DE102021108401A1 - tapered roller bearing - Google Patents

Abstract

Tapered roller bearing comprising an inner ring and an outer ring arranged coaxially above it, between which rolling elements designed as tapered rollers and inserted in cage pockets of a rolling element cage are arranged, so that the inner ring can be rotated about an axis of rotation relative to the outer ring, the cage pockets being supported by end cage edges and longitudinal webs running between the cage edges of the rolling element cage, with the inner ring having a radially outwardly directed support rim on its axial end section with a larger diameter, and a conical inner ring raceway for the rolling elements being formed axially next to the support rim on an outer lateral surface of the inner ring, with the inner ring having at its axial end section with smaller diameter has a radially outwardly directed safety rim, which is spaced axially by an inner ring section of the inner ring raceway, wherein the rolling element cage has locking arms in the axial direction ung intervene between the rolling elements and the safety rim, so that the rolling element cage is secured in the axial direction, the longitudinal webs of the rolling element cage each having a chamfer on the inner sides facing one another, which extends from the larger-diameter cage rim and increases continuously.

Description

The application relates to a tapered roller bearing comprising an inner ring and an outer ring arranged coaxially above it, between which rolling elements designed as tapered rollers and inserted in cage pockets of a rolling element cage are arranged, so that the inner ring can be rotated about an axis of rotation relative to the outer ring, the cage pockets being supported by end cage edges and between longitudinal webs of the rolling element cage running along the cage ribs, the inner ring having a radially outwardly directed support rib on its axial end section with a larger diameter, and a conical inner ring raceway for the rolling elements being formed axially next to the support rib on an outer lateral surface of the inner ring, with the inner ring on its axial end section with a smaller diameter has a radially outwardly directed securing flange which is spaced axially from the inner ring raceway by an inner ring section, the rolling element cage having latching arms au fwise, which engage in the axial direction between the rolling elements and the safety rib, so that the rolling element cage is secured in the axial direction.

From the DE 35 24 063 A1 a tapered roller bearing is known, the inner ring of which has a radially outwardly extending rim in the area of its large outer diameter and a somewhat smaller radial rim in the area of its small outer diameter. A groove is formed in the inner ring axially between the small retaining flange and the raceway of the inner ring, in which groove a radially inward-pointing elastic projection of a cage of the tapered roller bearing engages with play.

the DE 10 2014 205 051 A1 as well as the DE 10 2006 057 512 A1 show roller bearing cages in which roller bodies designed as tapered rollers are guided. For tapered roller bearings, rolling element cages designed as window cages are preferably used, in which the tapered rollers are inserted and guided. The window cage, also known as the TVP cage, includes two cage edges that are arranged axially to one another and are connected by spaced webs. The cage edges together with the webs form rolling element pockets in which the rolling elements are accommodated. Such constructed rolling element cages for tapered roller bearings are, for example, from DE 27 39 367 A1 and the DE 10 2016 210 331 A1 known. A roller bearing cage is preferably guided on the inner bearing ring or the outer bearing ring of the roller bearing.

The object of the present application is to provide an improved tapered roller bearing and a corresponding roller bearing unit that allow simpler assembly.

The object is solved by the features of the independent claims. Further preferred embodiments of the invention can be found in the dependent claims, the figures and the associated description.

Correspondingly, a tapered roller bearing is proposed comprising an inner ring and an outer ring arranged coaxially above it, between which rolling elements designed as tapered rollers and inserted in cage pockets of a rolling element cage are arranged, so that the inner ring can be rotated about an axis of rotation relative to the outer ring, the cage pockets being supported by end cage edges and between longitudinal webs of the rolling element cage running along the cage ribs, the inner ring having a radially outwardly directed support rib on its axial end section with a larger diameter, and a conical inner ring raceway for the rolling elements being formed axially next to the support rib on an outer lateral surface of the inner ring, with the inner ring on its axial end section with a smaller diameter has a radially outwardly directed safety flange, which is spaced axially from the inner ring raceway by an inner ring section, the rolling element cage Ra which engage in the axial direction between the rolling elements and the securing rim, so that the rolling element cage is secured in the axial direction, with the longitudinal webs of the rolling element cage each having a chamfer on the inner sides facing one another, which extends from the larger-diameter cage rim and thereby increases continuously . The bevel preferably extends over the entire length of the longitudinal webs.

If, in the context of this application, the directional information is used axially or radially, then these relate to the axis of rotation of the tapered roller bearing. The indication of the direction axial thus means an orientation parallel to the axis of rotation; the indication of direction radial means an orientation orthogonal to the axis of rotation.

The smaller-diameter axial end portion of the tapered roller bearing is separated from the larger-diameter axial end portion by the inner ring raceway.

The chamfer on the longitudinal webs, also referred to as a bevel, recess or pocket, advantageously allows a limited, also known as pivoting, tilting of the tapered roller radially outwards during assembly, the joining of the inner bearing ring and the roller and cage assembly comprising the tapered rollers and the roller bearing cage. The tilting of the rolling element is carried out starting from the support board, which is due to the larger end of the tapered roller rim.

So that the chamfers on the longitudinal webs allow the rolling elements to tilt, the chamfers are arranged on the insides of the longitudinal webs, ie on sides of the longitudinal webs that point radially inwards. Or to put it another way: The proposed chamfers are created by appropriate processing of the radially inner edges of the longitudinal webs.

Due to the possibility of tilting created in this way, the tapered rollers can be arranged with a small radial play in the rolling element cage and the rolling element cage can still be filled from the inside, ie from the direction of the end section with the smaller diameter.

The chamfers increase an inner enveloping circle diameter of the tapered rollers, which avoids an excessive dimensional overlap compared to a safety rib diameter of the inner bearing ring. This creates the possibility of filling the roller bearing cage with tapered rollers from the inside with an unchanged radial clearance that is optimal for the bearing function and is designed for a maximum of 1 mm. At the same time, damage to the tapered rollers and the inner ring can be effectively prevented by tilting the tapered rollers.

The chamfers in the webs of the rolling element cage, which can be produced easily and inexpensively and which increase continuously starting from the cage rim with the larger diameter, preferably up to the cage rim with the smaller diameter, create an insertion or assembly aid. Automated and consequently quick, cost-effective assembly of the tapered roller bearing is thus made possible, with the roller body cage being able to be filled from the inside with one stroke.

The spring effect of the preferably elastic latching arms of the rolling body cage results in an exact axial contact of the rolling bodies on the support rim of the inner ring, which means, among other things, that mounting in a device is independent of the bearing. In addition, it is not necessary to form a holding rim on the axial end section of the inner ring with the smaller diameter, which, among other things, simplifies the grinding of the inner ring raceway. Only the safety edge has to be provided, on which the latching arms can be supported axially.

The latching arms preferably engage in the region of the inner ring section between the rolling elements and the safety rim; more preferably, the latching arms not only contact the safety rim, but also the radially outwardly directed surface of the inner ring section.

It is further proposed that the mutually facing bevels of the rolling body cage together form a conical receptacle for the rolling body. The conical design allows ideal storage of the rolling element, which is designed as a tapered roller.

It is also advantageous if the concave bevels of the longitudinal webs are adapted to an outer contour of the rolling elements. Thus, not only can the rolling bodies be tilted during assembly, but the chamfers also form an advantageous bearing surface during the rolling movement of the tapered rollers during operation. This ensures efficient and low-wear operation of the cone bearing.

It is advantageous if the chamfers are designed in such a way that the rolling elements can be pivoted between ≧1° and ≦4° around the larger-diameter cage rim during assembly. With this design, an inner enveloping circle diameter defined for the tapered rollers can be implemented that deviates ≤ 1 mm from the safety rib diameter of the inner ring. The radial play between the tapered rollers within the roller bearing cage can be minimized in this way.

It is also advantageous if, in the installed state, an inner enveloping circle diameter defined by the rolling elements is smaller than a maximum outer diameter of the safety rim. The inner envelope diameter is preferably 0.8 mm to 1 mm smaller than the maximum outer diameter of the safety rim. By this measure, the radial play between the rolling element and the roller bearing cage can be further reduced. Furthermore, the rolling elements are also reliably secured in this way.

The inner ring section preferably has an annular groove. This annular groove is easy to manufacture and provides a predefined engagement for the latching arms. The annular groove can also merge directly into the safety flange on one side. The annular groove can, for example, also be designed in such a way that the latching arms are only secured on one side in the axial direction.

The annular groove preferably has a polygonal cross-sectional geometry, at least in sections, into which a respective free end of the latching arms engages. As a result, the inner ring can transmit at least slight axial forces acting in the direction of the support rim of the inner ring by means of the latching and contact arms of the rolling element cage via the rolling elements to the outer ring. For example, with a rectangular annular groove free ends of the latching arms, for example, have a corresponding, likewise rectangular cross-sectional geometry. As an alternative to this, the free ends of the latching arms can also have a wedge-shaped or triangular cross-sectional geometry for minimizing friction by reducing the effective contact area. If necessary, a circumferential groove can be formed between the ring groove and the inner ring raceway for the local reduction of notch stresses. As an alternative to this, an axially widened annular groove with a groove formed on one side, for example, can also take over its function.

It is advantageous if the rolling element cage has a multiplicity of radially outwardly directed contact arms, which are designed for axial fixation on the axial end of the outer ring that has the smaller inside diameter. The contact arms can be designed, for example, in the form of retaining claws. The contact arms and the latching arms interact in such a way that any radial play that may be present is minimized and at the same time a holding force of the outer ring in relation to the rolling element cage with the rolling elements used and the inner ring can be increased. Preferably, the contact arms have a contact surface facing the outer ring, which is aligned parallel to the opposite end contact surface of the outer ring. A predefined axial spacing of the outer ring relative to the contact arms can thus be achieved, which is preferably between 0.1 mm and 0.2 mm. In this way, a low-friction bearing of the outer ring can be guaranteed in normal operation. At the same time, when certain forces are applied, the contact arms can come to rest on the end face of the outer ring, so that the outer ring is secured by the contact arms in the direction of the axis of rotation.

The latching arms and the contact arms preferably enclose an angle between them. This ensures an excellent holding effect of the locking and contact arms. The angle is preferably between 80° and 120°, more preferably about 100°. The angle is preferably the opening angle enclosed by mutually adjacent contact arms and latching arms on an end face of the rolling body cage with a smaller diameter, the angle being measured, for example, in a plane parallel to the axis of rotation.

Provision is preferably made for a smaller-diameter groove and a larger-diameter groove to be formed coaxially with one another in an outside of a smaller-diameter side part of the rolling element cage that is directed axially away from the support rim of the inner ring. As a result, the spring effect of the locking arms and the contact arms of the window cage is advantageously increased.

It is further proposed that the locking arms are arranged on the smaller-diameter side part of the rolling element cage in the circumferential direction of the same, in the area of the longitudinal webs, and the contact arms are each arranged in the area next to the longitudinal webs. The contact arms are therefore arranged in the area of the cage pockets. Due to the constructive assignment of the locking arms to the longitudinal webs, the locking arms can absorb relatively high forces. The assignment of the contact arms to the cage pockets results in a relatively high flexibility of the contact arms. Accordingly, the proposed arrangement of the contact arms and locking arms in the circumferential direction creates a needs-based design of the rolling element cage.

It is also advantageous if a contact surface is formed on the free end of the contact arms, each of which is spaced axially from a front outer surface of the outer ring, this outer surface of the outer ring being axially oriented away from the larger-diameter supporting rim of the inner ring. The contact surfaces of the contact arms are preferably spaced 0.1 mm to 0.2 mm from the front-side outer surface of the outer ring in the direction of the axis of rotation. As a result, any friction that may occur between the window cage and the outer ring can be reduced, in particular when the contact surface is comparatively small.

The object mentioned at the outset is also achieved by a roller bearing unit, the roller bearing unit constructed as an insert bearing comprising two tapered roller bearings according to one of claims 1 to 8, the two inner rings being connected to one another via a retaining ring, a seal having a joint between the two inner rings seals.

The insert bearing in conjunction with a rolling element cage, also known as a TVP window cage, is particularly suitable for truck wheel bearings. For applications in driven truck axles with sealed and grease-lubricated roller bearing units, two tapered roller bearings used in the wheel hub are usually arranged in mirror image, with the inner rings supported against each other, fixed with a circlip and sealed with a center seal. The insert bearing advantageously forms an interchangeable unit that can be assembled and disassembled in repair shops using simple auxiliary tools. The enveloping circle diameter of the tapered rollers, which is increasing due to the proposed measure, enables the assembly of the tapered roller roller and rolling element cage via larger safety flange diameters of the inner ring. For reasons of strength, the inner rings of insert bearings require larger cross-sections, as they are used with a clamping force of ≥ 30 KN.

The roller bearing cage is preferably made from a durable, flexible plastic. Such plastics have the advantage that the rolling bodies or tapered rollers can be inserted into the cage pockets with little effort. This avoids impermissible mechanical loads or damage to the tapered rollers and/or the roller bearing cage. A suitable plastic is, for example, a polyamide or a mixture of polyamide and an additive, with an elastomer being able to be provided as an additive. As an alternative to plastic, a roller bearing cage made from a metal material, for example sheet steel or sheet brass, or a compression-molded sintered metal, can be used.

Finally, a method for assembling tapered roller bearings of a rolling bearing unit is proposed, in which the following sequential steps are provided. First, the cage pockets of the roller bearing cage, which is preferably made of a plastic, are filled with rolling elements designed as tapered rollers. The inner bearing ring of the tapered roller bearing is then inserted into the roller bearing cage filled with the roller bodies. The tapered rollers can be pivoted to a limited extent in the cage pockets of the roller bearing cage in order to overcome the safety edge of the inner ring, on which the elastic locking arms lock after assembly is complete.

The safety flanges of the two tapered roller bearings are preferably set up to create an axial contact for the seal arranged between the safety flanges. In this way, the seal can be reliably clamped between the safety edges.

• 1 eine schematische Schnittansicht einer Wälzlagereinheit mit zwei spiegelbildlich angeordneten, weitestgehend indentischen Kegelrollenlagern;
• 2 eine perspektivische Ansicht eines Wälzkörperkäfigs;
• 3 einen Ausschnitt einer schematischen Schnittansicht eines Kegelrollenlagers in einer Montageposition;
• 4 eine schematisch dargestellte Vorderansicht einer Kegelrollenanordnung zur Verdeutlichung eines Hüllkreises;
• 5 einen Ausschnitt eines Wälzlagerkäfigs;
• 6 die Lage der Wälzkörper während einer Montage des Innenrings;
• 7 die Lage der Wälzkörper nach erfolgter Montage des Innenrings;
• 8 ein Kegelrollenlager in einer frühen Montageposition in einer ersten schematischen Schnittdarstellung;
• 9 ein Kegelrollenlager in einer frühen Montageposition in einer zweiten schematischen Schnittdarstellung;
• 10 ein Kegelrollenlager in einer späten Montageposition in einer ersten schematischen Schnittdarstellung; und
• 11 ein Kegelrollenlager in einer späten Montageposition in einer zweiten schematischen Schnittdarstellung.

The application is explained below on the basis of preferred embodiments with reference to the attached figures. show:

• 1 a schematic sectional view of a roller bearing unit with two mirror-inverted, largely identical tapered roller bearings;
• 2 a perspective view of a roller retainer;
• 3 a detail of a schematic sectional view of a tapered roller bearing in an assembly position;
• 4 a schematically illustrated front view of a tapered roller assembly to illustrate an enveloping circle;
• 5 a section of a roller bearing cage;
• 6 the position of the rolling elements during an assembly of the inner ring;
• 7 the position of the rolling elements after the inner ring has been installed;
• 8th a tapered roller bearing in an early mounting position in a first schematic sectional view;
• 9 a tapered roller bearing in an early mounting position in a second schematic sectional view;
• 10 a tapered roller bearing in a late assembly position in a first schematic sectional view; and
• 11 a tapered roller bearing in a late assembly position in a second schematic sectional view.

the 1 shows a roller bearing unit 100, which can also be referred to as an insert bearing, which comprises two mirror-inverted, largely identically designed tapered roller bearings 1, the inner rings 2 of which abut one another. The inner rings 2 are connected in the area of a joint 33, on which two flat surfaces of the respective inner rings 2 lie against one another, via a U-shaped locking ring 31, which snaps positively into corresponding ring grooves of the inner rings 2. A seal 32 is provided to seal the joint 33 .

This in 1 The tapered roller bearing 1 shown comprises the inner ring 2 and an outer ring 4 arranged coaxially with respect to an axis of rotation 3 thereto, between which rolling elements 7 inserted in a rolling element cage 6 and designed as tapered rollers are guided. The tapered roller bearing 1 is rotationally symmetrical in relation to the axis of rotation 3 .

As in particular in 2 As can be seen, the rolling element cage 6 comprises a cage rim 9 with a larger diameter and a cage rim 8 with a smaller diameter, which are connected via a large number of longitudinal webs 10 . Each rolling body 7 is inserted in a cage pocket 5 of the rolling body cage 6, which is bounded on the face side by the cage edges 8, 9 and on both sides by spaced-apart longitudinal webs 10.

1 shows that the inner ring 12 has a radially outwardly directed supporting rim 11 in its axial end section 42 with the larger diameter. Axially adjacent to the support shelf 11, a conical inner ring raceway 12 is formed on an outer lateral surface of the inner ring 2. The inner ring 2 has a safety rim 13 on its axial end section 43 with the smaller diameter, with a substantially cylindrical inner ring section 14 being provided between the conical inner ring raceway 12 and the safety rim 13 , which is designed as an annular groove 23 .

On the side part 25 with the smaller diameter (see 2 ) of the rolling element cage 6 are radially inwardly directed and arranged evenly spaced apart locking arms 15 are formed, the respective free end 45 (see 2 ) engage with slight play in the area of the inner ring section 14 between the rolling elements 7 and the safety rim 13, so that the latching arms 15 are secured in the axial direction by the safety rim 13 and the rolling elements 7. The engagement of the locking arms 15 between the rolling elements 7 and the safety flange 13 with play, which is subject to play, results in a low-friction coupling between the rolling element cage 6 and the inner ring 2 .

In addition, on the side part 25 of the roller body cage 6 with the smaller diameter, contact arms 24 directed radially outwards are formed for axial contact with a front contact surface 30 of the outer ring 4 . For this purpose, the respective free ends 28 of the contact arms 24 have a contact surface 29 (see 2 ), which are spaced between 0.1 mm and 0.2 mm in the direction of the axis of rotation in normal operation from the approximately annular end-face contact surface 30 of the outer ring 4 . If certain external forces are exceeded, the contact surfaces 29 of the contact arms 28 can rest against the end contact surface 30 of the outer ring 4 for securing purposes; when the two contact surfaces 30, 29 rest against one another, they are preferably in low-friction contact with one another.

Furthermore, in 1 It can be seen that the inner diameter of the outer ring 4 at its end facing the contact arms 24 is 0.5 to 1.5 mm, preferably 1 mm, smaller than that through the free ends 28 (cf. 3 ) of the contact arms 24 defined outer diameter. Due to this dimensioning, the outer ring 4 can be pushed over the bearing arms 24 from the inside during assembly. During operation, this dimensioning can ensure that the outer ring 4 is adequately secured by the contact arms 24 .

The tapered roller bearing 1 off 1 For example, when the outer ring 4 is fixed, it can absorb large axial forces acting on the inner ring 2 in the direction of the arrow 39 assigned to the respective tapered roller bearing 1 . In the opposite direction of arrow 39, the tapered roller bearing 1 can also absorb and transmit axial forces, since the force transmission (starting from the inner ring 2) essentially takes place via the locking arms 15 engaging in the inner ring section 14 and the contact arms 24 of the rolling element cage 6 on the rolling elements 6 takes place.

2 shows that the radially inwardly directed locking arms 15 and the radially outwardly directed contact arms 24 pointing away from them are integrally formed in each case offset in the radial direction opposite one another on the smaller-diameter side part 25 of the rolling element cage 6 .

An angle 36 between the latching arms 15 and the contact arms 24 is here only as an example between 80° and 120°, for example approximately 100°. The angle 36 is the opening angle on the outer side 40 with the smaller diameter, which is enclosed between the latching arms 15 and the contact arms 24 . If the opening angle cannot be easily determined due to the complex geometry of the locking and/or contact arms 24 , the main direction of extension of respectively adjacent locking and contact arms is taken as a basis for determining the angle 36 .

The rolling body cage 6 is preferably made in one piece from a metal or a plastic, including the latching arms 15 and the contact arms 24 .

The contact arms 24 reliably prevent the outer ring 4 from sliding off in an uncontrolled manner in the direction of the inner ring section 14 of the inner ring 2 . By means of the locking arms 15 and the contact arms 24 of the rolling element cage 6, the inner ring 2 and the rolling element cage 6 together with the rolling elements 7 accommodated therein, including the outer ring 4, are held together to form a structural unit that is easy to handle, in particular easy to store, transport and assemble in a target application.

The locking arms 15 and the contact arms 24 reduce any radial play in the rolling element cage 6 and increase the holding force of the outer ring 4 in relation to the rolling element cage 6 with the rolling elements 7 accommodated therein and the inner ring 2. As a result, when the tapered roller bearing 1 is used as a wheel bearing in a motor vehicle, a previously necessary retaining ring is no longer required. In addition, the rolling element cage 6 enables the rolling elements 7 to be positioned or a defined system to rest against the supporting rim 11 of the inner ring 2. Fer ner is a rotation of the tapered roller bearing 1 in the course of installation in a surrounding structure no longer necessary.

2 shows a perspective partial view of the rolling element cage 6 of one of the tapered roller bearings 1, which are part of the rolling bearing unit 100 in FIG 1 are shown. Here it can be clearly seen that between the side part 25 with the smaller diameter and a side part 27 with the larger diameter of the rolling element cage 6 run a large number of webs 10 which are oriented essentially parallel to the axis of rotation 3 and are each identical in design, which form a corresponding number of rolling element pockets 5. Two circumferentially immediately adjacent webs 10 each delimit, together with a section of the two side parts 25, 27 of the rolling element cage 6, a cage pocket 5 where for the sake of a better graphic overview only two chamfers 16 are provided with reference numerals, which are representative of all the others. The chamfers 16 form a bearing for the rolling bodies 7 that roll during operation. The cage pockets 5 can each be designed for inserting or for snapping in the frustoconical rolling bodies 7 .

The radially inward-pointing locking arms 15 and the radially outward-pointing contact arms 24 are formed on the side part 25 with the smaller diameter. The latching arms 15 and the contact arms 24 are integrally formed essentially on the smaller-diameter side part 24 of the rolling element cage 6 . Viewed in the circumferential direction of the rolling element cage 6, the contact arms 24 are each arranged in the region of a rolling element pocket 5 or between two webs 10 immediately adjacent on the circumferential side, so that the number of rolling element pockets 5 or the number of rolling elements 7 preferably corresponds to the number of contact arms provided on the rolling element cage 6 24 matches. The latching arms 15 are each arranged in the region of the webs 10 as viewed in the circumferential direction of the rolling element cage 6 .

A smaller-diameter groove 34 and a larger-diameter groove 35 are preferably formed on a front-side outer side 40 of the smaller-diameter side part 25 of the roller body cage 6 oriented away from the support flange 11 of the tapered roller bearing 1 . Through the effect of these grooves 34, 35, the elasticity of the latching arms 15 and the contact arms 24 of the rolling element cage 6 is increased, among other things.

At the in 2 The rolling element cage 6 shown is a rolling element cage 6, also known as a TVP window cage.

The longitudinal webs 10 of the 2 shown rolling element cage 6 are, as in 5 shown in detail, specially designed and allow as shown in the 8th and 10 shown, a limited tilting or pivoting of the rolling elements 7. During assembly, an axial insertion of the inner ring 2 into the rolling element cage 6, the rolling elements 7 used in the rolling element cage 6 tilt radially outwards about the larger-diameter cage rim 9 and thereby overcome the safety rim 13 of the inner ring 2.

How out 1 As can be seen, the safety rim 13 has a certain radial extent 41 . This is necessary due to the design because the two tapered roller bearings 1 are braced in the direction of the arrows 39 with a force of approximately 30 kN.

In the 3 the tapered roller bearing 1 is shown in an assembly position. Due to the chamfers 16 provided on the webs 10 (see 2 and 5 ) The rolling elements 7 on the smaller-diameter cage rim 8 have an increased degree of freedom. For this purpose, the longitudinal webs 10 of the rolling element cage 6 are designed in such a way that an assembly of the inner ring 2 is guaranteed if, with rolling elements 7 in the rolling element cage 6 abutting lightly, there is a difference between the inner enveloping circle diameter 21 formed by all rolling elements 7 (see Fig 4 ) and the maximum diameter 22 of the safety edge is 13 ≤ 1 mm. Here the overlap 44 of the safety edge 13 and the inner enveloping circle 18 of the rolling elements 7 is approximately 0.4 mm in the radial direction.

Furthermore, the 3 a lateral surface 46, which is part of the end of the inner ring 2 with the smaller diameter, against which the seal 32 rests in the assembled state. 3 shows that the diameter 47 of this lateral surface 46 is larger than the diameter 48 of the inner ring section 14 or the bottom of the groove 23. The diameter 22 of the securing rim 13 arranged axially between the lateral surface 46 and the inner ring section 14 is larger than the diameter 47 of the lateral surface 46 and the diameter 48 of the inner ring section 14.

4 serves only to illustrate the inner enveloping circle diameter 21. The rolling element cage 6 shown schematically there does not have the latching arms 15 and the contact arms 24, for example, for the purpose of better representation. the 4 shows a front view of the arrangement of the rolling elements 7, which are arranged in the rolling element cage 6 to form a roller and cage assembly 17. In 4 are of the rolling element cage 6, the smaller-diameter cage rim 8 and the longitudinal webs 10 are visible. All rolling elements 7 together delimit an inner enveloping circle 18 which has a diameter 21 which is 0.8 mm to 1 mm smaller than the maximum diameter 22 of the safety rim 13 (see 3 ) to allow assembly of the inner ring 12. Such a diameter 21 occurs when the rolling bodies 7 are tilted radially outwards, for example when tilted by an angle 37 (see FIG 8th ) of 2.7°.

the 5 shows a section of the rolling element cage 6. In the in 5 In the rolling element cage 6 shown, the longitudinal webs 10 have a chamfer 16 over the entire length between the cage edges 8, 9, which increases continuously in a wedge shape from the cage edge 9 with the larger diameter to the cage edge 8 with the smaller diameter. The bevel 16, which can also be referred to as a recess or opening, runs at a bevel angle 38, which can be from 1° to 4°. The chamfers 16 arranged facing each other in the cage pocket 5 of the rolling element cage 6 form a conical receptacle for the rolling elements 7.

In the 6 and 7 a section of the roller and cage assembly 17, which is formed from the rolling element cage 6 and the rolling elements 7, is shown in each case.

The representation according to 6 shows the roller and cage assembly 17 during assembly of the inner ring 2. The rolling elements 7 pressed radially outwards are supported on the chamfers 16 of the longitudinal webs 10, which have a largely triangular cross-sectional profile. The chamfers 16 arranged facing in the cage pocket 5 of the rolling body cage 6 together form a conical receptacle for the rolling bodies 7. A concave contact surface of the chamfers 16 is preferably adapted to an outer contour of the rolling bodies 7.

the 7 shows the rolling element 7 in the installed state, in which the rolling element 7 is supported on the front side on the supporting rim 11 (not shown) of the inner ring 2 and compared to FIG 6 are shifted radially inwards. A pocket clearance 20 is formed between the longitudinal webs 10 or their chamfers 16 and an outer surface 19 of the rolling elements 7, so that the rolling elements 7 are mounted on the smaller-diameter end of the rolling element cage 6 with radial play between the rolling element cage 6 and the inner ring 2.

8th shows the tapered roller bearing 1 with the rolling element 7 in an early assembly position, in which the rolling element 7 has been pushed a little more than halfway over the safety flange 13 in the axial direction. The rolling element 7 is shown in two positions in order to illustrate the tilting of the same about the cage rim 9 with the larger diameter. The rolling body 7 represented by solid lines is in contact with the chamfers 16 of the webs 10 (see FIG 9 ) and is thus maximally moved radially outwards. This corresponds to the position of the rolling element 7 which is also shown in 6 is shown. The rolling element 7 represented by the dashed line is tilted radially inwards and rests against the lateral surface 46 of the inner ring 2, on which the sealing ring 32 (see FIG 1 ) is attached. Thus, the rolling body 7 can be tilted by an angle 37 relative to its radially inner edge 42 at the end with the larger diameter, which is for example between 1 and 4°, further for example 2.7°.

9 shows the tilting of the rolling body 7 in a sectional view along the section line AA 8th . It can be clearly seen that the rolling body 7 represented by solid lines rests against the chamfer 16 of the longitudinal webs 10 and is thus pressed radially outwards, so that the inner enveloping diameter 21 (see 3 ) enlarged. The body represented by dashed lines is tilted radially inwards, so that the inner envelope diameter 21 (see 3 ) is reduced.

10 shows the tapered roller bearing 1 with a rolling element 7 in a later assembly position, in which the rolling element 7 has been pushed almost completely over the safety flange 13 in the axial direction. The rolling element 7 shown by means of solid lines is opposite the position of the rolling element 7 in dashed line by the angle 37 of about 1° to 4.5°, preferably between 1° and 4°, opposite the radially inner edge 26 at the end of the rolling element with the larger diameter 7 tilted; such a tilting of the rolling elements 7 is sufficient to move the rolling elements 7 over the safety rim 13 without causing damage while applying a corresponding axial force, so that they can be reliably brought into the mounted position in which the rolling elements 7 can roll on the inner ring raceway 14.

11 shows analogous to 9 in a sectional view along the section line AA 10 the corresponding tilting of the rolling element 7.

Reference List

1

tapered roller bearing

2

inner ring

3

axis of rotation

4

outer ring

5

cage bag

6

rolling element cage

7

rolling elements

8th

cage board

9

cage board

10

longitudinal webs

11

support board

12

inner ring raceway

13

safety board

14

inner ring section

15

locking arms

16

chamfer

17

roller wreath

18

inner enveloping circle

19

outer surface (of the rolling element)

20

pocket air

21

inner enveloping circle diameter

22

maximum outer diameter of the safety edge

23

ring groove

24

investment arms

25

side part with smaller diameter

26

edge

27

larger diameter side panel

28

free end (of the contact arm)

29

contact surface (of the contact arm)

30

face outer surface (of the outer ring)

31

locking ring

32

poetry

33

Gap

34

smaller-diameter groove

35

larger diameter groove

36

Angle between locking arm and contact arm

37

tilting angle (of the rolling element)

38

bevel angle

39

Arrow

40

outside

41

radial extension of the safety board

42

axial end section (large diameter)

43

axial end section (small diameter)

44

overlap

45

free end (locking arm)

46

lateral surface (of the inner ring)

47

diameter

48

diameter

49

axial distance

100

roller bearing unit

QUOTES INCLUDED IN DESCRIPTION

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Patent Literature Cited

• DE 3524063 A1 [0002]
• DE 102014205051 A1 [0003]
• DE 102006057512 A1 [0003]
• DE 2739367 A1 [0003]
• DE 102016210331 A1 [0003]

Claims (10)

Tapered roller bearing (1) comprising - an inner ring (2) and an outer ring (4) arranged coaxially above it, between which rolling elements (7) designed as tapered rollers and inserted in cage pockets (5) of a rolling element cage (6) are arranged, so that the inner ring (2nd ) relative to the outer ring (3) can be rotated about an axis of rotation (3), wherein - the cage pockets (5) of the end cage rims (8, 9) and between the cage rims (8, 9) running longitudinal webs (10) of the rolling element cage (6) are limited, wherein - the inner ring (2) has a radially outwardly directed support rim (11) on its axial end section (42) with a larger diameter, and - axially next to the support rim (11) on an outer lateral surface of the inner ring (2) a conical Inner ring raceway (12) for the rolling elements (7) is formed, wherein - the inner ring (2) at its axial end portion (43) with a smaller diameter has a radially outwardly directed safety rim (13) by an inner ring abs section (14) is spaced axially from the inner ring raceway (12), wherein - the rolling element cage (6) has latching arms (15) which engage in the axial direction between the rolling elements (7) and the safety flange (13), so that the rolling element cage (6 ) is secured in the axial direction, characterized in that - the longitudinal webs (10) of the rolling element cage (6) each have a chamfer (16) on inner sides facing one another, which extends from the larger-diameter cage rim (9) and is continuous enlarged. Taper roller bearing (1) after claim 1 , characterized in that the facing chamfers (16) of the rolling element cage (6) together form a conical receptacle for the rolling element (7). Tapered roller bearing (1) according to one of the preceding claims, characterized in that the chamfers (16) are designed in such a way that the rolling bodies (7) can be pivoted between ≥ 1° and ≤ 4° about the larger-diameter cage rim (9) during assembly. Tapered roller bearing (1) according to one of the preceding claims, characterized in that in the mounted state an inner enveloping circle diameter (21) defined by the rolling elements (7) is smaller than a maximum outer diameter (22) of the safety rim (13). Tapered roller bearing (1) according to one of the preceding claims, characterized in that - the inner ring section (14) has an annular groove (23). Tapered roller bearing (1) according to one of the preceding claims, characterized in that - the rolling element cage (6) has a large number of radially outwardly directed contact arms (24) which are designed for axial fixing to the axial end of the outer ring (4) with the smaller inside diameter. Taper roller bearing (1) after claim 6 , characterized in that the latching arms (15) are arranged on the smaller-diameter side part (25) of the rolling element cage (6), viewed in the circumferential direction of the same, in the area of the longitudinal webs (10) and the contact arms (24) are each in the area next to the longitudinal webs (10 ) are arranged. Tapered roller bearing (1) according to one of Claims 6 or 7 , characterized in that at the free end (28) of the contact arms (24) a contact surface (29) is formed, which are each axially spaced from a front-side outer surface (30) of the outer ring (4), this outer surface (30) of the outer ring (4) is directed axially away from the support flange (11) of the inner ring (2) with the larger diameter. Rolling bearing unit (100), characterized in that the rolling bearing unit (100) constructed as an insert bearing comprises two tapered roller bearings (1) according to one of the preceding claims, wherein the two inner rings (2) are connected to one another via a retaining ring (31), wherein one Gasket (32) seals a joint (33) between the two inner rings (2). roller bearing unit claim 9 , characterized in that the safety flanges (13) of the two tapered roller bearings (1) are designed to create an axial bearing for the between the safety flanges (13) arranged seal (32).

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