DE102017207505A1 - Radial bearing arrangement, in particular for a balance shaft - Google Patents

Abstract

The invention relates to a radial bearing assembly (1) having an outer part (3) and an inner part (4), wherein the parts are rotatable with respect to each other about a common longitudinal axis X1. The radial bearing assembly further comprises rolling elements (5), which are arranged radially between the outer part (3) and the inner part (4). A bearing seat (8) is formed on an outer surface of the inner member (4), wherein the rolling elements (5) roll with line contact on the bearing seat (8) having a width that varies over the bearing seat circumference, wherein a bearing seat portion (15a 19) of smaller width outside a load zone of the bearing seat in which a transverse load acts on the rolling elements (5), rather than being located in the load zone. The radial bearing arrangement is designed to prevent the passage of two rolling elements at two interrupting edges of the bearing seat at the same time.

Description

TECHNICAL FIELD OF THE INVENTION

The present invention relates to a radial bearing assembly for supporting an outer part with respect to an inner part, in particular for supporting a balance shaft in a housing which is intended to be used in a motor vehicle. The invention also relates to a balance shaft which is supported by such a radial bearing arrangement.

BACKGROUND OF THE INVENTION

A radial bearing arrangement for supporting an outer part with respect to an inner part is known from the prior art, for example from US Pat EP-A1-2014935 , This reference describes an arrangement in which the outer part and the inner part rotate with respect to each other about a common longitudinal axis. A bearing seat is formed on the outer portion or on the inner portion of the bearing assembly, the bearing seat having a load zone exposed to a radial load applied substantially stationary relative to the bearing seat. In particular, load zones of this type are created on bearing seats of balance shafts, more specifically on shafts having a center of gravity that is not rotationally symmetric relative to the longitudinal axis about which the shaft rotates in a housing.

It has been recognized that in conventional wheel bearings, the bearing seat is subjected to a significantly lower load or no mechanical load outside the load zone at all. It has therefore been proposed to provide a bearing seat having a width which varies over its circumference, the bearing seat being significantly tapered outside the load zone. A radial needle bearing of this kind is for example from the EP-A1-1775484 known. This design results in a great weight saving. In addition, the rolling elements cantilever locally and temporarily over the width of the bearing seat, so that lubricant can be fed directly to the rolling elements to improve the Wälzkörperschmierung.

The variable width of the bearing seat implies a recessed portion on the sides of the rolling surfaces for the rolling elements, and thus broken edges. A disadvantage of this arrangement is that the rolling elements, here needles, circumferentially roll on the interrupt edges of the bearing seat and induce a vibration during use of the assembly.

SUMMARY OF THE INVENTION

The object of the present invention is to solve the above-mentioned problems. It is proposed a radial bearing assembly, which is particularly suitable for supporting a balance shaft in a housing, which is reduced in weight, and which allows a reduced vibration for the arrangement in use.

To this end, the invention relates to a radial bearing assembly having an outer part and an inner part, wherein the parts are rotatable with respect to each other about a common longitudinal axis, and rolling elements, which are arranged radially between the outer part and the inner part. The rolling elements are arranged circumferentially in pockets of a cage, each pocket being a length L2 has and from the adjacent bag by a length L3 is separated, which is defined in a projection to the radial plane of the pitch circle diameter of the radial bearing assembly. The radial bearing assembly is further provided with a bearing seat provided on an outer surface of the inner member, wherein the rolling elements roll with line contact on the bearing seat having a width that varies over the bearing seat periphery, with a smaller-width bearing seat portion outside a load zone the bearing seat, in which a transverse load is exerted on the rolling elements, instead of within the load zone, wherein the inner part is provided with at least one recess on the sides of the bearing seat portion with a smaller width, wherein the recess has a length L3 has, which is defined in the projection of the radial bearing assembly on the radial plane.

More specifically, the widths are defined with respect to the longitudinal axis while the lengths are circumferentially defined, with the lengths L1 . L2 and L3 Projections on a radial plane according to the pitch circle diameter of the radial bearing assembly are.

wobei N eine gegebene Anzahl von Wälzkörpern ist, die zu einer gegebenen Zeit oberhalb der Aussparung angeordnet sind.According to the invention, the radial bearing assembly is formed according to the following formula: $$\left[\left(\text{N}+\raisebox{1ex}{$1$}\!\left/ \!\raisebox{-1ex}{$2$}\right.\right)\times \text{L2}\right]+\left[\text{N}\times \text{L3}\right]<\text{D}<\left[\left(\text{N}+\raisebox{1ex}{$1$}\!\left/ \!\raisebox{-1ex}{$2$}\right.\right)\times \text{L2}\right]+\left[\left(\text{N}+1\right)\times \text{L3}\right]$$

where N is a given number of rolling elements located above the recess at a given time.

The value of N depends on several parameters, such as the total number of rollers, the length of the rollers, the bearing seat diameter, the lengths L2 and L3 , The value of N may be fixed depending on the application.

The bearing seat outside the bearing zone lies axially adjacent a recess, and two interrupt edges are defined circumferentially between the recess and the bearing seat portion of greater width at the load zone.

When a rolling element rolls circumferentially on the rolling surface of the bearing seat, it rolls from a portion of the bearing seat on the load zone to a portion of the bearing seat of reduced width outside the load zone. The rolling elements then roll through an interruption edge. Thanks to the invention, at the same time a portion of the cage, which radially separates two pockets, faces the other interrupting edge. Then the passage of two rolling elements is prevented at two interrupting edges of the bearing seat at the same time.

The vibration of the radial bearing assembly of the present invention is then reduced in use as compared to an arrangement in which two rolling elements roll at the same time through two discontinuous edges.

Another advantage is that the inner part that supports the bearing seat width varies over its circumference with the bearing seat sides recessed so as to reduce the weight of the part.

The rolling elements are efficiently supported by the bearing seat, even at sections of reduced axial length.

The rolling elements are supported by the bearing seat over the entire circumference of the radial bearing arrangement, so that the rolling elements are prevented from falling out or from shifting during a stopping or releasing process.

Another advantage of the present invention is improved lubrication of the rolling elements by means of the recess of the inner part. The contact line between the rolling elements and the bearing is efficiently and easily supplied with lubricant. This reduces the wear of the parts of the radial bearing assembly and allows for a longer life.

• - Die Wälzkörper sind Nadelrollen.
• - Die Wälzkörper sind umfänglich von einem Käfig gehalten.
• - Der Breitenübergang zwischen den Lagersitzabschnitten unterschiedlicher Breite ist graduell. Alternativ ist der Breitenübergang stufenweise.
• - Zumindest einer der Lagersitzabschnitte erstreckt sich quer und senkrecht zu der Längsachse.
• - Zumindest einer der Lagersitzabschnitte erstreckt sich quer und winkelig, wobei er einen Winkel mit einer Ebene senkrecht zu der Längsachse bildet.
• - Der Lagersitzabschnitt ist gerade, gewellt oder gekrümmt.
• - Der Lagersitz ist mit zumindest zwei Lagersitzabschnitten ausgestattet, die sich quer erstrecken, und die längs voneinander durch eine durchgängige Aussparung voneinander getrennt sind, wobei die Wälzkörper in Linienkontakt mit jedem der Lagersitzabschnitte sind.
• - Der innere Teil ist hohl, um so eine Mittelöffnung zu definieren, die nur von dem Lagersitz umgeben ist, wobei die Aussparung durch die Dicke des inneren Teils bereitgestellt ist.
• - Der innere Teil ist ein Abschnitt einer rotierenden Welle, wobei der Lagersitz an einer äußeren Fläche der Welle ausgebildet ist.
• - Die Wälzanordnung ist vorzugsweise gemäß folgender Formel ausgebildet: $$\text{D}=\left(\text{N}+\raisebox{1ex}{$1$}\!\left/ \!\raisebox{-1ex}{$2$}\right.\right)\times \left(\text{L2}+\text{L3}\right)\text{.}$$
  

According to further aspects of the invention, which are advantageous but not necessarily, such a radial bearing arrangement may have one or more of the following characteristics:

• - The rolling elements are needle rollers.
• - The rolling elements are circumferentially held by a cage.
• The width transition between the bearing seat portions of different widths is gradual. Alternatively, the width transition is gradual.
• - At least one of the bearing seat portions extends transversely and perpendicular to the longitudinal axis.
• - At least one of the bearing seat portions extends transversely and angularly, wherein it forms an angle with a plane perpendicular to the longitudinal axis.
• - The bearing seat portion is straight, wavy or curved.
• - The bearing seat is provided with at least two bearing seat portions which extend transversely, and which are separated from each other by a continuous recess from each other, wherein the rolling elements are in line contact with each of the bearing seat portions.
• The inner part is hollow so as to define a central opening which is surrounded only by the bearing seat, the recess being provided by the thickness of the inner part.
• - The inner part is a portion of a rotating shaft, wherein the bearing seat is formed on an outer surface of the shaft.
• The rolling arrangement is preferably designed according to the following formula: $$\text{D}=\left(\text{N}+\raisebox{1ex}{$1$}\!\left/ \!\raisebox{-1ex}{$2$}\right.\right)\times \left(\text{L2}+\text{L3}\right)\text{,}$$
  

list of figures

• - 1 ist eine schematische Seitenansicht eines Teils einer Radiallageranordnung gemäß einem ersten beispielhaften Ausführungsbeispiel der Erfindung,
• - 2 und 3 sind schematische perspektivische Ansichten von inneren Teilen der Radiallageranordnung gemäß zwei alternativen Ausführungsformen,
• - 4 ist eine schematische Draufsicht auf einen inneren Teil einer Radiallageranordnung an einer Radialebene gemäß einem Teilkreisdurchmesser der Radiallageranordnung; und
• - 5 und 6 sind schematische Draufsichten auf innere Teile einer Radiallageranordnung gemäß alternativen Ausführungsbeispiel der Erfindung.

The invention will now be explained in conjunction with the appended figures as illustrative examples, without limiting the subject matter of the invention. In the attached figures:

• - 1 is a schematic side view of a portion of a radial bearing assembly according to a first exemplary embodiment of the invention,
• - 2 and 3 13 are schematic perspective views of inner parts of the radial bearing assembly according to two alternative embodiments,
• - 4 is a schematic plan view of an inner part of a radial bearing assembly at a radial plane according to a pitch circle diameter of the radial bearing assembly; and
• - 5 and 6 FIG. 13 are schematic plan views of inner parts of a radial bearing assembly according to an alternative embodiment of the invention. FIG.

DETAILED DESCRIPTION OF SOME EMBODIMENTS

A radial bearing arrangement 1 is schematic in 1 illustrated, in particular for use with a balance shaft in a piston engine of a motor vehicle, wherein the shaft is an eccentrically weighted shaft which shifts vibrations in the engine.

The order 1 has an outer part 3 , here an outer ring, an inner part 4 , and several rolling elements 5 on, which are arranged between the inner and the outer part. The outer part 3 and the inner part 4 are about a common longitudinal axis X1 centered and are in relative rotation about this axis. In the embodiment of the balance shaft application, the outer part is 3 stationary and the inner part 4 rotates with the shaft about its longitudinal axis X1 ,

In the following, the specific identifications of the arrangement 1 for this figure and the following, the adjectives "longitudinal" and "transverse" and the adverbs "longitudinal" and "transverse" relative to the axis X1 Are defined. Thus, a longitudinal portion or longitudinal part is parallel to the axis X1 while a transverse section or cross member is perpendicular to this axis X1 is.

The outer part 3 has an inner bore 6 on which is a rolling surface for the rolling elements 5 along a contact line 7 forms. The inner part 4 has a bearing seat 8th on, a rolling surface for the rolling elements 5 along a contact line 9 forms. Here you can see the rolling elements 5 have a cylindrical shape, such as the needle rollers, as in 1 shown. Alternatively, it is also possible to use frustoconical or toroidal rolling elements. Alternatively, the Wälzlagerausgestaltung may also have a double row bearing, such as a double row needle roller bearing. However, only ball bearings, that is bearings with punctiform contact with the rolling surfaces, are not to be regarded as radial contact arrangements with line contact and are not covered by the present invention.

The rolling elements 5 move along the inner part 4 in the transverse direction Y1 ,

The rolling elements are circumferentially equidistant from each other and from a cage 10 added. More precisely, the rolling elements 5 in bags 10a around the cage 10 are provided, arranged.

The bags 10a extend axially along a given width, preferably of reduced width compared to that of a loaded bearing seat portion 11 , As in further 4 shown, the pockets extend 10aA circumferentially along a length L2 at a radial plane of the pitch circle diameter of the radial bearing arrangement 1 is defined.

The bags 10a are circumferentially on the cage 10 equidistant from each other by spacer portions 10b wherein two adjacent cages are defined by a length L3 are separated from each other, at the radial plane of the pitch circle diameter of the radial bearing assembly 1 is defined.

With further reference to 1 includes the bearing seat 8th of the inner part 4 a loaded bearing seat section 11 with an axial width substantially equal to that of the inner part 4 , The section 11 supports the rolling elements 5 along a major part of the rolling element width. The section 11 is advantageously provided in a load zone in which a transverse load on the rolling elements 5 is exercised. The load is exerted in the load zone and can efficiently from the outer part 4 the wave 2 on the rolling elements 5 along a contact line 9 be transmitted with maximum width.

According to the first embodiment of Figure 1 has the bearing seat 8th of the inner part 4 furthermore two bearing seat sections 15a and 15b on, extending across the load section 11 extend in a circumferential direction. A first section 15a extends from a first axial side of the load section 11 , and a second section 15b extends from a second axial side of the load section 11 and axially opposite to the first side.

The width of the sections 15a . 15b each is smaller than the width of the load section 11 , The sum of the widths of the sections 15a . 15b is smaller than the width of the load section 11 of the bearing seat 8th ,

The sections 15a . 15b extend transversely and vertically with respect to the longitudinal axis X1 , ie parallel to the rolling direction of movement Y1 the rolling elements. The sections 15a . 15b are parallel to each other and are longitudinally through a recess 16 separated from each other. The rolling elements 5 are in line contact with each of the sections 15a . 15b ,

The sections 15a . 15b are advantageously on the bearing seat 8th outside a load zone in which a shear load on the rolling elements 5 is exercised. There is neither a load on the rolling elements 5 exercised still transferred, making it the sole purpose of the rolling surfaces 15a . 15b is, the displacement of the rolling elements 5 to support. The rolling elements 5 are not from the bearing seat 8th over the recess 16 supported. The widths of the rolling surfaces 15a . 15b are very reduced compared to the longitudinal section. The recess 16 in between allows the use of less material and thus greatly reduces the weight of the inner part.

The recess 16 defines two side edges 16a . 16b which extend parallel to each other in the circumferential direction, and two axial edges 16c . 16d which extend substantially in the axial direction. The axial edges 16c . 16d have curved shapes to a gradual width transition between the load section 11 and the sections 15a . 15b sure. The bearing seat width decreases circumferentially gradually from the load portion 11 to the first section 15a on a first axial side, and gradually decreases circumferentially from the load portion 11 to the second section 15b on a second axial side.

The recess 16 is defined between two circumferential ends, which are defined by the edges 16c and 16d are defined. The edges 16c . 16d are interruption edges between the recess 16 and the loaded bearing section 11 on both sides of the circumference. As in 4 illustrated, has the recess 16 a total length L3 between the ends of the interruption edges 16c . 16d with a loaded bearing section 11 , L3 is at a radial plane of the pitch circle diameter of the radial bearing assembly 1 defined, as well as L1 and L2 ,

The two bearing seat sections 15a . 15b define two contact lines with a rolling element 5 along the longitudinal direction. This allows the stability of the radial bearing assembly 1 to improve. In the embodiment of 1 the sections extend 15a . 15b transversely at both longitudinal end sides of the inner part, so as to improve the stability of the rolling elements.

The bearing seat 8th supports the rolling elements 5 over the entire circumference of the radial bearing assembly, in the load zone through the longitudinal section 11 and in the no-load zone through the sections 15a . 15b , Thereby, a sliding or sliding of the rolling elements can be reliably prevented.

The sections 15a . 15b can be straight, corrugated or curved as shown.

According to a first alternative training, as in 2 represented, is the inner part 4 empty, with the recess 16 has a given radial depth in the material of the inner part.

Such a recess makes it possible to reduce the weight of the inner part, and also forms a lubricant reservoir for the rolling elements.

Advantageously, the inner part is formed on an outer surface of the rotating shaft, for example a balance shaft.

According to a second alternative embodiment, as in 3 represented, is the inner part 4 hollow, around a center hole 14 to define, with the bore 14 only from the bearing seat 8th is surrounded.

The bearing seat 8th forms a wall, which means the center hole 14 surrounds. More specifically, the loaded bearing seat portion defines 11 and the sections 15a . 15b the center hole 14 ,

In addition, a continuous recess 17 between the two sections 15a . 15b defined directly with the center hole 14 communicate via a continuous window.

Preferably, the inner part 4 produced by, for example, laser cutting or water jet cutting.

The inner part 4 who is the camp seat 8th is hollow, to greatly reduce the weight of the part.

Another advantage is that lubricant can be fed through the recess to the rolling elements.

Preferably, the bearing seat 8th only be connected to a massive shaft on both sides of the load zone.

wobei N eine gegebene Anzahl der Wälzkörper 5 ist, die über der Aussparung 16, 17 zu einer gegebenen Zeit angeordnet sind.According to the invention, the radial bearing arrangement 1 designed such that the passage of two rolling elements 5 at two interruption edges 16c . 16d the bearing seat is prevented at the same time. The recess 16 . 17 by the length L3 is defined, and the cage 10 that by the length L2 the bags 10a and the length L3 defined between two adjacent pockets follow the following formula: $$\left[\left(\text{N}+\raisebox{1ex}{$1$}\!\left/ \!\raisebox{-1ex}{$2$}\right.\right)\times \text{L2}\right]+\left[\text{N}\times \text{L3}\right]<\text{D}<\left[\left(\text{N}+\raisebox{1ex}{$1$}\!\left/ \!\raisebox{-1ex}{$2$}\right.\right)\times \text{L2}\right]+\left[\left(\text{N}+1\right)\times \text{L3}\right]$$

where N is a given number of rolling elements 5 is that over the recess 16 . 17 are arranged at a given time.

The term [(N + ½) × L2 ] corresponds to the total length of the pockets 10a that with rolling elements 5 equipped at the same time in rolling contact with the bearing seat 8th and over the recesses 16 . 17 are. The terms [N × L3 ] and [(N + 1) × L3 ] are the corresponding total length of the spacer sections 10b between two adjacent pockets 10a ,

According to this formula, the total length is L3 the recess 16 . 17 the sum of the total lengths of the pockets 10a and the spacer sections 10b of the cage 10 over the recess 16 . 17 , of a single length L3 of the spacer section.

At the same time, a given number N of rolling elements 5 over the recess 16 . 17 arranged, wherein the rolling elements 5 in bags 10a the cage are arranged, the circumference of the bearing seat 8th radially surrounded by the inner part.

If a single rolling element 5 at the bearing seat 8th unwinds and from the loaded bearing seat section 11 to the storage sections 15a . 15b rolls with reduced width outside the loaded zone, the rolling element happens 5 a first interruption edge 16c passing through the recess 16 (or 17) and the loaded bearing seat section 11 is defined.

In a radial bearing arrangement 1 , which is designed according to the present formula, rolls at the same time no rolling elements 5 over the second interruption edge 16c , On the contrary, if a rolling element 5 at a first interruption edge 16c is is a spacing section 10b of the cage 10 radially of the second interrupting edge 16d opposite, as in 4 is illustrated.

Advantageously, the radial bearing arrangement 1 configured according to the following formula: $$\text{D}=\left(\text{N}+\raisebox{1ex}{$1$}\!\left/ \!\raisebox{-1ex}{$2$}\right.\right)\times \left(\text{L2}+\text{L3}\right)\text{,}$$

Alternative embodiments of the invention are in the 5 and 6 in which the same elements have the same references, and differ from the previous embodiment in the shape of the recess.

In 5 has the bearing seat 8th of the inner part 4 two bearing seat sections 15a and 15b on, extending across the loaded bearing seat section 11 extend in the circumferential direction. A first section 15a extends from a first axial side of the load section 11 , and a second section 15b extends from a second axial side of the load section 11 and axially opposite to the first side.

The bearing seat sections 15a . 15b extend transversely and vertically with respect to the longitudinal axis X1 , ie parallel to the direction of movement of the rolling elements Y1 , The sections 15a . 15b are parallel to each other and are longitudinally separated from each other by a recess 18 separated.

The recess 18 defines two side edges 18a . 18b which extend parallel to each other in the circumferential direction, and two axial edges 18c . 18d which extend parallel to each other in the axial direction. The width transition between the load section 11 and the sections 15a . 15b is gradual.

In 6 For example, the reduced width bearing seat portion has a Z-shaped configuration with a single portion 19 with reduced width, which is circumferentially angled between the edges of the load section 11 extends. Two recesses 20a . 20b are on both axial sides of the section 19 Are defined.

This configuration also helps to provide a particularly good supply of lubricant to the rolling elements.

According to another alternative, which is not shown, a portion of the bearing seat 8th have a double inclination in the form of a toothing, in order to achieve that the rolling surfaces assume an M-shaped configuration.

Representative, non-limiting examples of the invention have been described above in detail with reference to the attached drawings. This detailed description is merely intended to teach one skilled in the art further details in order to practice preferred aspects of the present teachings and is not intended to limit the scope of the invention. Moreover, each of the additional features and teachings disclosed above may be used separately or in conjunction with other features and teachings to provide improved radial bearing arrangements.

In addition, various features of the representative examples described above, as well as the various independent and dependent claims below, may be combined in ways that are not specifically and explicitly listed to provide additional useful embodiments of the present teachings.

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 2014935 A1 [0002]
• EP 1775484 A1 [0003]

Claims (10)

Radial bearing assembly (1) comprising: - an outer part (3) and an inner part (4), wherein the parts are rotatable with respect to each other about a common longitudinal axis X1, - rolling elements (5) radially between the outer part (3) and the inner part (4), - a cage (10) which is circumferentially provided with pockets (10a) in which the rolling elements (5) are arranged, each pocket (10a) having a length (L2) and from the adjacent pocket is separated by a length (L3) defined in a projection on the radial plane of the pitch circle diameter of the radial bearing assembly (1), a bearing seat (8) formed on an outer surface of the inner member (4) wherein the rolling elements (5) roll with line contact on the bearing seat (8) having a width that varies over the bearing seat circumference, wherein a smaller diameter bearing seat portion (15a, 15b; 19) outside a load zone of the bearing seat in which transversal load on d The rolling element (5) is exerted, instead of within the load zone, is provided, wherein an inner part (4) with at least one recess (16; 17; 18; 20a, 20b) is provided on the sides of the bearing seat portions (15a, 15b, 19) of smaller width, the recess (16; 17; 18; 20a, 20b) having a length (L3) which in the projection of the radial bearing assembly (1 ) is defined on the radial plane, characterized in that the radial bearing arrangement (1) is designed according to the following formula: $$\left[\left(\text{N}+\raisebox{1ex}{$1$}\!\left/ \!\raisebox{-1ex}{$2$}\right.\right)\times \text{L2}\right]+\left[\text{N}\times \text{L3}\right]<\text{D}<\left[\left(\text{N}+\raisebox{1ex}{$1$}\!\left/ \!\raisebox{-1ex}{$2$}\right.\right)\times \text{L2}\right]+\left[\left(\text{N}+1\right)\times \text{L3}\right]$$

where N is a given number of rolling elements (5) arranged above the recess (16; 17; 18; 20a, 20b) at a given time. Radial bearing arrangement according to Claim 1 wherein the radial bearing assembly (1) is configured according to the following formula: $$\text{D}=\left(\text{N}+\raisebox{1ex}{$1$}\!\left/ \!\raisebox{-1ex}{$2$}\right.\right)\times \left(\text{L2}+\text{L3}\right)\text{,}$$

A radial bearing assembly as claimed in any one of the preceding claims, wherein the inner member (4) is hollow so as to define a central aperture (14) surrounded only by the bearing seat (8). Radial bearing arrangement (1) according to one of the preceding claims, wherein the rolling elements (5) are needle rollers. A radial bearing assembly (1) according to any one of the preceding claims, wherein the width transition between the bearing seat portions (11; 15a, 15b; 19) having different widths is gradual. Radial bearing assembly (1) according to one of Claims 1 to 4 wherein the width transition between the bearing seat portions (11; 15a, 15b; 19) is stepwise with different widths. Radial bearing assembly (1) according to any one of the preceding claims, wherein at least one of the bearing seat portions (15a, 15b) extends transversely and perpendicularly with respect to the longitudinal axis (X1). A radial bearing assembly (1) according to any one of the preceding claims, wherein at least one of the bearing seat portions (19) extends transversely and angularly forming an angle with a plane perpendicular to the longitudinal axis (X1). A radial bearing assembly (1) according to any one of the preceding claims, wherein the bearing seat (8) is provided with at least two bearing seat portions (15a, 15b) extending transversely and separated longitudinally from one another by a recess (16; 17; 18). wherein the rolling elements (5) are in line contact with each of the bearing seat portions (15a, 15b). A radial bearing assembly (1) according to any one of the preceding claims, wherein the inner part (4) is a portion of a rotary shaft, wherein a bearing seat (8) is formed on an outer surface of the shaft.

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