DE102019107271A1 - Cylindrical roller bearing and fixed-bearing arrangement with a cylindrical roller bearing - Google Patents

Abstract

The invention relates to a cylindrical roller bearing (1) with cylindrical rollers (2) and with an outer ring (3), wherein the cylindrical rollers (2) are provided with a length (L) and a roller diameter (DR), - a first ratio (L: DR) of roll length (L) to the roll diameter (DR) ≤ the numerical value 3, - the outer ring (3) has an annular body (4) with a cross-section determined by an axial width (B) and a radial height (H) Ring body (4) outside an outer cylindrical surface (11) having an outer diameter (DA), - the outer ring (3) is provided with an inner race (6), - the inner race (6) has a first inner cylindrical surface (12) with a first Inner diameter (DI), - the raceway (6) is turned radially inwardly to an axially oriented axis of rotation (5) of the cylindrical roller bearing (1), - the outer ring (1) in one piece-einmaterialig with a first board (7) and a second Board (8) is provided, - the shelves (7, 8) radially i n direction of the axis of rotation (5) from the ring body (4) protrude and thereby beyond the inner race (6) in the radial direction with a board height (BH) directed radially perpendicular to the rotation axis (5) protrude, - the inner race (6) is axially formed between the rims (7, 8) spaced apart axially with respect to one another (A), - the width (B) of the outer ring is the sum of the axial distance (A) between the rims (7, 8), Width (BB1) of the first board 7 and the width (BB2) of the second board (8).

Description

Field of the invention

The invention relates to a cylindrical roller bearing with cylindrical rollers and with an outer ring and a fixed-bearing assembly with such a cylindrical roller bearing.

Background of the invention

DE 10 2006 031 048 A1 describes a vehicle transmission. An output shaft of this vehicle transmission is mounted with a fixed-floating bearing assembly in the vehicle transmission. The fixed bearing is a ball bearing and the floating bearing is a sleeve roller bearing. DE 19814309 C1 discloses a axle drive. In the axle drive, a differential is rotatably mounted by means of a fixed-floating bearing assembly. The fixed bearing is formed by two opposing inclined bearing. The floating bearing is a cylindrical roller bearing with two bearing rings. The inner ring of the cylindrical roller bearing has no axial edges. The outer ring is provided with axial ribs.

The sleeve roller bearing and the cylindrical roller bearing both have cylindrical rollers as rolling elements. Most of them are caged. The main difference between a sleeve roller bearing and a cylindrical roller bearing lies in the design of the outer ring.

When sleeve roller bearing, the outer ring is a roller sleeve. The roller sleeve is usually drawn from sheet metal. For this purpose, a cup with a cylindrical part and a bottom is first formed from a circuit board. The bottom of the cup is perforated so that a radially inwardly facing edge remains on the cylindrical part. This edge forms one of the rims of the outer ring. The axial thickness of the board usually corresponds to the thickness of the starting material of the board and is therefore even thicker than the wall of the cylindrical part. The bottom of the opposite end of the sleeve is radially inwardly formed, for example by crimping so that the other board is formed. The axial wall thickness of this Bordes is technically conditionally somewhat less than the wall thickness of the cylindrical part of the sleeve.

For the production of the roller sleeve steel is used, which can be formed and therefore naturally has little carbon. To harden the material, therefore, the surface must be carburized or otherwise enriched. Accordingly, during surface hardening, such as case hardening, only the surface is cured to a certain application depth. The core of the material stays soft.

The advantage of the sleeve roller bearings is on the one hand in the small radial space requirement of the outer ring and the other in the elastic behavior of the wall of the outer ring. In addition, the shelves are relatively narrow, so that almost the entire width of the outer ring for the career of the rollers and the rollers can be used. The weight of the bearing is low due to the thin-walled outer ring. The use of a sleeve roller bearing is particularly advantageous in vehicle transmissions with small center distances of the transmission shafts, since the bearings due to the small axial distances only little radial space is available. However, this only works if the loads on the storage site are not too high. The only surface hardened track is limited in terms of their load capacity.

The outer ring of the cylindrical roller bearing is designed to be solid relative to the roller sleeve, d. h., He has a relatively large radial height, and therefore has high load capacities. The material used is bearing steel, which can be hardened well and preferably. The radial dimensions of the outer ring are relatively large. This results in large diameters of the outer dimensions of the cylindrical roller bearings. They are heavy.

Description of the invention

The object of the invention is therefore to provide a roller bearing and a floating bearing of the type of roller bearing, with which the aforementioned disadvantages are avoided.

This object is achieved by the subject matter of claim 1.

It is envisaged that a first ratio of roll length to roll diameter is less than or equal to the numerical value 3 is, wherein the width of at least one of the shelves is less than or equal to 11% of the width of the outer ring. The width of the outer ring is the sum of the axial distance between the edges of the outer ring and the width of the first board and the width of the second board of the outer ring.

The advantage of the cylindrical roller bearing according to the invention is that this combines the advantages of the sleeve roller bearings and the massive roller bearings in itself. That is, on the one hand is available through the axially narrowed shelves almost the entire width of the outer ring and or the inner ring for the career of the rollers available. The roles can be designed to be longer and the load capacity of the camp are higher overall with a small overall width of the camp. On the other hand, due to the larger radial wall thicknesses of the outer rings above their inner race, the high load capacity the cylindrical roller bearings are exploited. The production can be dependent on the selected lot sizes with relatively little investment in tools.

The concept of floating bearings is usually used in fixed-bearing arrangements for the rotational storage of shafts and machine elements. Shafts are, for example, gear shafts and machine elements and may be, for example, gears of vehicle transmissions. The shaft is mounted on two bearings. The shafts and machine elements are mounted radially at both bearing points by means of rolling bearings. A storage location is equipped with at least one fixed storage. The fixed bearing absorbs axial forces in both directions. In cylindrical roller bearings, for example, both bearing rings are provided with axial ribs, between which the rollers are arranged axially and supported against axial thrust. Both bearing rings are firmly seated in or on the bearing seat. Accordingly, the fixed bearing point has no degree of freedom axially.

The other depository will be a floating depository. In this floating bearing point, the shaft or the machine element by means of the rolling bearing while radially supported but otherwise axially free to move out. With such an arrangement, thermal expansion and axial length tolerances of the system can be compensated or compensated. At floating bearing points, either the rolling bearings are movably received relative to the surrounding structure or the rolling bearings have internal axial degrees of freedom. Rolling bearings are movable against the surrounding structure, for example, when the inner ring to the shaft seat or the outer ring to its housing seat is axially displaceable, or if according to an embodiment of the invention, the outer raceway for the cylindrical rollers is formed directly on the shaft.

In rolling bearings of the type considered, ie those with inner axial degrees of freedom, either the shaft fixed to the inner ring against the rolling elements axially displaceable and the rolling elements are performed with relatively little clearance between two axial edges of the outer ring or the rolling elements are compared to the fixed in the housing seated outer ring axially displaceable and the rolling elements run on the inner ring with little axial play between two axial Borden. Floating bearings are therefore not intended to absorb axial forces. In cylindrical roller bearings of the type, for example, only one of the bearing rings, either the inner ring or the outer ring, on both sides on axial edges. The other bearing ring, either the inner ring or the outer ring is cylindrical without ribs.

Axial rims are side edges that protrude radially outwardly beyond the roller raceway of the inner ring on the inner ring from the rotational axis of the roller bearing, with one side edge axially adjoining the roller raceway and one lateral edge laterally right on the roller raceway. Axial rims on the outer ring are radially inwardly in the direction of the rotational axis of the rolling bearing beyond the roller race of the outer ring protruding side edges, of which one side edge axially to the left side of the roller track and a side edge to the right side of the roller track. The shelves are either one-piece-einmaterialig formed with the respective bearing ring or arranged separately from the respective bearing ring. There are also bearing rings, inner rings or outer rings, each having only one board. Furthermore, there are also bearing rings on which a board one-piece one-material and the other is designed as a separate component.

The material of the outer ring is bearing steel, which is preferably suitable for curing.

Alternative hardening methods are all conceivable hardening methods for steel, preferably through hardening, surface hardening etc ..

The width of each Bordes should not fall below 1.5 mm on the outer ring of the cylindrical roller bearing according to the invention.

• - Das Verhältnis der Rollenlänge der Zylinderrollen zu deren Rollendurchmesser ist kleiner oder gleich dem Zahlenwert 3. Die Breite des Außenrings bzw. des Ringkörpers entspricht dem axialen Abstand zwischen den Borden zuzüglich der axialen Breiten der Borde. Die Breite von wenigstens einem der Borde, vorzugsweise beider Borde, aber eines jeden für sich, ist kleiner oder gleich 11 % der Breite B des Außenrings. Die Borde sind demnach im Vergleich zum Stand der Technik sehr schmal, was sich positiv auf den Materialverbrauch bei der Herstellung des Lagers und auf dessen Gewicht auswirkt. Die symmetrische Ausbildung von Borden gleicher Breite vereinfacht die Fertigung und vermeidet den Zwang orientierter Montage. Gleiche axiale Lagerbreite vorausgesetzt, kann deshalb mehr Kapazität der Lagerbreite vorteilhaft für höhere Tragzahlen des Zylinderrollenlagers genutzt werden.
• - Eine Ausgestaltung der Erfindung sieht vor, dass ein Verhältnis des Rollendurchmessers der Zylinderrollen dem Fünffachen der radialen Höhe des Ringkörpers entspricht oder weniger als das Fünffache ist. Die radiale Höhe ist also die senkrecht zur Rotationsachse gemessener Höhe. Der Außenring des Zylinderrollenlagers ist vergleichsweise zur Rollenhülse massiv ausgebildet, d. h., er weist eine relativ große radiale Bauhöhe zwischen der Innenlaufbahn und seinem außenzylindrischen Sitz auf und hat deshalb hohe Tragfähigkeiten.
• - Eine weitere Ausgestaltung der Erfindung sieht vor, dass die radiale Höhe der Borde des Außenrings, gemessen auf Höhe der Innenlaufbahn, bis zu den der Rotationsachse zugewandten innenzylindrischen Flächen der Borde kleiner als 16 % - 23%, vorzugsweise 20% des Rollendurchmessers der Zylinderrollen ist. Damit ist die radiale Höhe hinsichtlich des Verhaltens beim Härten und funktionsbedingt optimal der geringen Breite der Borde angepasst. Die Borde sind demnach im Vergleich zum Stand der Technik radial relativ niedrig, was sich positiv auf den Materialverbrauch bei der Herstellung des Lagers und auf dessen Gewicht auswirkt.
• - Der vorgenannte Vorteil greift auch, wenn gemäß einem weiteren unabhängigen Anspruch für ein gattungsgemäßes Zylinderrollenlager mit beliebigem Verhältnis von Breite der Borde zur Breite des Außenrings, jedoch mit einem Verhältnis der Rollenlänge zum Rollendurchmesser kleiner oder gleich dem Zahlenwert 3, die Bordhöhe vorzugsweise kleiner als 16 % des Rollendurchmessers der Zylinderrollen ist.
• - Der vorgenannte Vorteil greift auch, wenn gemäß einem weiteren unabhängigen Anspruch für ein gattungsgemäßes Zylinderrollenlager mit beliebigem Verhältnis von Breite der Borde zur Breite des Außenrings sowie beliebigen Verhältnis von Rollenlänge zu Rollendurchmesser, jedoch einschließlich eines Verhältnisses vom Rollendurchmesser zur Höhe des Ringkörpers größer oder gleich dem Zahlenwert 5 ist. Die Höhe des Ringkörpers ist dabei der radiale Abstand am Lagerring zwischen dem Lagersitz und der Wälzlaufbahn, also die radiale Dicke des Lagerrings ohne Borde. Zugleich ist gemäß Definition dieses unabhängigen Anspruchs die radiale Bordhöhe beider gleichhohen Borde kleiner als 16 % des Rollendurchmessers DR der Zylinderrollen. Die Bordhöhe wird beginnend auf Höhe der innenzylindrischen Fläche der Innenlaufbahn bis hin zu den Abschlüssen der in Richtung Rotationsachse ragenden freien Enden der Borde gemessen.
• - Der vorgenannte Vorteil greift auch, wenn gemäß einem weiteren unabhängigen Anspruch für ein gattungsgemäßes Zylinderrollenlager mit beliebigem Verhältnis von Breite der Borde zur Breite des Außenrings sowie beliebigem Verhältnis von Rollenlänge zu Rollendurchmesser, jedoch einschließlich eines Verhältnisses vom Rollendurchmesser zur Höhe des Ringkörpers, größer oder gleich dem Zahlenwert 5 ist. Die Höhe des Ringkörpers ist dabei der radiale Abstand am Lagerring zwischen dem Lagersitz und der Wälzlaufbahn, also die radiale Dicke des Lagerrings ohne Borde. Zugleich ist gemäß Definition dieses unabhängigen Anspruchs die Breite von wenigstens einem der Borde, vorzugsweise jeweils bei beiden (aber dabei von jedem für sich), kleiner oder gleich 11 % der Breite des Außenrings. Die Breite des Außenrings ist dabei die Summe aus dem axialen Abstand zwischen den Borden, der Breite des ersten Bordes und der Breite des zweiten Bordes.
• - Die Anwendung eines erfindungsgemäßen Zylinderrollenlagers als Loslager in einer Loslagerstelle zur Lagerung einer Getriebewelle eines Fahrzeuggetriebes ist vorgesehen. Bei den Getriebebauern oder Fahrzeugherstellern wird in der Regel um jeden Millimeter an Bauraumersparnis gekämpft. Dies zum einen, weil der generell zur Verfügung stehende Bauraum begrenzt ist und die Funktionalität der Getriebe sich jedoch zunehmend erhöht. Letzteres kann bedeuten, dass mehr oder belastbarer dimensionierte Bauteile im Getriebeinneren angeordnet werden müssen, obwohl nicht mehr Bauraum zur Verfügung steht. Ein vergleichsweise schmaleres Zylinderrollenlager als das herkömmliche oder ein gleich breites Zylinderrollenlager wie das herkömmliche jedoch mit höheren Tragzahlen bietet dementsprechend Vorteile. Zum anderen kann jeder Gramm Materialeinsparung an einem Einzelteil in der Gesamtsumme von vielen Bauteilen zur Einsparungen am Gewicht des Getriebes und dementsprechend zu Verbrauchseinsparungen am Gesamtfahrzeug beitragen.

The invention for both cylindrical rollers and Wälzlaufbahnen the outer or inner ring with cylindrical treads and / or spherical treads. According to the invention, optionally or simultaneously:

• - The ratio of the roller length of the cylindrical rollers to their roller diameter is less than or equal to the numerical value 3 , The width of the outer ring or of the annular body corresponds to the axial distance between the shelves plus the axial widths of the shelves. The width of at least one of the shelves, preferably both shelves, but each individually is less than or equal to 11% of the width B of the outer ring. The shelves are therefore very narrow in comparison to the prior art, which has a positive effect on the material consumption in the production of the bearing and on its weight. The symmetrical design of Borden same width simplifies the production and avoids the constraint oriented assembly. Assuming the same axial bearing width, therefore, more capacity of the bearing width can be advantageously used for higher load ratings of the cylindrical roller bearing.
• - An embodiment of the invention provides that a ratio of the roll diameter of the cylindrical rollers is five times the radial height of the ring body or less than is five times. The radial height is thus the height measured perpendicular to the axis of rotation. The outer ring of the cylindrical roller bearing is formed comparatively to the roller sleeve solid, ie, it has a relatively large radial height between the inner race and its outer cylindrical seat and therefore has high load capacities.
• - Another embodiment of the invention provides that the radial height of the rims of the outer ring, measured at the level of the inner race, to the axis of rotation facing inner cylindrical surfaces of the rims is less than 16% - 23%, preferably 20% of the roller diameter of the cylindrical rollers , Thus, the radial height in terms of behavior during curing and functionally optimally adapted to the small width of the shelves. The shelves are therefore radially relatively low in comparison to the prior art, which has a positive effect on the material consumption in the production of the bearing and on its weight.
• - The above advantage also applies when according to another independent claim for a generic cylindrical roller bearing with any ratio of width of the ribs to the width of the outer ring, but with a ratio of the roll length to the roll diameter is less than or equal to the numerical value 3 , the board height is preferably less than 16% of the roller diameter of the cylindrical rollers.
• - The above advantage also applies when according to another independent claim for a generic cylindrical roller bearing with any ratio of width of the ribs to the width of the outer ring and any ratio of roll length to roll diameter, but including a ratio of the roll diameter to the height of the ring body greater than or equal to value 5 is. The height of the annular body is the radial distance on the bearing ring between the bearing seat and the Wälzlaufbahn, so the radial thickness of the bearing ring without ribs. At the same time, according to the definition of this independent claim, the radial crown height of both equal high rims is less than 16% of the roll diameter DR the cylindrical rollers. The height of the board is measured starting at the level of the inner cylindrical surface of the inner raceway up to the ends of the free ends of the rims protruding in the direction of the axis of rotation.
• - The above advantage also applies when according to another independent claim for a generic cylindrical roller bearing with any ratio of width of the ribs to the width of the outer ring and any ratio of roll length to roll diameter, but including a ratio of the roll diameter to the height of the ring body, greater than or equal the numerical value 5 is. The height of the annular body is the radial distance on the bearing ring between the bearing seat and the Wälzlaufbahn, so the radial thickness of the bearing ring without ribs. At the same time, according to the definition of this independent claim, the width of at least one of the shelves, preferably both (but each by itself), is less than or equal to 11% of the width of the outer ring. The width of the outer ring is the sum of the axial distance between the Borden, the width of the first Bordes and the width of the second Bordes.
• - The application of a cylindrical roller bearing according to the invention as a floating bearing in a floating bearing for supporting a transmission shaft of a vehicle transmission is provided. In the case of gear manufacturers or vehicle manufacturers, it is usually fought for every millimeter of space savings. On the one hand, because the generally available space is limited and the functionality of the transmission, however, increasingly increased. The latter may mean that more or more resilient dimensioned components must be arranged inside the gear, although not more space is available. A comparatively narrower cylindrical roller bearing than the conventional or an equally wide cylindrical roller bearing as the conventional but with higher load ratings accordingly offers advantages. On the other hand, each gram of material saved on a single part in the total of many components can contribute to the weight reduction of the transmission and consequently to fuel savings on the overall vehicle.

• - Axial ist mit der Rotationsachse des Wälzlagers gleichgerichtet.
• - Radial ist quer zur Rotationsachse des Wälzlagers ausgerichtet.
• - Die Innenlaufbahn muss nicht direkt axial mit den Borden abschließen. Vorzugsweise sind links und rechts neben der Innenlaufbahn radiale Freistiche in dem Ringkörper zwischen der Innenlaufbahn und dem jeweiligen Bord ausgebildet. Als Breite der Innenlaufbahn gilt trotzdem der axiale Abstand zwischen den Borden.
• - Die radiale Höhe des Außenrings wird jedoch von der Innenlaufbahn aus zur außenzylindrischen Fläche des Außenrings gemessen.

General definitions defining the subject of the invention are:

• - Axial is rectified with the axis of rotation of the bearing.
• - Radial is aligned transversely to the axis of rotation of the bearing.
• - The inner raceway does not have to lock directly axially with the ribs. Radial undercuts in the annular body between the inner race and the respective board are preferably formed left and right next to the inner raceway. The width of the inner race still applies the axial distance between the Borden.
• However, the radial height of the outer ring is measured from the inner raceway to the outer cylindrical surface of the outer ring.

list of figures

• 1 zeigt einen Teilschnitt durch ein erfindungsgemäßes Zylinderrollenlager 1.
• 2 zeigt schematisch eine Fest-Loslageranordnung 15, in der eine Getriebewelle 16 mit einem Festlager 17 und einem Loslager 18 gelagert ist.
• 3 zeigt eine alternative Ausbildung des Loslagers 18 aus der Fest-Loslageranordnung 15 nach 2.

The invention will be explained in more detail with reference to an embodiment.

• 1 shows a partial section through an inventive cylindrical roller bearing 1 ,
• 2 schematically shows a fixed-bearing arrangement 15 in which a transmission shaft 16 with a fixed camp 17 and a floating warehouse 18 is stored.
• 3 shows an alternative embodiment of the floating bearing 18 from the fixed-floating bearing arrangement 15 to 2 ,

1 - The cylindrical roller bearing 1 has an outer ring 3 , Cylindrical rollers 2 and an inner ring 22 on. From the partial section is only a cylindrical roller 2 figuratively, however, are in the cylindrical roller bearing 1 circumferentially of the inner ring 22 several of the cylindrical rollers 2 in a cage 23 guided. The cylindrical rollers 2 are radially between an inner raceway 6 of the outer ring 3 and an outer career 19 of the inner ring 22 in the cage 23 guided. Radial is transverse to the central axis 24 the cylindrical roller 2 , that is, the central axis 24 is axially aligned in the longitudinal direction.

The cylindrical rollers 2 show the length L and the roll diameter DR on. The outer ring 3 is from a ring body 4 formed, one by an axial width B and a radial height H having described cross-section. The ring body 4 is outside with an outside cylindrical surface 11 with an outer diameter THERE Mistake. The inner raceway 6 in the case shown is an inner cylindrical surface 12 with a first inner diameter DI , The outer ring 3 is one-piece-single-material with a first board 7 as well as a second board 8th Mistake. The shelves 7 and 8th are radially inward toward the inner ring 22 from the ring body 4 protrude and protrude in the radial direction with a board height bra radially perpendicular over the inner raceway 6 out and are axial with a distance A spaced apart. The axially directed roll length L the respective cylindrical roller 2 almost equal to the distance A the shelves 7 and 8th , but the respective cylindrical roller 2 with an axial play S between the shelves 7 and 8th tightly guided. The axial clearance S between the cylindrical roller 2 and the board 7 and or 8th is very small and is therefore considered as a distance in 1 not reproducible. The relationship to the distance A is, however, illustrated by the sum A = L + S. The width of the inner raceway 6 is simplified and therefore irrelevant any undercuts as the distance A considered. The distance A So is as an axial distance between the facing surfaces 13 and 14 the shelves 7 and 8th Are defined.

The cage 23 is out of page margins 25 and longitudinal webs 26 formed between which the cylindrical rollers 2 are arranged. The width BK of the margin 25 of the cage is smaller, equal to or greater than the width BB1 or BB2 of the respective board 7 or 8th , but preferably smaller than the respective width BB1 or BB2 ,

The ratio of roll length L of the cylindrical rollers 2 to the roll diameter DR is less than or equal to the numerical value 3 , The width B of the outer ring 3 or the ring body 4 corresponds to the distance A between the shelves 7 and 8th plus the widths BB1 and BB2 the shelves 7 and 8th : B = A + BB1 + BB2.

The width BB1 . BB2 from at least one of the shelves 7 or 8th , preferably both shelves (ie, each by itself) is less than or equal to 11% of the width B of the outer ring. The ratio of roll diameter DR the cylindrical rollers 2 to the radial height H of the ring body 4 is five times or less than five times that. The outer ring 3 of the cylindrical roller bearing 1 is formed comparatively to the roller sleeve solid, ie, has a relatively large radial height H on. The radial height bra the shelves 7 and 8th , measured at the height of the inner race up to that of the 1 not apparent rotation axis 5 (please refer 2 ) facing inner cylindrical surfaces 9 and 10 the shelves 7 and 8th less than 16% - 23%, preferably 21% of the roll diameter DR the cylindrical rollers 2 is.

The radial height bra the shelves 7 and 8th , measured starting at the height of the inner race 6 up to the axis of rotation 5 (the transmission shaft 16 or the cylindrical roller bearing 1 (see. 2 ) facing inner cylindrical surfaces 9 and 10 the shelves 7 and 8th , is less than 16% of the roll diameter DR the cylindrical rollers 2 , The board height bra is preferably less than 12% of the roll diameter DR the cylindrical rollers 2 , The radial height of the board bra both equal high rims 7 and 8th Total is less than 16% of the roll diameter DR the cylindrical rollers. 4. The ratio of the roll diameter DR to the height H of the ring body 4 , between the cylindrical surfaces 11 and 12 measured vertically, is greater than or equal to the numerical value 5 ,

2 shows schematically an application of a cylindrical roller bearing according to the invention 1 as a floating warehouse 18 in the fixed-load bearing arrangement 15 for rotating mounting of the gear shaft 16 around a rotation axis 5 in an otherwise not shown vehicle transmission. The rotation axis 5 of the cylindrical roller bearing 1 corresponds to the gear shaft 16 , The transmission shaft 16 is at a fixed deposit 27 and at the loose depository 28 rotatable about its axis of rotation in a gear housing, not shown 29 stored. The function of the movable bearing 18 results from the structural features of the cylindrical roller bearing 1 , The outer ring 3 sits firmly in the gearbox 29 , The cylindrical rollers 2 are axially tight between the shelves 7 and 8th and thus with respect to the transmission housing 29 conducted in a "fixed storage function". The outer raceway 19 of the cylindrical roller bearing 1 is directly at the gear shaft 16 trained and laterally not limited by stops. This results in the "movable bearing function" in the form of an "interface" at which the transmission shaft 16 opposite the cylindrical rollers 2 is freely movable axially. At the fixed deposit, one or more arbitrary as a fixed bearing 17 functioning rolling bearings be installed. The transmission shaft 16 is at the fixed deposit 27 axially supported, but at the loose bearing point 18 with the shaft section 20 opposite the cylindrical rollers 2 and thus with respect to the transmission housing 29 movable.

3 - In the with 3 The arrangement shown has the floating bearing point 28 an inner ring 22 of the cylindrical roller bearing 1 on. The inner ring 22 sits firmly on a shaft section 20 and secures the "floating bearing function". That's the outer track 19 of the inner ring 22 Left and right sides free of attacks, ie, the inner ring 22 is without shelves. The function of the floating bearing is analogous to that with 2 illustrated arrangement of the structural features of the cylindrical roller bearing 1 , The outer ring 3 sits firmly in the gearbox 29 , The cylindrical rollers 2 are axially tight between the shelves 7 and 8th in a "fixed bearing function" and thus axially immovable relative to the housing 29 guided. The transmission shaft 16 on the other hand is at the non-locating point at an interface between the outer raceway 19 of the inner ring 22 and the cylindrical rollers 22 opposite the gearbox 29 axially displaceable.

LIST OF REFERENCE NUMBERS

1

Cylindrical roller bearings

2

cylindrical rollers

3

outer ring

4

ring body

5

Rotation axis of the cylindrical roller bearing 1

6

Inner raceway

7

first board

8th

second board

9

inside cylindrical surface of the board 7

10

inside cylindrical surface of the board 8th

11

Outer cylindrical surface of the ring body 4

12

Inner cylindrical surface of the inner raceway 6

13

Area of the board 7

14

Area of the board 8th

15

Fixed-Floating-bearing

16

gear shaft

17

fixed bearing

18

movable bearing

19

Outer race

20

shaft section

21

not used

22

inner ring

23

Cage

24

central axis

25

margin

26

longitudinal web

27

Fixed bearing point

28

floating bearing

29

gearbox

A

axial distance between the surfaces 13 and 14

B

Width of the ring body 4

BB1

axial width of the first board 7

BB2

axial width of the second board 8th

bra

Height of the shelves 7 and 8th

THERE

Outer diameter of the outer cylindrical surface 11

DI

Inner diameter of the inner cylindrical surface 12

DR

Roll diameter of the cylindrical rollers 2

H

Height of the ring body 4

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

• DE 102006031048 A1 [0002]
• DE 19814309 C1 [0002]

Claims (9)

Cylindrical roller bearing (1) with cylindrical rollers (2) and with an outer ring (3), wherein - The cylindrical rollers (2) are provided with a length (L) and a roll diameter (DR), - The outer ring (3) has an annular body (4) having a by an axial width (B) and a radial height (H) certain cross-section - The annular body (4) has on the outside an outer cylindrical surface (11) with an outer diameter (DA), - The outer ring (3) is provided with an inner raceway (6), the inner race (6) has a first inner cylindrical surface (12) with a first inner diameter (DI), - The track (6) is turned radially inwardly to an axially oriented axis of rotation (5) of the cylindrical roller bearing (1), - The outer ring (3) is provided in one piece-einmaterialig with a first board (7) and a second board (8), - The rims (7, 8) radially in the direction of the axis of rotation (5) from the annular body (4) protrude beyond the inner raceway (6) in the radial direction with a board height (BH) radially perpendicular to the rotation axis (5) directed out . the inner raceway (6) is formed axially between the ribs (7, 8) spaced apart from one another at a distance (A), - The width (B) of the outer ring is the sum of the axial distance (A) between the Borden (7, 8), the width (BB1) of the first board 7 and the width (BB2) of the second board (8), wherein a first ratio (L: DR) of roll length (L) to roll diameter (DR) is less than or equal to the numerical value 3, and wherein the width (BB1, BB2) of at least one of the shelves (7, 8) is less than or equal to 11 % of the width (B) of the outer ring (3). Cylindrical roller bearings after Claim 1 , characterized in that a second ratio (DR: H) of the roll diameter (DR) to the height H between the cylindrical surfaces (11, 12) is less than or equal to the numerical value 5. Cylindrical roller bearings after Claim 1 , characterized in that the rims (7, 8) are the same width (BB1 = BB2). Cylindrical roller bearings after Claim 1 , characterized in that the board height (BH) is less than 16% of the roll diameter (DR). Cylindrical roller bearing (1) with cylindrical rollers (2) and with an outer ring (3), wherein - the cylindrical rollers (2) are provided with a length (L) and a roller diameter (DR), - a first ratio (L: DR) of roller length (L) to the roll diameter (DR) ≤ the numerical value 3, - the outer ring (3) has an annular body (4), - the annular body (4) has on the outside an outer cylindrical surface (11) with an outer diameter (DA), - Outer race (3) is provided with an inner race (6), - the inner race (6) has a first inner cylindrical surface (12) with a first inner diameter (DI), - the raceway (6) radially inwardly to an axially oriented rotational axis ( 5) of the cylindrical roller bearing (1), - the outer ring (3) is provided in one piece with a first board (7) and a second board (8), - the ribs (7, 8) radially in the direction of the axis of rotation ( 5) from the ring body (4) protrude and thereby over the raceway (6) in radial direction with a board height (BH) directed radially perpendicular to the axis of rotation 5 project beyond, characterized in that the board height (BH) is less than 16% of the roll diameter (DR). Cylindrical roller bearings after Claim 5 , characterized in that the board height (BH) is less than or equal to 12% of the roll diameter (DR). Cylindrical roller bearing (1) with cylindrical rollers (2) and with an outer ring (3), wherein - the cylindrical rollers (2) are provided with a roller diameter (DR), - the outer ring (3) has a ring body (4) with one by an axial width (B) and a height (H) has certain cross-section, - the ring body (4) on the outside has an outer cylindrical surface (11) with an outer diameter (DA), - the outer ring (3) is provided with an inner raceway (6), the inner race (6) is turned radially inwards towards an axially aligned rotational axis (5) of the cylindrical roller bearing (1), - the inner race (6) has a first inner cylindrical surface (12) with a first inner diameter (DI), - the height ( H) of the annular body (4) is aligned perpendicular to the axis of rotation (5) between the first inner cylindrical surface (12) and the outer cylindrical surface (11), - a ratio (DR: H) of the roll diameter (DR) to the height (H) between the cylindrical surfaces (11, 12) is greater than or equal to the numerical value 5. - The outer ring (3) in one piece-einmaterialig with a first board (7) and a second board (8) is provided, - the ribs (7, 8) protrude radially outward from the annular body (4) in the direction of the axis of rotation (5) and extend beyond the inner race (6) in the radial direction with a flange height (BH) directed radially perpendicular to the axis of rotation (5), characterized in that the board height (BH) is less than 16% of the roll diameter (DZ). Cylindrical roller bearing (1) with cylindrical rollers (2) and with an outer ring (3), wherein - the cylindrical rollers (2) are provided with a roller diameter (DR), - the outer ring (3) has a ring body (4) with one by an axial width (B) and a height (H) has certain cross-section, - the ring body (4) on the outside has an outer cylindrical surface (11) with an outer diameter (DA), - the outer ring (3) is provided with an inner raceway (6), the inner race (6) is turned radially inwards towards an axially aligned rotational axis (5) of the cylindrical roller bearing (1), - the inner race (6) has a first inner cylindrical surface (12) with a first inner diameter (DI), - the height ( H) of the annular body (4) is aligned perpendicular to the axis of rotation (5) between the first inner cylindrical surface (12) and the outer cylindrical surface (11), - a ratio (DR: H) of the roll diameter (DR) to the height (H) between the cylindrical surfaces (11, 12) ≥ 5. - The outer ring (3) one-piece-einmaterialig with a first board (7) and a second board (8) is provided, - the rims (7, 8) radially in the direction of the axis of rotation (5) from the ring body (4) protrude and thereby protrude beyond the inner race (6) in the radial direction with a board height (BH) directed radially perpendicular to the axis of rotation (5), - the width (B) of the outer ring is the sum of the axial distance (A) between the ribs (7, 8), the width (BB1) of the first board 7 and the width (BB2) of the second board (8). characterized in that the width (BB1, BB2) of at least one of the shelves (7, 8) is less than or equal to 11% of the width (B) of the outer ring (3). Fixed-floating bearing arrangement (15) of a gear shaft (16) with a fixed bearing (17) through which the gear shaft (16) on one side radially opposite a gear housing (17) is mounted, and with a designed as a cylindrical roller bearing (1) floating bearing (18 ) after one of the Claims 1 - 8th wherein the cylindrical roller bearing (1) optionally has an outer raceway (19) formed on an inner ring (18) or directly on a shaft portion (20) of the transmission shaft (16), neither the inner ring (18) nor the shaft portion (20) formed outer raceway (19) is formed between Borden and wherein the cylindrical rollers (2) relative to the outer raceway (19) or the shaft portion (20) or the transmission shaft (16) with the inner ring (18) and / or the outer raceway (19) opposite the cylindrical rollers (2) is displaceable.

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