EP1880123A1

EP1880123A1 - Four-row tapered roller bearing

Info

Publication number: EP1880123A1
Application number: EP06722841A
Authority: EP
Inventors: Werner RÖMLING
Original assignee: INA Schaeffler KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2005-05-13
Filing date: 2006-05-06
Publication date: 2008-01-23
Also published as: US7871202B2; US20080193066A1; DE102005022205A1; WO2006119738A1

Abstract

The invention relates to a four-row tapered roller bearing (1) for machine mountings, with an inner ring (2) of two-part design axially and an outer ring (3) of single- or multi-part design axially, with an inner and/or an outer tapered-roller row (4, 5; 7, 6) being supported in each case by an inner ring part (2a, 2b). In order, firstly, to confer a large supporting width on the bearing and, secondly, to ensure as optimum as possible and as uniform as possible a loading of the rolling bodies in the form of the tapered rollers (8), the tapered-roller rows (4, 5, 6, 7) are arranged in an O-arrangement, and the roller axles (13) of the respectively adjacent outer and inner tapered rollers (8) of the two respectively adjacent outer and inner tapered-roller rows (4, 5; 7, 6) are arranged at an inclination in such a manner that those lines of influence (14) of the tapered rollers (8) which characterize the pressure angles (a<SUB>1</SUB>, a<SUB>2</SUB>) intersect in the region of the axis of rotation of the tapered roller bearing (1). In addition to other advantages, this bearing can be produced more cost-effectively and, with regard to production quality, more reliably than known four-row tapered roller bearings.

Description

Name of the invention

Four row tapered roller bearing

description

Field of the invention

The invention relates to a four-row tapered roller bearing, for example, for machine-building bearings such as planetary bearings or rolling mill bearings, with an axially formed two-part inner ring and an axially single or multi-part outer ring, each an outer and an inner tapered roller row are supported by an inner ring part.

Background of the invention

Tapered roller bearings have been known for a long time. For example, US Pat. No. 2,130,258 describes tapered roller bearings in tandem, X and O construction in which the tapered rollers are supported by substantially identically formed one- or multi-part inner rings and substantially identically designed multi-part outer rings. Furthermore, from this document, a four-row tapered roller bearing in X- or O-construction known in which the respective axially outer tapered roller row and the adjacent axially inner tapered roller row tapered rollers have the same size and rectified arranged and where accordingly their pressure angle are the same.

A disadvantage of this tapered roller bearing that this consists of very many individual parts, which increases the assembly costs and the manufacturing cost.

In contrast, DE 41 42 802 A1 discloses a four-row tapered roller bearing, which provides the combinations of an O-arrangement with an X-arrangement by the tapered rollers are arranged between an axially multi-part inner ring and an axially multi-part outer ring and the inner roller rows in O Arrangement and the adjacent outer roller rows are formed in X-arrangement. Also, this tapered roller bearing is disadvantageous from comparatively many items.

From practice, it is also known that bearing in O arrangement of the bearing give a large support width and this is very rigid and receptive for large tilting moments. By contrast, bearings in the X arrangement have a small support width and rigidity, and their capacity for tilting moments is accordingly also smaller than in an O arrangement.

In addition, it is known that in four-row tapered roller bearings for a bearing in itself a statically indeterminate storage is recorded, which in turn can lead due to the elasticity of the surrounding parts and the rolling elements to a different Wälzkörperbelastung and in consequence to a reduced life of the storage system , This is where the invention described below begins.

Object of the invention

The invention has for its object to provide an improved four-row tapered roller bearing, which for example for mechanical bearing arrangements such as planetary gear bearings, rolling mill bearings and the like bes- least, and which gives the bearing a large support width on the one hand and makes them very rigid and receptive for large tilting moments, and on the other hand ensures the best possible or even load on the rolling elements. In addition, this tapered roller bearing should include as few items as possible, so that its production is significantly cheaper than in known four-row tapered roller bearings.

Summary of the invention

Starting from a four-row tapered roller bearing for machine building bearings, with an axially formed two-part inner ring and an axially single or multi-part outer ring in each of which an outer and an inner row of tapered rollers are supported by an inner ring part, the above object is achieved in that the tapered roller rows in an O-arrangement are arranged so that the roller axes of the respective adjacent axially outer and inner tapered rollers of the two adjacent axially outer and inner tapered roller rows are arranged inclined so that the pressure angle CH, α ₂ characteristic lines of action of the tapered rollers in the region of the axis of rotation of Cutting tapered roller bearing, and that each inner ring part results in a double support or statically determined support. Accordingly, in this four-row tapered roller bearing, starting from the axial center of the bearing, the tapered rollers are axially aligned immediately adjacent axially inner and outer tapered roller rows at different angles to the axis of rotation of the bearing.

An independent design solves according to the features of claim 2, the task by a four-row tapered roller bearing for machine building bearings, with an axially two-piece inner ring and an axially integrally formed or multi-part outer ring, each having an axially outer and / or an axially inner tapered roller row of a Inner ring part are worn, the tapered roller rows arranged in an O-arrangement and the roller axes of the respective adjacent outer and inner tapered rollers of the two adjacent outer and inner tapered roller rows are arranged inclined so that the pressure angles CH, cfc characterizing lines of action of the tapered rollers do not intersect in the region of the axis of rotation of the tapered roller bearing, and each inner ring part a twofold -Abstützung or a statically determined support results.

In contrast to the technical solution according to claim 1, in this design, starting from the axial center of the bearing, the tapered rollers are axially aligned immediately adjacent axially inner and outer tapered roller rows at the same angle to the axis of rotation of the bearing. Therefore, the lines of action of the axially immediately adjacent inner and outer tapered rollers are aligned substantially parallel to each other.

Due to the described constructions, a comparatively rigid bearing with comparatively few individual parts is created, which is particularly suitable for dynamic load cases and avoids uneven wear of the tapered roller rows, along with increased noise pollution and a reduction in service life or running time of the bearing. Furthermore, by this measure, for example, a disadvantageous tumbling of example planetary wheels in no-load operation prevented, since the storage is always determined statically by said double support per inner ring part. Due to the fact that the bearing is optimized for the dynamic load case, the safety is also improved or the surface pressure is reduced and any edge pressure is avoided under a static stress on the bearing. In addition, this tapered roller bearing can be cheaper and easier to produce with consistent quality, as was possible with previously known generic tapered roller bearings.

The subclaims describe preferred developments or refinements of the invention. Thereafter, it is envisaged that support rims can be arranged for axial support of the tapered rollers depending on the application both on the inner and on the outer ring. Furthermore, it is proposed that the spacings of the support rims and, accordingly, the axial length of the tapered rollers are designed for equal loads on the rows of tapered rollers, depending on certain boundary conditions, such as a possible deformation of the conversion parts. In that regard, with respect to the two inner ring parts, the distances of the support rims and accordingly the axial lengths of the tapered rollers may be chosen differently.

Furthermore, it may be indicated that the number of tapered rollers, at least in two of the rows of tapered rollers, deviates from the selected number of tapered rollers in the remaining rows of tapered rollers.

Also, it has proved to be useful to apply the tapered rollers of the two inner tapered roller rows with a bias or a relation to the other tapered roller rows other axial play, preferably a smaller axial play. As a result, a more homogeneous load distribution and a further noise reduction in no-load or low-load operation is possible.

In addition, it may be expedient to reduce the manufacturing costs to form the one- or multi-part outer ring by a raceways for the tapered rollers exhibiting planet or other wheel.

Finally, with regard to the point of intersection of the lines of action of the tapered rollers, it is preferred that this point of intersection lies less than 10% of the outer bearing diameter away from the axis of rotation of the tapered roller bearing.

Overall, it can be stated that the construction of a four-row tapered roller bearing according to the invention requires comparatively few individual parts, whereby the number of mating surfaces and measuring surfaces on such a bearing is significantly reduced. It is therefore understandable that such a bearing is particularly inexpensive and yet produced with high quality. Brief description of the drawings

The invention will be explained in more detail below with reference to the accompanying drawings of some embodiments. The single FIGURE shows a four-row tapered roller bearing according to the invention in a schematic sectional view.

Detailed description of the drawings

The tapered roller bearing 1 shown in the drawing is suitable for machine building bearings, in particular for planetary bearings, rolling mill bearings, etc. It is composed of a split inner ring 2 with two inner ring parts 2a, 2b and an outer ring 3 with two outer ring parts 3a, 3b and four between the inner ring and outer ring parts 2a, 2b, 3a, 3b arranged tapered roller rows 4, 5, 6, 7 together, wherein each row of conical rollers 4, 5, 6, 7 has a plurality of tapered rollers 8, which in turn are held by a known per se and accordingly not shown in detail at least one cage.

Through the two outer ring parts 3a, 3b, a radially outer annular groove 9 is formed in the assembly, which in turn merges into at least one radial bore not shown in detail. Furthermore, a lubrication groove 10 is provided in the connection region of the two inner ring parts 2a, 2b.

In the present case, two pairs of tapered rollers 5 and 6 or 7 and 8 are each supported by an inner ring part 2a or 2b. As the single figure can be further seen, the tapered roller rows 4, 5, 6, 7 arranged in an O-arrangement, which gives the bearing a large support width and makes this very rigid and receptive to large tilting moments. Further, the outer tapered roller rows 4 and 7 are axially supported between Stützborden 11 of the inner ring parts 2a, 2b and the inner tapered roller rows 5, 6 axially between Stützborden 12 of the two outer ring parts 3a, 3b.

Of course, it is also possible to provide support rims 11, 12 exclusively on the inner ring parts 2a, 2b or on the outer ring parts 3a, 3b, which is covered by the invention (not shown in detail). However, the guidance of the tapered rollers 8, at least the axially inner, lying in the radially outer ring rims 12 is favored, since this is a more favorable supply of lubricant is recorded.

It is also possible and is detected by the invention, to provide a one-piece outer ring 3 or assign each tapered roller row 4, 5, 6, 7 a separate outer ring part (not shown in detail).

In order to ensure the best possible or uniform loading of the tapered rollers 8, the roller axes 13 of the tapered rollers 8 of the respective adjacent outer and inner tapered roller rows 4, 5 and 7, 6 are arranged inclined so that the pressure angle oi, α ₂ character- nenden lines of action 14 of the adjacent tapered rollers 8 intersect in the region of the presently not shown in detail rotational axis of the tapered roller bearing 1.

As a result, it will be apparent to one skilled in the art, with the aid of the invention, that it is particularly advantageous for each inner ring part 2a, 2b to have a double support or a statically determined support.

In this connection, it should be noted that, for optimal performance of the structure of a bearing according to the invention, the intersection of the lines of action 14 of the tapered rollers 8 is preferably less than 10% of the bearing outer diameter away from the axis of rotation of the tapered roller bearing 1. Especially in the use of inventively designed tapered roller bearings for storage of planetary gears now disadvantageous deflection and inclination of the planetary pin is avoided compared to conventionally designed tapered roller bearings with the same load, but at least mitigated.

In addition, other possibilities have been found to be able to influence the bearing properties of the four-row tapered roller bearing 1 described above.

Thus, the distances of the support ribs 11, 12 and accordingly the axial length of the tapered rollers 8 depending on certain boundary conditions, such as a possible deformation of conversion parts, be designed or varied to a largely equal load of the respective tapered roller rows 4, 5, 6, 7, which has an advantageous effect on the bearing life. As a result, with respect to the two inner ring parts 2a, 2b, the distances of the support ribs 11, 12 and accordingly the axial lengths of the tapered rollers 8 can be chosen differently.

Likewise, the number of tapered rollers 8 of at least one, preferably two of the tapered roller rows 4, 5, 6, 7 deviate from the selected number of tapered rollers 8 of the remaining tapered roller rows, for example, to reduce an adverse co-rotation of a single common outer ring 3 in planetary gears ( not shown in detail).

Furthermore, it has proven to be expedient to act on the two axially inner tapered roller rows 5, 6 with a slight bias, whereby a homogeneous load distribution and a noise reduction in the lower or no-load area are recorded in particular when used in a planetary drive. In order to further reduce the number of components and the production cost and to increase the accuracy in the production of the tapered roller bearing, it may eventually be useful to form the one or more part outer ring 3 by, for example, a raceways for the tapered rollers 8 exhibiting planet or other wheel ( not shown in detail). The conventional separate outer ring 3 is thus unnecessary and is replaced, so to speak, by the planet or other wheel.

LIST OF REFERENCE NUMBERS

1 tapered roller bearing

2 inner ring

2a inner ring part

2b inner ring part

3 outer ring

3a outer ring part

3b outer ring part

4 tapered roller row

5 tapered roller row

6 tapered roller row

7 tapered roller row

8 tapered rollers

9 ring groove

10 lubrication groove

11 ring rims

12 ring rims

13 roller axle

14 effective lines αi pressure angle α ₂ pressure angle

Claims

claims

1. A four-row tapered roller bearing (1) for mechanical bearing bearings, with an axially formed two-part inner ring (2) and an axially one or more parts outer ring (3), wherein in each case an axially outer and an axially inner tapered roller row (4, 5, 7, 6 are supported by an inner ring part (2a, 2b), characterized in that the tapered roller rows (4, 5, 6, 7) arranged in an O-arrangement and the roller axes (13) of the respective adjacent outer and inner tapered rollers (8) both adjacent outer and inner taper roller rows (4, 5, 7, 6) are arranged inclined so that the pressure angle (αi, 02) characteristic lines of action (14) of the tapered rollers (8) in the region of the axis of rotation of the tapered roller bearing (1) cut, and each inner ring part (2 a, 2 b) results in a double support or a statically determined support.

2. Four-row tapered roller bearing (1) for mechanical bearing bearings, with an axially formed two-part inner ring (2) and an axially one or more parts outer ring (3), wherein in each case an axially outer and / or an axially inner tapered roller row (4, 5; 6) are supported by an inner ring part (2a, 2b), wherein the conical roller rows (4, 5, 6, 7) are arranged in an O arrangement and the roller axes (13) of the respective adjacent outer and inner tapered rollers (8) the two respectively adjacent outer and inner tapered roller rows (4, 5, 7, 6) are arranged inclined in such a way that the lines of action characterizing the contact angles (αi, α ₂ ) (14) of the tapered rollers (8) do not intersect in the region of the axis of rotation of the tapered roller bearing (1), and each inner ring part (2a, 2b) results in a double support or a statically determined support.

3. Four-row tapered roller bearing according to claim 1 or 2, characterized in that support rims (11, 12) for the axial support of the tapered rollers (8) on the inner and / or on the outer ring (2, 3) are arranged.

4. A four-row tapered roller bearing according to claim 3, characterized in that the distances of the support rims (11, 12) and accordingly the axial length of the tapered rollers (8) in dependence on certain boundary conditions, such as a possible deformation of the conversion parts, for equal loads on the tapered roller rows ( 4, 5, 6, 7) are designed.

5. Four-row tapered roller bearing according to claim 4, characterized in that with respect to the two inner ring parts (2a, 2b), the distances of the support rims (11, 12) and accordingly the axial lengths and diameters of the tapered rollers (8) are chosen differently.

6. A four-row tapered roller bearing according to one of claims 1 to 5, characterized in that the number of tapered rollers (8) at least one, preferably two of the tapered roller rows (4, 5, 6, 7) of the selected number of tapered rollers (8) the rest of the tapered roller rows deviates.

7. Four-row tapered roller bearing according to one of claims 1 to 6, characterized in that the two axially inner tapered roller rows (5, 6) are subjected to a bias or a relation to the other tapered roller rows (4, 7) other axial play.

8. Four-row tapered roller bearing according to one of claims 1 to 7, characterized in that the one or more part outer ring (3) by a Runways for the tapered rollers (8) exhibiting planetary or other wheel is formed.

9. Four-row tapered roller bearing according to one of claims 1 to 7, characterized in that the intersection of the lines of action (14) of the tapered rollers (8) less than 10% of the bearing outer diameter of the axis of rotation of the tapered roller bearing (1) is removed.