WO2006026947A1

WO2006026947A1 - Massive cage for a roller bearing, especially a double-row spherical roller bearing, and method for determining the boring angle of the cage pockets and the longitudinal radius of the webs of such a massive cage

Info

Publication number: WO2006026947A1
Application number: PCT/DE2005/001424
Authority: WO
Inventors: Gerhard Schorr; Martin Grehn; Manfred Gessner
Original assignee: Schaeffler Kg
Priority date: 2004-09-08
Filing date: 2005-08-12
Publication date: 2006-03-16
Also published as: DE102004043374A1; EP1787037A1

Abstract

The invention relates to a massive cage (2) for a roller bearing (1), especially a double-row spherical roller bearing. Said massive cage (2) is composed of a circumferential massive cage ring (3) which comprises a row (6, 7) of massive webs (8) on each of the two axial lateral faces (4, 5) thereof, said massive webs (8) extending away from the cage ring (3) substantially in the direction of the bearing axis and being placed at regular intervals from each other. The opposite axial surfaces (9, 10) of two adjoining webs (8) of each row (6, 7) are embodied with a concave shape that is adapted to the exterior face (12) of the roller bearing (1) rollers (11) such that one respective cage pocket (13) into which a roller bearing (1) roller (11) can be inserted is formed between said webs (8). According to the invention, the longitudinal axis (14) of each cage pocket (13) is provided with a boring angle (ß) that deviates from the pressure angle (a) of the roller bearing (1) to such a degree that the exterior faces (12) of the roller bearing (1) rollers (11) which are inserted into the cage pockets (13) are located at a nearly constant minimized radial distance (va or vi) from both the outer and the inner axial edges (15, 16, 17, 18) of the webs (8) of the cage pocket (13) thereof on each radial cross-sectional plane (I to III) of the rollers (11).

Description

Name of the invention

Solid cage for a roller bearing, in particular for a double-row spherical roller bearing, and method for determining the drilling angle of the cage pockets and the longitudinal radius of the webs of such a solid cage

description

Field of the invention

The invention relates to a solid cage for a roller bearing according to the features of patent claim 1 and to a method for determining the angle of rotation of the cage pockets and the longitudinal radius of the webs of such a solid cage, and is particularly advantageous in a two-row spherical roller bearing and on all types of storage feasible, in which the outer and the inner contour of the cage cross-section is not parallel to Wälzkör¬ perlängsachse.

Background of the invention

It is generally known to the person skilled in the art of rolling bearing technology that, in the case of cage types for rolling bearings, a distinction is fundamentally made between sheet metal cages and solid cages made of different materials. The usual sheet metal cages are usually stamped or pressed from sheet steel or brass sheet and are characterized by solid cages by a Lower weight and by a lighter lubricant supply in Lager¬ from inside. In contrast, solid cages usually consist of blanks made of brass, steel, light metal or hard tissue, which are machined by turning and milling and, above all, are advantageous for small series and for reasons of strength for large, heavily loaded rolling bearings.

Such, designed as a comb cage for a double row spherical roller bearing solid cage is already known for example from DE 200 20 397 U1. This solid cage consists of a circumferential cage ring, which has on each of its two axial side faces a row of solid webs extending substantially in the direction of the bearing axis of the cage ring and equally spaced from each other. The opposite axial surfaces of two adjacent webs of each row are in this case formed with a concave shape adapted to the lateral surface of the rollers, so that in each case a cage pocket is formed between these webs, in which a roller of the roller bearing can be inserted.

In such a solid cage for a spherical roller bearing, however, it is disadvantageous that its cage pockets are usually incorporated by a form cutter with a perpendicular to the respective pressure angle of the bearing longitudinal axis in the cage blank, so that the lateral surfaces of the barrel rollers used in the cage pockets of the roller bearing in different radial cross-sectional planes have different radial distances both to the outer and to the inner axial edges of the webs of their cage pocket. Starting from the usual pocket air between the barrel rollers and the webs of their cage pocket, this causes a local tarnishing of the barrel rollers at the axial edges of the webs of their cage pocket, especially at the operating temperature of the spherical roller bearing at the roller cross-sectional plane with the smallest radial distance to the cage pocket webs the result that the required lubricating film between the rollers and the cage locally breaks and is exceeded by the resulting frictional heat, the permissible operating temperature of the bearing to the partial burning of the lubricant. In addition, it is due to the To the barrel rollers at the axial edges of the webs to increased Ver¬ wear of the webs of the cage pockets, which can lead to jamming of the rollers in their cage pockets and ultimately to the failure of the spherical roller bearing. A simple measure for eliminating these adverse effects, although it would be to increase the diameter of the cage pockets so that it can not come to a tarnishing of the barrel rollers on the axial edges of the webs of their cage pocket even at the level of the roller cross-sectional plane with the smallest radial distance to the cage pocket webs However, this would in turn have the consequence that in other roller cross-sectional planes the radial distance to the cage pocket webs would be too great for an optimal roller guidance in the cage pockets.

Object of the invention

On the basis of the stated disadvantages of the known state of the technology, the invention is therefore based on the object of conceiving a solid cage for a roller bearing, in particular for a double-row spherical roller bearing, with which without enlarging the diameter of the cage cage Start of the barrel rollers at the axial edges of the webs of their cage bags at operating temperature of the spherical roller bearing is effectively avoided.

Description of the invention

According to the invention this object is achieved in a solid cage for a roller bearing according to the preamble of claim 1 such that the longitudinal axis of each cage pocket opposite the pressure angle α of the roller bearing has such a different drilling angle ß, that the lateral surfaces of the pockets used in the Käfig¬ roles of the roller bearing In each radial cross-sectional plane of the rollers, they have an approximately constant minimized radial spacing relative to both the outer and the inner axial edges of the webs of their cage pocket. In an expedient development of the solid mass design according to the invention, the deviating drilling angle β of each cage pocket is fundamentally smaller than the contact angle α of the respective roller bearing and has different values depending on it. However, this is true only for the largest part of all conceivable cross-sections of solid cages, since it is also possible in a certain constellation of outer and inner contour of the cage cross-section that the deviating Bohrwinkel ß is greater than the Druckwin¬ angle α of the respective roller bearing , Regardless of the type of bearing and the bearing size, however, this deviating drilling angle β can be determined by a uniform method in which the relative thermal expansion of the rollers of the roller bearing of a roller cage other than the solid cage is taken into account with maximum and minimum temperature use of the roller bearing , Further details of this method according to the invention, with which the longitudinal radius of the webs of the solid cage can be determined at the same time, can be deduced from the following description of an embodiment of the solid cage according to the invention.

The solid cage designed according to the invention for a roller bearing thus has the advantage over the solid cages known from the state of the art that, by incorporating the cage pockets into the cage blank with a smaller boring angle relative to the contact angle .alpha Lagerradialluft and the operating temperature optimum geometry of the cage pockets through which the rollers of the roller bearing in each radial cross-sectional plane of the rollers both to the outer and to the inner axial edges of the webs of their cage pocket have a uniform klei¬ nen radial distance. As a result, without an increase in the diameter of the cage pockets, start-up of the barrel rolls at the axial edges of the webs of their cage pockets at the operating temperature of the spherical roller bearing is effectively avoided and the disadvantages resulting from this approach of the barrel rolls to the pocket webs, such as a local tearing of the lubricating film between the rollers and the cage or jamming of the rollers in their cage pockets are excluded. Brief description of the drawings

A preferred embodiment of the inventively embodied Mas¬ sivkäfigs for a roller bearing and the aforementioned method for determining the Bohrwinkels ß of the cage pockets and the longitudinal radius of the webs of a Massivkä¬ fig will be explained in more detail with reference to the accompanying drawings nä¬ forth. Showing:

Figure 1 is an enlarged detail of a perspective view of a spherical roller bearing without outer ring with inventively designed solid cage and a roller;

FIG. 2 / I shows a first cross section through a cage pocket of the solid cage according to the invention in accordance with the cross-sectional plane I in FIG. 1;

FIG. 2 / II shows a second cross section through a cage pocket of the solid cage according to the invention in accordance with the cross-sectional plane II in FIG. 1;

FIG. 2 / III shows a third cross section through a cage pocket of the solid cage according to the invention in accordance with the cross-sectional plane III in FIG. 1;

FIG. 3 shows an illustration of step a) of the method according to the invention for determining the boring angle β of the cage cage and the longitudinal radius S _L R of the bars of a solid cage;

FIG. 4 shows an illustration of steps b) and c) of the method according to the invention for determining the drilling angle β of the cage pockets and the longitudinal radius SLR of the webs of the solid mass cage;

FIG. 5 shows an illustration of the steps d) and e) of the method according to the invention for determining the drilling angle .beta. figtaschen and the longitudinal radius SLR of the webs of Massivkä¬ figs;

FIG. 6 shows an illustration of step f) of the method according to the invention for determining the drilling angle β of the cage cage as well as the longitudinal radius S _L R of the bars of the solid cage;

FIG. 7 shows an illustration of step g) of the method according to the invention for determining the drilling angle β of the cage cage and the longitudinal radius S _L R of the webs of the solid cage;

8 shows an illustration of the steps I) and m) of the method according to the invention for determining the drilling angle β of the cage pockets and the longitudinal radius S _L R of the webs of the solid mass cage;

FIG. 9 shows a reduced overall view of the solid cage designed according to the invention;

Figure 10 is an enlarged view of the longitudinal section A - A of Figure 9 by a cage pocket of the invention ausgebil¬ Deten massive cage.

Detailed description of the drawings

From Figure 1 is clearly designed as a double-row spherical roller bearings roller bearing 1, which consists essentially of an outer bearing ring, not shown, and an inner bearing ring so¬ as a number between the bearing rings in two rows next to each other on their careers rolling rollers 11 , which are held by a trained as comb cage solid cage 2 at equal intervals zueinan¬. Clearly visible, this solid cage 2 consists of a circumferential massive cage ring 3, which at each of its two axia¬ len side surfaces 4, 5 a row 6, 7 substantially in Lagerachsrich¬ direction away from the cage ring 3 wegerstreckende and evenly spaced each other. stood, massive webs 8 has. The opposing axial surfaces 9, 10 of two adjacent webs 8 each row 6, 7 are also formed with a mantle surface 12 of the rollers 11 of the roller bearing 1 adapted concave shape, so that between these webs 8 each have a cage pocket 13 is formed in a Roller 11 of the roller bearing 1 can be used.

Furthermore, it is shown in Figure 1 that to avoid the tarnishing of the rollers 11 at the axial edges 15, 16, 17, 18 of the webs 8 of their cage pockets 13 at operating temperature of the roller bearing 1, the longitudinal axis 14 of each Käfigta- see 13 with respect to the contact angle α of Roller bearing 1 has a different drilling angle ß. It is thereby achieved that the lateral surfaces 12 of the rollers 11 of the roller bearing 1 inserted into the cage pockets 13, as shown in FIGS. 2 / I, 2 / II and 2 / III, are in each of the radia¬ len indicated in FIG Cross-sectional planes I to III of the rollers 11 both to the outer and to the inner axial edges 15, 16, 17, 18 of the webs 8 of their cage pocket 13 have an approximately constant minimized radial distance v _a and Vj, by the start of the rollers 11 at the axial edges 15, 16, 17, 18 of the webs 8 is no longer possible. The deviating drilling angle β of each cage cage 13 is smaller than the contact angle α of the roller bearing 1 and has different values depending on this for different bearing sizes. Regardless of the type of bearing and the size of the bearing, however, this deviating drilling angle β can be determined by a uniform method illustrated in FIGS. 3 to 10, in which the relative thermal expansion of the rollers 11 of the material consisting of a material other than the solid cage 2 Roller bearing 1 is considered to the solid cage 2 at maximum and minima¬ lem temperature use of the roller bearing 1.

In this method, in a first step shown in FIG. 3, first of all the definition of a first cross-sectional plane I through the center MR of a roller 11 of the roller bearing 1 and then the arrangement of the center MD _{I of} the corresponding roller diameter D _R i on the intersection between the vertical Roller axis X and the pitch circle diameter T of the cage ring 3. As a second step, the displacement of the roller diameter D _R1 on the vertical roller axis X out of the partial circle position outwards is then effected by the amount va _{max of} the pocket air and the marking of a contact point A of the roller diameter Dm at the point of intersection with the outer diameter D ₃ of FIG Cage rings 3. This contact point A is then moved as a third, also shown in Figure 4 step outward along the verlän¬ siege connection line Vi between this and the center M of Käfig¬ rings 3 by an amount vt _m j _n , the relative thermal expansion of roller 11 and solid cage 2 with minimum temperature use of the roller bearing 1 corresponds.

In the same way, in a fourth and fifth step of the method according to the invention, the roll diameter DR _{1 shown} displaced on the vertical roller axis X from the partial circle position to the inside by the amount vi _{max of} the pocket air and the mark ei¬ nes contact point B of the roll diameter D _R i at the intersection of the inner diameter Dj of the cage ring 3 and the shifting of this contact point B inward along the connecting line V ₂ between this and the center M of the cage ring 3 by an amount vt _max , which is the relative Wärme¬ expansion of roller 11 and solid cage 2 at maximum temperature use of the roller bearing 1 corresponds.

In FIG. 6, it is then shown that, as the sixth step, the joining of the displaced contact points A and B takes place with a straight line Gi and the formation of a perpendicular bisector Li on this straight line Gi, which intersects the vertical roller axis X at a point which the center Mn of the pocket diameter D _t i and the radius of the pocket pitch circle TT ₁ in the first cross-sectional plane I results.

Subsequently, as a seventh step, as can be seen in FIG. 7, a circle is drawn around the center M _n with a radius which corresponds to the distance of the center point M _t1 from the shifted contact points A or B, so that itself as a result of the pocket diameter Du in the first cross-sectional segment I through the roller 11 of the roller bearing 1.

Thereafter, as summarized steps 8 and 9 of the method according to the invention, the determination of any second and third transverse plane II and IM by the roller 11 of the roller bearing 1 within the cage pocket 13 and the arrangement of the midpoints M _D 2 and M _{D3 of} the ent ¬ speaking roll diameter DR ₂ and DR ₃ on the intersection between the vertical roll axis X and pitch diameter T of the cage ring 3 with subsequent duplicate repetition of steps 1 to 7 for the second and third cross-sectional plane II and IM, through which the pocket centers M _t 2 and M _t 3, the pocket diameter D _t2 and D _t3 as well as the radii of the Ta¬ schenteilkreisreise TT ₂ and TT ₃ in the second and third cross-sectional plane II and IM through the roller 11 of the roller bearing 1 result.

In a tenth step shown in FIG. 8, the ascertained pocket centers M _t i to M _t3 and the determined pocket diameters Dn to D _{t3 are then transferred} into a scale-oriented sectional view through the cage pocket 13, the determined radii of the pocket subcircuits TT ₁ to TT ₃ in each cross-sectional plane I to IM form the respective reference point. By likewise if shown in Figure 8 connecting all pocket centers of Mn to M _t3 by a straight line G ₂ and the final measurement of the angle between the resulting by the connection line L ₂ and the longitudinal axis L _κ of the retainer ring 3 is then obtained, finally, the drilling angle ß of the cage pockets 13 of the invention formed according to solid cage. 2

For further determination of the longitudinal radius S _L R of the webs 8 of each cage pocket 13, the determined pocket diameters D _t i and D _t2 and D _t2 and D _{t3 are} then in an eleventh step, also indicated in FIG. 8, additionally with one straight line G in each case ₃ and G ₄ connected to each other, on which in the center M _L R of the longitudinal radius SLR of the webs 8 intersecting respective bisectors L ₂ and L _{3 are} formed. Finally, a circle is drawn around the midpoint MLR with a radius which is equal to the distance of the center. telpunktes M _L R ZU one of the pocket diameter Dn to D ₁₃ corresponds, and this radius is pivoted by 90 ° about the horizontal roller axis Y, so that as a result of the again in Figures 9 and 10 for better illustration longitudinally illustrated longitudinal radius SLR of the webs each cage pocket 13 gives.

LIST OF REFERENCE NUMBERS

1 roller bearing MD2 center of D _R2

2 massive cage 35 M _D 3 center of D _R3

3 cage ring X vertical roller axis

4 side surface Y horizontal roller axis

5 side surface T pitch circle diameter of 3

6 row va _max maximum pocket air outside

7 Series 40 Vimax maximum pocket air inside

8 webs A contact point

9 axial surface B contact point

10 Axial surface Since outer diameter of 3

11 rolls Di inner diameter of 3

12 lateral surface 45 Vi first connecting line

13 cage pocket V ₂ second connecting line

14 longitudinal axis M center point of 3

15 outer axial edge Vtmax relative thermal expansion at ma

16 outer axial edge ximaler operating temperature

17 inner axial edge 50 Vtmin relative thermal expansion at mi

18 inner axial edge nimaler operating temperature

I first cross-sectional plane Gi first straight

II second cross-sectional plane G ₂ second straight line

In the third cross-sectional plane G ₃ third straight line α pressure angle of 1 55 G ₄ fourth straight line ß drilling angle of 13 D ₁₁ pocket diameter in I

Va Radialbstand to 15, 16 Dt ₂ pocket diameter in Il

Vi radial distance to 17, 18 D ₁₃ pocket diameter in IM

SLR longitudinal radius of 8 M ₁₁ center point of D _t i

MR center of 11 60 M, ₂ center of D _t2

Dm roll diameter in IM ₁₃ midpoint of D _t3

DR ₂ roll diameter in Il TT ₁ pocket pitch circle radius in I

DR ₃ roll diameter in III TT ₂ pocket pitch circle radius in Il

M _D I center point of D _R1 TT ₃ pocket pitch circle radius in IM FAG 1504-HZA 12

Li perpendicular to Gi

L2 perpendicular to G2

L ₃ perpendicular to G ₃

M _L R Center of the longitudinal radius of 8

Claims

claims

1. Massive cage for a roller bearing, in particular for a double row Pendelrol¬ lenlager consisting of a circumferential solid cage ring (3) at each of its two axial side surfaces (4, 5) a row (6, 7) substantially in Lagerachsrichtung from Cage ring (3) wegerstreckende so¬ as uniformly spaced apart, solid webs (8), whereby the opposite axial surfaces (9, 10) of two adjacent webs (8) of each row (6, 7) with one of the lateral surface (12) the rollers (11) of the roller bearing (1) are adapted to a concave shape and between these webs (8) a cage pocket (13) is formed, into which a roller (11) of the roller bearing (1) can be inserted; characterized in that the longitudinal axis (14) of each cage pocket (13) relative to the pressure angle (α) of the roller bearing (1) has a different drilling angle (ß), that the lateral surfaces (12) of the cage pockets (13) used rollers ( 1 1) of the roller bearing (1) in each radial cross-sectional plane (I to III) of the rollers (11) both to the outer and to the inner axial edges (15, 16, 17, 18) of the webs (8) of their cage pocket (13) have an approximately constant minimized radial distance (v _a and Vi).

2. Massive cage according to claim 1, characterized in that the deviating drill angle (β) of each cage pocket (13) is always smaller than the contact angle (α) of the respective roller bearing (1) and has different values depending on this, but by a uniform method can be determined, in which the relative thermal expansion of the one from another Material as the solid cage (2) existing rollers (11) of the roller bearing (1) to the solid cage (2) is taken into account at maximum and minimum temperature use of the roller bearing (1).

Method for determining the drilling angle (β) of the cage pockets (13) and the longitudinal radius (SLR) of the webs (8) of a solid cage (2) with the features of claims 1 and 2, characterized by the following steps:

a) defining a first cross-sectional plane (I) through the center (M _R ) of a roller (11) of the roller bearing (1) and arrangement of the center

(M _D i) of the corresponding roller diameter (Dm) on the Schnitt¬ point between the vertical roller axis (X) and pitch circle diameter (T) of the cage ring (3);

b) shifting the roller diameter (D _R1 ) on the vertical Rollen¬ axis (X) from the pitch circle outward by the amount (va _max ) of the pocket air and marking a contact point (A) of the Rollendurch¬ diameter (DR ₁ ) at the intersection of Outer diameter (D _a ) of the cage ring (3);

c) shifting the contact point (A) outward along the extended connecting line (V ₁ ) between this and the center (M) of the Kä¬ figrings (3) by an amount (vtmin), the relative thermal expansion of the roller (11) and Massive cage (2) with minimum use of temperature of the roller bearing (1) corresponds to;

d) shifting the roller diameter (D _R1 ) on the vertical Rollen¬ axis (X) from the part circle position to the inside by the amount (vi _max ) of Ta¬'s air and marking a contact point (B) of the roll diameter (D _R1 ) on Intersection with the inner diameter (Dj) of the cage ring (3);

e) shifting the contact point (B) inwardly along the Verbindungs¬ line (V ₂ ) between this and the center (M) of the cage ring (3) to an amount (vW) corresponding to the relative thermal expansion of roller (11) and solid cage (2) at maximum temperature application of the roller bearing (1);

f) connecting the shifted contact points (A and B) to a straight line (Gi) and forming a perpendicular bisector (Li) on this straight line (Gi) which intersects the vertical roller axis (X) at a point defining the midpoint (M _t - ι) of the pocket diameter (D _n ) and the radius of the pocket sub-circle (TT ₁ ) in the first cross-sectional plane (I) results;

g) pulling a circle around the center (M _t i) with a radius corresponding to the distance of the center point (M _t i) to the shifted contact points (A or B) and receiving the pocket diameter (D _t -ι) in the ers ¬ th cross-sectional plane (I) through the roller (11) of the roller bearing (1);

h) fixing a second cross-sectional plane (II) by a roller (11) of the roller bearing (1) within the cage pocket (13) and arrangement of the center point (MD ₂ ) of the corresponding roller diameter (DR2) on the intersection between the vertical roller axis (X ) and pitch circle diameter (T) of the cage ring (3);

i) repetition of steps b) to g) for the second cross-sectional plane (II) by the roller (11) of the roller bearing (1) and obtaining the Taschenmittel¬ point (M _t2 ), the pocket diameter (Dt ₂ ) and the radius of Ta - Schenteilkreises (TT ₂ ) in the second cross-sectional plane (II) by the Rol¬ le (11) of the roller bearing (1);

j) determining a third cross-sectional plane (III) by a roller (11) of the roller bearing (1) within the cage pocket (13) and arranging the center point (M _D3 ) of the corresponding roller diameter (D _R3 ) on the

Intersection between vertical roller axis (X) and Teilkreisdurch¬ diameter (T) of the cage ring (3); k) repetition of steps b) to g) for the third cross-sectional plane (III) by the roller (11) of the roller bearing (1) and obtaining the Taschenmittel¬ point (M ₁₃ ), the pocket diameter (D _t3 ) and the radius of Ta ¬ Schenteilkreises (TT ₃ ) in the third cross-sectional plane (IM) through the roller (11) of the roller bearing (1);

I) transmission of the determined pocket center points (Mn to M _t3 ) and the Ta¬ diameters (D _t i to D _t3 ) in a scaled sectional view through the cage pocket (13), wherein the determined radii of the pocket subcircles (TT ₁ to TT _3rd ) in each cross-sectional level (I to IM) the respective

Form a reference point;

m) Connection of all pocket centers (Mn to M _t3 ) with a straight line (G ₂ ) and measurement of the angle between the line (G ₂ ) formed by the connection and the longitudinal axis (L _κ ) of the cage ring (3)

Preservation of the drilling angle (β) of the cage pockets (13);

n) connection of the determined pocket diameter (Dn and D ₁₂ and D _t2 and D ₁₃ ), each with a straight line (G ₃ and G ₄ ) and formation of the respective perpendicular bisector (L ₂ and L ₃ ) on both straight lines (G ₃ and G ₄ ), which are in the

Cut center (M _LR ) of the longitudinal radius (S _L R) of the webs (8);

o) drawing a circle about the center (M _LR ) with a radius corresponding to the distance of the center point (M _L R) TO one of the pocket diameter (D _t i to D _t3 ), pivoting this radius by 90 ° about the horizontal right roller axis (Y) with preservation of the longitudinal radius (SLR) of the webs (8) je¬ the cage pocket (13).