WO2012004329A1

WO2012004329A1 - Rolling bearing

Info

Publication number: WO2012004329A1
Application number: PCT/EP2011/061472
Authority: WO
Inventors: Siegfried Tisch; Tilmann RÖMHELD
Original assignee: Schaeffler Technologies Gmbh & Co. Kg
Priority date: 2010-07-08
Filing date: 2011-07-07
Publication date: 2012-01-12
Also published as: DE102010026544A1

Abstract

The invention relates to a rolling bearing, in particular a camshaft rolling bearing, for the mounting of a camshaft (12a, 13a; 12b) of a motor vehicle, the rolling bearing comprising an outer connection unit (14a;14b) with at least one outer ring (15a; 15b). According to the invention, the outer connection unit (14a; 14b) comprises at least one support ring (17a; 17b) which is provided for at least partially reinforcing at least the outer ring (15a; 15b).

Description

Name of the invention

The invention relates to a rolling bearing according to the preamble of claim 1.

From DE 10 2007 020 306 A1 is already a rolling bearing, in particular a camshaft roller bearing for supporting a camshaft of a motor vehicle, with an external connection unit having at least one outer ring known.

The invention is in particular the object of increasing the stability of the rolling bearing with little space required. It is achieved according to the invention by the features of claim 1. Further refinements emerge from the subclaims.

The invention relates to a rolling bearing, in particular of a camshaft rolling bearing for supporting a camshaft of a motor vehicle, with an external connection unit, which has at least one outer ring.

It is proposed that the external connection unit has at least one support ring, which is intended to at least partially stiffen the outer ring. As a result, in particular, a stable outer ring with a small outer wall thickness can be realized, as a result of which a required installation space or a required storage space is reduced. Thus, by means of an embodiment according to the invention, a shaft can be mounted in the absence of a local bearing surface or in the case of an interrupted bearing surface of the outer ring. Preferably, the shaft is formed as a camshaft. A "bearing surface" is to be understood in particular as a surface of the outer ring, with which the outer ring is supported on a bearing receptacle, for example on a cylinder head. Space or storage space "should in particular a radial space or storage space to be understood. "Provided" is to be understood in particular to be specially equipped and / or designed.

It is further proposed that the support ring is provided to fix the outer ring axially to a bearing receptacle. As a result, a particularly advantageous roller bearing can be provided. The term "bearing receptacle" is to be understood in particular as meaning a component which is arranged stationary with respect to the shaft The bearing receptacle may be formed integrally with a stationary component connected to the stationary component.

It is also proposed that the support ring is arranged between two end faces of the outer ring. This allows a particularly advantageous fixation of the outer ring can be realized. In particular, a bearing of the shaft can be realized without a separate bearing bridge. An "end face" should be understood to mean, in particular, a side which defines an axial extent of the outer ring or the support ring, Preferably an end face defines a beginning or an end of the outer ring or of the support ring In particular, an arrangement can be understood in which at least one end face and preferably two end faces of the support ring are located axially with respect to a longitudinal axis of the outer ring within the end faces of the outer ring. Particularly advantageously, the end faces of the support ring are arranged between two bearing surfaces of the outer ring. With regard to a mounting of the rolling bearing, a central arrangement of the support ring on the outer ring is preferred.

In particular, it is advantageous if the support ring surrounds the outer ring circumferentially. As a result, an advantageous load capacity of the outer ring can be achieved. By "circumferential" is intended in particular to be understood a course which extends at least partially and preferably completely along a circumference of the outer ring. Furthermore, it is advantageous if the support ring is pressed onto the outer ring. As a result, an arrangement of the support ring on the outer ring can be simplified manufacturing technology. Preferably, the support ring on the outer ring can also be upset. In principle, the support ring and the outer ring can also be formed in one piece.

Particularly preferably, the support ring is designed in several parts. As a result, the support ring can be made particularly simple. In principle, the outer ring can also be designed in several parts.

Moreover, it is advantageous if the support ring is at least partially formed from Blechumformteilen. Thereby, the axial fixation of the outer ring and a simultaneous holding a rolling cage of the rolling bearing can be realized.

Further advantages emerge from the following description of the drawing. In the drawings, two embodiments of the invention are shown. The drawings, the description and the claims contain numerous features in combination. The person skilled in the art will expediently also consider the features individually and combine them into meaningful further combinations.

Showing:

Fig. 1 shows a shaft bearing device with several inventive

roller bearings,

2 shows the rolling bearing according to the invention,

Fig. 3 is a schematic representation of a cross section of the rolling bearing and

4 shows a shaft bearing device with an alternatively configured

Roller bearing.

FIG. 1 shows an exemplary embodiment of a shaft bearing device. The shaft bearing device is formed as a camshaft bearing device. To actuate valves, not shown, of a reciprocating internal combustion engine of a motor vehicle, the shaft bearing device has two camshafts 12a, 13a with cams 21a, 22a, 23a, 24a. A position 25a and a position 26a of the valves is just below the cams 21a, 22a and the cams 23a, 24a. For connecting a cylinder head 47a with a cylinder head gasket and a crankcase, the reciprocating internal combustion engine further on cylinder head screws not shown in detail. The cylinder head bolts are arranged in a position 27a and a position 28a on the cylinder head 47a.

For storage of the two camshafts 12a, 13a of the motor vehicle, the shaft bearing device comprises a plurality of roller bearings 10a, 11a according to the invention. The rolling bearings 10a, 11a are designed as a camshaft rolling bearing. In principle, an inventive rolling bearing can still be used at other locations of the shaft bearing device. The rolling bearing 10a supports the camshaft 12a and the rolling bearing 11a rotatably supporting the camshaft 13a relative to the cylinder head 47a. The rolling bearings 10a, 11a are arranged between the cylinder head 47a and a cylinder head cover, not shown. The roller bearing 10a has an inner connection unit 29a, an outer connection unit 14a and a rolling unit 30a (see FIG. 2). The rolling unit 30a has a roller cage 31a, pockets 32a and rolling elements 33a. The pockets 32a are formed as recesses in the roller cage 31 a. The rolling elements 33a are arranged in the pockets 32a. A number of pockets 32a correspond to a number of rolling elements 33a. The rolling elements 33 a each have an axial length which is smaller than an axial length of the rolling cage 31 a. The rolling elements 33a are in the form of cylindrical rollers. The rolling bearing 10a is formed as a needle bearing. In order to form a first raceway for the rolling elements 33a, the inner connection unit 29a has an inner ring 34a. The raceway is formed as an outer peripheral surface of the inner ring 34a on which the rolling elements 33a roll. The inner ring 34a has an axial length 35a that is greater than the axial length of the rolling elements 33a. The axial length of the rolling elements 33a and the axial length 35a of the inner ring 34a are at least equal. The inner connection unit 29a is non-rotatably mounted on the camshaft 12a. The axial length 35a of the inner ring 34a is 25 mm in this embodiment.

To form a second raceway for the rolling elements 33a, the outer connection unit 14a has a single outer ring 15a. The raceway is formed as an inner circumferential surface of the outer ring 15a, on which the rolling elements 33a roll. The outer ring 15a has two end faces 19a, 20a which axially bound the outer ring 15a, i. define an axial length 36a of the outer ring 15a. The end faces 19a, 20a are spaced from each other by the axial length 36a. The axial length 36a of the outer ring 15a is greater than the axial length of the rolling elements 33a and greater than the axial length 35a of the inner ring 34a. The axial length of the rolling elements 33a and the axial length 36a of the outer ring 15a are at least equal. The outer ring 15a is rotatably connected to the cylinder head 47a. The outer ring 15a is arranged stationary with respect to the cylinder head 47a. Thus, the roller cage 31 a and thus the inner ring 34 a is rotatably supported relative to the outer ring 15 a. The axial length 36a of the outer ring 15a is 28 mm in this embodiment. The two end faces 19a, 20a thus have a spacing of 28 mm. An inner radius 41 a of the outer ring 15 a is 19.25 mm. An outer radius 42a of the outer ring 15a is 21, 00 mm. An outer wall thickness 43a of the outer ring 15a is thus 1.75 mm (see Fig. 3).

For stiffening or for reinforcing the outer ring 15a and for axially fixing the outer ring 15a to a bearing receptacle 16a, the outer connection unit 14a has a support ring 17a. The support ring 17a has two end faces 37a, 38a which axially delimit the support ring 17a, ie define an axial length 39a of the support ring 17a. The two end faces 37a, 38a are spaced from each other by the axial length 39a. The axial length 39a of the support ring 17a is smaller than the axial length 36a of the outer ring 15a. The support ring 17a is arranged between the two end faces 19a, 20a of the outer ring 15a. net. The end faces 37a, 38a of the support ring 17a are arranged offset to the end faces 19a, 20a of the outer ring 15a. The support ring 17a circumferentially surrounds the outer ring 15a. The support ring 17a is pressed onto the outer ring 15a. In this embodiment, the bearing receptacle 16a is formed integrally with the stationary cylinder head 47a. The bearing receiver 16 a is formed as a groove in the cylinder head 47 a. The support ring 17a thus fixes the outer ring 15a axially on the cylinder head 47a. The support ring 17a engages in the bearing receptacle 16a and thus in the groove, whereby the outer ring 15a is axially fixed by a positive connection. Due to the axial fixation of the outer ring 15a, the roller bearing 10a is axially fixed.

A dimensioning of the support ring 17a and an arrangement on the outer ring 15a of the support ring 17a is selected from a load of the outer ring 15a, a support surface of the outer ring 15a and an available space within certain limits. The axial length 39a of the support ring 17a is 5 mm in this embodiment. The two end faces 37a, 38a thus have a spacing of 5 mm. A distance 44a from an axial center of the support ring 17a and the end face 19a of the outer ring 15a is 12.5 mm. The end face 3a7 of the support ring 17a and the end face 19a of the outer ring 15a are thus 10 mm axially apart from each other. The support ring 17a has an outer radius 45a of 25.00 mm. The support ring 17a thus has a radial projection 46a of 4 mm over the outer ring 15a.

The rolling bearing 10a and the rolling bearing 1 1 a are identical. An inner ring of the rolling bearing 1 1 a is rotatably mounted on the camshaft 13 a. An outer ring of the rolling bearing 1 1 a is rotatably connected to the cylinder head 47a. A support ring 18a of the bearing 1 1 a fixes the outer ring of the bearing 1 1 a and thus the roller bearing 1 1 a axially to a bearing receptacle 16a 'and stiffened at the same time the outer ring of the bearing 1 1 a.

The rolling bearing 10a is disposed above the position 27a of the cylinder head bolt and the rolling bearing 1 1 a above the position 28a of the cylinder head bolt and thus overbuilt the cylinder head bolts in the assembled state. Along In one direction 40a, the support rings 17a, 18a are arranged in front of the positions 27a, 28a of the cylinder head bolts. The rolling bearings 10a, 1 1 a are only partially with their contact surfaces on the cylinder head 47a. The support ring 17a is arranged between the bearing surfaces of the outer ring 15a on the outer ring 15a. The support ring 18a is disposed between the bearing surfaces of the outer ring of the rolling bearing 1 1 a on the outer ring of the rolling bearing 1 1 a.

FIG. 4 shows a further exemplary embodiment of the invention. The following description is essentially limited to the differences between the exemplary embodiments, reference being made to the description of the other exemplary embodiment, in particular FIGS. 1 to 3, with regard to components, features and functions remaining the same. In order to distinguish the exemplary embodiments, the letter a in the reference symbols of the exemplary embodiment in FIGS. 1 to 3 is replaced by the letter b in the reference symbols of the exemplary embodiment of FIG. With regard to identically named components, in particular with regard to components with the same reference numerals, reference may in principle also be made to the drawings and / or the description of the other exemplary embodiment, in particular FIGS. 1 to 3.

FIG. 4 shows an alternative designed rolling bearing 10b. The rolling bearing 10b supports a camshaft 12b. The rolling bearing 10b has an inner connection unit 29b, an outer connection unit 14b and a rolling unit 30b. The inner connection unit 29b has an inner ring 34b and the rolling unit 30b has a plurality of rolling elements 33b.

In contrast to the previous embodiment, the external connection unit 14b is designed in three parts. The external connection unit 14b comprises a single outer ring 15b, a first support ring element 48b and a second support ring element 49b. The outer ring 15b is formed as a cylindrical hollow body. The support ring member 48b and the support ring member 49b are also each formed as a cylindrical hollow body. The support Ring member 48b is pushed from one side onto the outer ring 15b and the support ring member 49b from another side on the outer ring 15b. The support ring members 48b, 49b form a support ring 17b and act as the support ring 17b. The support ring 17b is formed in two parts. The outer ring 15b is integrally formed. The formed as a hollow body outer ring 15b and formed as a hollow body support ring elements 48b, 49b are each formed as a sleeve.

The support ring 17b stiffens the outer ring 15b. The external connection unit 14b is composed of a plurality of parts, in which embodiment the outer ring 15b consists of one part and the support ring 17b is composed of two parts. In principle, the outer ring 15b can also be designed in several parts. The support ring 17b can in principle also be formed from more than two support ring elements.

To form the support ring 17b, the support ring element 48b has a part 50b and the support ring element 49b has a part 51b. The parts 50b, 51b are respectively disposed on axially inwardly facing sides of the respective support ring member 48b, 49b. The part 50b of the support ring element 48b and the part 51b of the support ring element 49b extend radially outwards in the direction of a bearing receptacle 16b. The bearing receiver 16b is formed as a groove in a cylinder head 47b. The support ring 17b is formed by the part 50b of the support ring member 48b and the part 51b of the support ring member 49b. The part 50b and the part 51b and thus the support ring 17b engage in the bearing receptacle 16b, whereby the support ring member 48b and the support ring member 49b and thus the outer ring 15b are axially fixed to the bearing receptacle 16b. The part 50b and the part 51b and thus the support ring 17b are realized by a deformation of the support ring elements 48b, 49b. For simultaneously holding a roller cage 31b of the rolling unit 30b, the support ring member 48b has a part 52b and the support ring member 49b has a part 53b. The parts 52b, 53b are respectively disposed on axially outwardly facing sides of the respective support ring member 48b, 49b. The part 52b is at a Front side 19b of the outer ring 15b and the part 53b disposed on an end face 20b of the outer ring 15b. The part 52b of the support ring member 48b and the part 53b of the support ring member 49b extend radially inward in the direction of the camshaft 12b. The outer ring 15b and the roller cage 31b are surrounded by the support ring member 48b and the support ring member 49b. The outer ring 15b is disposed radially between the rolling element 33b and the support ring elements 48b, 49b. The outer ring 15b is disposed axially between the parts 52b, 53b and thus axially within the support ring elements 48b, 49b. The support ring 17b is formed by two deep-drawn sleeves. The part 52b and the part 53b are realized by a deformation of the support ring elements 48b, 49b. The support ring member 48b and the support ring member 49b are each formed as a sheet metal part. The support ring 17b is thus formed by two Blechumformteile.

In principle, the outer connection unit 14b may be formed in two parts, the outer ring 15b being formed integrally with the support ring elements 48b, 49b. On the outer ring 15b as a separate component is omitted. The support ring elements 48b, 49b of such a configuration of the external connection unit 14b form the outer ring 15b. The support ring elements 48b, 49b form a raceway for the rolling elements 33b. The support ring elements 48b, 49b thus rest on the rolling element 33b.

Claims

claims

1. Rolling bearing, in particular a camshaft roller bearing for supporting a camshaft (12a, 13a, 12b) of a motor vehicle, having an outer connection unit (14a, 14b) which has at least one outer ring (15a, 15b), characterized in that the outer connection unit ( 14a, 14b) has at least one support ring (17a, 17b) which is intended to at least partially stiffen at least the outer ring (15a, 15b).

2. Rolling bearing according to claim 1, characterized in that the support ring (17a, 17b) is provided to fix the outer ring (15a, 15b) axially on a bearing seat (16a, 16b).

3. Rolling bearing according to claim 1 or 2, characterized in that the support ring (17a, 17b) between two end faces (19a, 20a, 19b, 20b) of the outer ring (15a, 15b) is arranged.

4. Rolling bearing according to one of the preceding claims, characterized in that the support ring (17a, 17b) surrounds the outer ring (15a, 15b) circumferentially.

5. Rolling bearing according to one of the preceding claims, characterized in that the support ring (17 a) on the outer ring (15 a) is pressed.

6. Rolling bearing according to one of the preceding claims, characterized in that the supporting ring (17b) is designed in several parts.

7. Rolling bearing according to claim 6, characterized in that the support ring (17b) is at least partially formed from Blechumformteilen.

8. shaft bearing device, in particular a Nockenwellenlagervomchtung, with at least one rolling bearing (10a, 1 1 a; 10b, 1 1 b) according to any one of the preceding claims.