switching operation. Such car automatic transmissions usually have a hydraulic torque converter as a starting clutch and consist essentially of several multi-plate clutches and a combination of several freewheels and planetary gears together. All switching and coupling operations are carried out via the multi-plate clutches, which produce the non-positive connection of the individual successively connected planetary gear with the input and output shaft of the automatic transmission. The individual planetary gear set up in a known manner from the coaxially arranged components, sun pinion, planet carrier and ring gear as well as from the planetary gears rotatably arranged at a constant center distance in the planet carrier. The input is via the sun pinion while on the planetary gears, the rotational movement is transmitted to the planet carrier (output shaft) and by the rolling of the planet gears in the ring gear, a corresponding translation.

The storage of planetary gears in such planetary gears is for example from the DE 44 18 693 C1 , of the DE 198 04 734 A1 or the DE 103 34 880 A1 known and consists essentially of two planetary carrier forming, mutually parallel side walls which receive a plurality of planetary pin in a plurality of axially opposite axial bores. In this Planetenradbolzen the planetary gears are rotatably ge-stored on centrally located in Planetenradbohrungen Radial roller bearings, which are usually designed as needle rims or full complement needle sets and are permanently lubricated via axial and radial lubricant supply lines within the Planetenradbolzen. In addition, two trained as annular thrust washers are arranged between the side walls of the planet carrier and the axial sides of each planetary gear, which are designed as wear protection of the mostly uncured Planetenradträgers against the hardened planetary gears and as Axialanlauf for the radial rolling bearings in the planetary gears. Thus, these thrust washers cause no accumulation of lubricant in the radial bearings of the Planetenrä-the through which it comes as a result of the lurching of the accumulated lubricant quantity to an undesirable increase in temperature of the lubricant and the radial roller bearing, it is known from the cited documents, the lubricant either on the inner diameter To dissipate the thrust washers molded recesses or by chordal grooves in the Planetenradbolzen through the thrust washers therethrough.

The disadvantage of such a Planetenradlagerung, however, is that caused by the thrust washers between the planetary gears and the planet carrier high power losses caused by the occurring between them and the planetary gears and the Radial rolling bearings sliding friction, so that with such planetary gears not in modern auto-Automatikgetrie-ben required high energy efficiency can be met. Likewise, the known measures on the thrust washers to improve the lubricant flow through the radial bearings proved to be inadequate, since the guided through the recesses in the thrust washers through this lubricant flow is stopped by the rear side of the thrust washers arranged side walls of the planet carrier and thus it still to the unwanted lubricant accumulation in the radial roller bearings of the planetary gears comes. In addition, the known Planetenradlagerung has proven to be disadvantageous also in view of the increased manufacturing costs for the planetary gears, as for the axial sides of the planet gears to reduce the sliding friction with the thrust washers a separate surface treatment by grinding and honing is necessary.

Object of the invention

Based on the stated disadvantages of the known prior art, the invention is therefore based on the object to design a Planetenradlagerung in a planetary gear, with which the resulting by sliding friction between the starting elements and the planetary gears and the Radialwälzlagern performance losses and a sufficient lubricant flow through the Radial rolling bearing can be realized and which at the same time allows a cheaper production of planetary gears.

Description of the invention

This object is achieved in a Planetenradlagerung according to the preamble of Claim 1 solved such that the thrust elements between the side walls of the planet carrier and the axial sides of the planet gears are designed as friction reduced axial needle bearings, each consisting of an axial angle disc with an outboard, a flat track section and an inboard and two in each Axialwinkelscheibe juxtaposed Axialnadelkränzen which are each formed by a Axialnadelkäfig and a number held therein bearing needles.

Preferred embodiments and advantageous developments of the inventively designed Planetenradlagerung are described in the subclaims 1 to 6.

Thereafter, it is provided according to claim 2 in the inventively designed Planetenradlagerung that each Axialnadellager formed from the diameter of the bearing needles and the material thickness of the Axialwinkelscheibe formed axial width of 0.8 mm minimum and against each previously used at the same place thrust washer with an axial width from 0.8 mm without changes to the surrounding construction is interchangeable. Since the most common for the Planetenradlagerung in automatic transmissions automatic thrust washers have a Mindestaxialbreite of 0.8 mm, it is thus possible to replace almost all thrust washers in the planetary gears of an automatic transmission against low-friction axial needle bearings. This has hitherto not been considered at all, since hitherto all attempts to produce axial needle bearings with such a small axial width have, due to the filigree design of the axial needle rings and the axial angle discs, proved to be extremely problematic with regard to the mechanical manufacturing and assembly processes.

According to claims 3 and 4, the inventively designed Planetenradlagerung is also characterized by the fact that the inner diameter of the outer Axialnadelkränze each Axialnadellagers is greater than the outer diameter of the inner Axialnadelkränze each Axialnadellagers and the axial sides of the planet gears exclusively in contact contact with the bearing needles of the outer Axialnadelkränze the axial needle bearings are, and that the radial roller bearings for each planet preferably as two each consisting of a cage and a plurality of bearing needles, juxtaposed radial needle rings are formed, which stand with their cages exclusively in contact with the bearing needles of the inner Axialnadelellanzen of Axialnadellager. This means that the inner axial needle ring of each axial needle bearing is arranged coaxially in the outer axial needle ring of the axial needle bearing and both axial needle rims can rotate independently of each other. Such a design is therefore particularly advantageous since the outer axial needle ring operatively connected to the planet gears must accommodate the full number of revolutions of the planet gears, while the inner axial needle ring operatively connected to the radial roller bearings of the planetary gears only has to absorb one revolution number known to be only half the planetary gear speed equivalent. With the use of two separate Axialnadelkränzen within a Axialnadelellager can thus be avoided compared to a Axialnadellager with only one Axialnadelkranz and only a number of longer bearing needles resulting from the different rotational speeds of the planetary gears relative to their radial rolling bearings high sliding components in the rolling contact of the bearing needles, which again to power losses within would contribute to the automatic transmission.

Finally, it is proposed as an advantageous embodiment of the inventively designed Planetenradlagerung by the claims 4 to 6 that the outer diameter of the outer Axialnadelkränze each Axialnadellagers slightly smaller than the inner diameter of the outer rims of the Axialwinkeldelad and the inner diameter of the inner Axialnadelkränze each Axialnadellagers slightly larger than the inner diameter of Inner rims of the Axialwinkelscheiben is formed. In this case, the Axialnadelkäfige the outer Axialnadelkränze at its outer diameter and the Axialnadelkäfi ge of the inner Axialnadelkränze at their inner diameter with the profile cross-section respectively parallel to the raceway sections of the Axialwinkelscheiben extending and directed to the Außenborden or Innenborden outer webs or inner webs, with which the Axialnadelkränze over several in the outer rims and in the inner rims of the axial angle discs uniformly circumferentially integrated punctate impressions in the axial angle discs can be clipped and secured against falling out of these.

In summary, the inventively designed Planetenradlagerung thus compared to the known from the prior art Planetenradlagerungen has the advantage that instead of the previously used between the side walls of the planet carrier and the axial sides of the planetary thrust washers now Axialnadellager with two separate Axialnadelkränzen are used, which the same Have axial width as the thrust washers and thus are interchangeable without changes in the surrounding structure. The Axialnadelellager thereby cause both the planetary gears and their radial roller bearings are now supported by rolling friction axially against the planet, so that the previously by sliding friction These losses are almost completely avoided. At the same time a sufficient lubricant flow through the radial roller bearings can be realized in the Planetenradlagerung invention, since the lubricant on the Axialwinkelscheiben and Axialnadelkränze the Axialnadellager at any time easily from the radial roller bearings of the planetary gears can be discharged. In addition, a more cost-effective production of the planetary gears is possible by the planetary gear according to the invention, since for the axial sides of the planet gears only a deferred surface treatment by grinding is necessary.

Brief description of the drawings

A preferred embodiment of the inventively designed Planetenradlagerung will be explained in more detail with reference to the accompanying drawings. Showing:

1 a partial spatial view of a cross section through a planetary gear with the inventively designed Planetenradlagerung;

2 an enlarged view of the detail X of the inventively designed Planetenradlagerung according to 1 ;

3 a partial spatial view of a cross section through an axial needle bearing of the inventively designed Planetenradlagerung.

Detailed description of the drawings

1 clearly shows a Planetenradlagerung in a planetary gear, wel-che essentially from a planet carrier 1 with two side walls arranged parallel to one another 2 . 3 consists in several each axially coaxial axial bores 4 . 5 a plurality of planet gear bolts 6 take up. On the planet wheel bolt 6 There are several planet gears 7 over into central planetary bores 8th used radial roller bearings 11 . 12 rotatably mounted, via axial and radial lubricant supply lines 9 . 10 inside the planet wheel bolts 6 be permanently lubricated. In addition, between the side walls 2 . 3 of the planet carrier 1 and the axial sides 13 . 14 the planet wheels 7 annular disk-shaped starting elements 15 . 16 arranged, which as wear protection of the planet carrier 1 opposite the planet wheels 7 and as an axial stop for the radial rolling bearings 11 . 12 the planet wheels 7 are formed.

Out 2 goes out further that the annular disc-shaped thrust elements 15 . 16 between the side walls 2 . 3 of the planet carrier 1 and the axial sides 13 . 14 the planet wheels 7 according to the invention as friction-reduced axial needle bearings 17 . 18 are formed, each consisting of a Axialwinkelscheibe 19 . 20 with an outboard 21 . 24 , a level track section 22 . 25 and an inboard 23 . 26 as well as two in each Axialwinkelscheibe 19 . 20 arranged side by side Axialnadelkränzen 27 . 28 . 29 . 30 exist, each by a Axialnadelkäfig 31 . 32 . 33 . 34 and a number of bearing needles held therein 35 . 36 . 37 . 38 be formed. In this case, have the Axialnadellager 17 . 18 as indicated, one each from the diameter of the bearing needles 19 . 20 and the material thickness of the axial angle disc 17 . 18 formed axial width B _A of at least 0.8 mm and are thus interchangeable with any thrust washer previously used at the same place with an axial width from 0.8 mm without changes in the surrounding structure.

In addition, is off 2 it can be seen that the inner diameter of the outer Axialnadelkränze 27 . 29 each axial needle bearing 17 . 18 larger than the outer diameter of the inner Axialnadelkränze 28 . 30 each axial needle bearing 17 . 18 is and the axial sides 13 . 14 the planet wheels 7 only in contact with the bearing needles 35 . 37 the outer axial needle rims 27 . 29 the axial needle bearing 17 . 18 stand. Likewise goes out 2 apparent that the radial rolling bearings 11 . 12 for every planetary gear 7 preferably as two each from a cage 39 . 40 and a variety of bearing needles 41 . 42 existing, arranged side by side radial needle rims 43 . 44 are trained with their cages 39 . 40 only in contact with the bearing needles 36 . 38 the inner axial needle rims 28 . 30 the axial needle bearing 17 . 18 stand.

Finally, in 3 to clearly see that the outer diameter of the outer Axialnadelkränze 27 . 29 each axial needle bearing 17 . 18 slightly smaller than the inside diameter of the outboard 23 . 26 the axial angle discs 19 . 20 and the inner diameter of the inner Axialnadelkränze 28 . 30 each axial needle bearing 17 . 18 slightly larger than the inner diameter of the inner rims 21 . 24 the axial angle discs 19 . 20 is trained. In this case, the Axialnadelkäfige 31 . 33 the outer axial needle rims 27 . 29 on its outer diameter and the Axialnadelkäfige 32 . 34 the inner axial needle rims 28 . 30 at their inner diameter in the profile cross section in each case parallel to the raceway sections 22 . 25 the axial angle discs 19 . 20 running and to their outboards 21 . 24 or inner rims 23 . 26 directed outer webs 45 . 46 or inner webs 47 . 48 on, with which the Axialnadelkränze 27 . 29 over several in the outboard 21 . 24 and in the inner rims 23 . 26 the axial angle discs 19 . 20 Evenly distributed around punctiform imprints 49 . 50 . 51 . 52 into the axial angle discs 19 . 20 be clipped and secured against falling out of these.

LIST OF REFERENCE NUMBERS

1

 planet

2

Sidewall of 1

3

Sidewall of 1

4

Axial bore in 2

5

Axial bore in 3

6

 pinion pin

7

 planet

8th

 Planetenradbohrung

9

axial lubricant supply in 6

10

radial lubricant supply in 6

11

Radial rolling bearings in 8th

12

Radial rolling bearings in 8th

13

Axial side of 7

14

Axial side of 7

15

 thrust element

16

 thrust element

17

 axial needle

18

 axial needle

19

Axial angle disc of 25

20

Axial angle disc of 26

21

Outboard of 19

22

Runway section of 19

23

Inboard of 19

24

Outboard of 20

25

Runway section of 20

26

Inboard of 20

27

outer axial needle ring of 17

28

inner axial needle ring of 17

29

outer axial needle ring of 18

30

inner axial needle ring of 18

31

Axial needle cage of 27

32

Axial needle cage of 28

33

Axial needle cage of 29

34

Axial needle cage of 30

35

Needles from 27

36

Needles from 28

37

Needles from 29

38

Needles from 30

39

Cage of 43

40

Cage of 44

41

Needles from 43

42

Needles from 44

43

Radial needle ring of 11

44

Radial needle ring of 12

45

Outer bridge of 31

46

Inner bridge of 32

47

Outer bridge of 33

48

Inner bridge of 34

49

Imprints in 21

50

Imprints in 23

51

Imprints in 24

52

Imprints in 26

B _A

Axial width of 17 respectively. 18

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

• DE 4418693 C1 [0003]
• DE 19804734 A1 [0003]
• DE 10334880 A1 [0003]

Claims (7)

Planetenradlagerung in a planetary gear, consisting essentially of a planet carrier ( 1 ) with two side walls arranged parallel to one another ( 2 . 3 ), which in several axially opposite axial bores ( 4 . 5 ) a plurality of planetary pin ( 6 ), on which several planet gears ( 7 ) into central planetary gear bores ( 8th ) and via axial and radial lubricant supply lines ( 9 . 10 ) within the planetary pin ( 6 ) permanently lubricated radial roller bearings ( 11 . 12 ) are rotatably mounted, wherein between the side walls ( 2 . 3 ) of the planet carrier ( 1 ) and the axial sides ( 13 . 14 ) of planetary gears ( 7 ) annular disk-shaped starting elements ( 15 . 16 ) are arranged, which as wear protection of the planet carrier ( 1 ) with respect to the planetary gears ( 7 ) and as Axialanlauf for the radial rolling bearings ( 11 . 12 ) of planetary gears ( 7 ) are formed, characterized in that the starting elements ( 15 . 16 ) between the side walls ( 2 . 3 ) of the planet carrier ( 1 ) and the axial sides ( 13 . 14 ) of planetary gears ( 7 ) as a friction-reduced axial needle bearing ( 17 . 18 ) are formed, each from an axial angle disc ( 19 . 20 ) with an outboard ( 21 . 24 ), a flat track section ( 22 . 25 ) and an inboard ( 23 . 26 ) as well as two in each Axialwinkelscheibe ( 19 . 20 ) Axialnadelkränzen arranged side by side ( 27 . 28 . 29 . 30 ), each by a Axialnadelkäfig ( 31 . 32 . 33 . 34 ) and a number of bearing needles ( 35 . 36 . 37 . 38 ) are formed. Planetenradlagerung according to claim 1, characterized in that each Axialnadellager ( 17 . 18 ) one from the diameter of its bearing needles ( 35 . 36 . 37 . 38 ) and the material thickness of its Axialwinkelscheibe ( 19 . 20 ) formed axial width (B _A ) of at least 0.8 mm and is exchangeable against any previously used at the same place thrust washer with an axial width from 0.8 mm without changes in the surrounding structure. Planetenradlagerung according to claim 2, characterized in that the inner diameter of the outer Axialnadelkränze ( 27 . 29 ) of each axial needle bearing ( 17 . 18 ) greater than the outer diameter of the inner Axialnadelkränze ( 28 . 30 ) of each axial needle bearing ( 17 . 18 ) and the axial sides ( 13 . 14 ) of planetary gears ( 7 ) exclusively in contact with the bearing needles ( 35 . 37 ) of the outer Axialnadelkränze ( 27 . 29 ) the axial needle bearing ( 17 . 18 ) stand. Planetenradlagerung according to claim 3, characterized in that the radial rolling bearings ( 11 . 12 ) for each planetary gear ( 7 ) preferably as two each from a cage ( 39 . 40 ) and a plurality of bearing needles ( 41 . 42 ) existing, juxtaposed Radialnadelkränze ( 43 . 44 ) formed with their cages ( 39 . 40 ) exclusively in contact with the bearing needles ( 36 . 38 ) of the inner axial needle rims ( 28 . 30 ) the axial needle bearing ( 17 . 18 ) stand. Planetenradlagerung according to claim 4, characterized in that the outer diameter of the outer Axialnadelkränze ( 27 . 29 ) of each axial needle bearing ( 17 . 18 ) slightly smaller than the inner diameter of the outer rims ( 23 . 26 ) of the axial angle discs ( 19 . 20 ) and the inner diameter of the inner Axialnadelkränze ( 28 . 30 ) of each axial needle bearing ( 17 . 18 ) slightly larger than the inner diameter of the inner rims ( 21 . 24 ) of the axial angle discs ( 19 . 20 ) is trained. Planetenradlagerung according to claim 5, characterized in that the Axialnadelkäfige ( 31 . 33 ) of the outer Axialnadelkränze ( 27 . 29 ) at its outer diameter and the Axialnadelkäfige ( 32 . 34 ) of the inner axial needle rims ( 28 . 30 ) at its inner diameter in the profile cross section in each case parallel to the raceway sections ( 22 . 25 ) of the axial angle discs ( 19 . 20 ) and their outboards ( 21 . 24 ) or inner rims ( 23 . 26 ) directed outer webs ( 45 . 47 ) or inner webs ( 46 . 48 ) exhibit. Planetenradlagerung according to claim 6, characterized in that in the outer rims ( 21 . 24 ) and in the inner rims ( 23 . 26 ) of the axial angle discs ( 19 . 20 ) each have a plurality of uniformly circumferentially distributed punctiform impressions ( 49 . 50 . 51 . 52 ) are incorporated, over which the Axialnadelkränze ( 27 . 28 . 29 . 30 ) with the outer webs ( 45 . 47 ) or inner webs ( 46 . 48 ) of their axial needle cages ( 31 . 32 . 33 . 34 ) into the axial angle discs ( 19 . 20 ) Can be clipped and secured against falling out of these.

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