WO2018184631A1

WO2018184631A1 - Roller

Info

Publication number: WO2018184631A1
Application number: PCT/DE2018/100296
Authority: WO
Inventors: Roger Remmel
Original assignee: European Trailer Systems Gmbh
Priority date: 2017-04-07
Filing date: 2018-04-03
Publication date: 2018-10-11
Also published as: DE202017102103U1

Abstract

The invention relates to a roller, in particular a support roller, for a carriage of a convertible top frame for a tarpaulin structure, comprising two ball bearing rings (304, 305) having balls (304a, 305a), at least one inner bearing shell (302, 303) and an outer bearing shell (301), which is assigned to both ball bearing rings (304, 305), each of which is arranged concentrically about a roller axis (309) forming a rolling bearing. The outer bearing shell (301) comprises a central circumferential surface (311) for the radial support on a guide. The at least one inner bearing shell (302, 303) comprises a first inner bearing shell (302) and a second inner bearing shell (303). According to the invention, a roller for a carriage of a convertible top frame for a tarpaulin structure, which can reliably transmit forces in a direction that is perpendicular to the plane of extent of the roller, is attained such that the first inner bearing shell (302) has an axial appendage, which passes through a through-hole (303i) of the second inner bearing shell (303).

Description

role

The invention relates to a roller, in particular a support roller, for a

Carriage of a hood frame for a tarpaulin structure, comprising two ball bearing rings with balls, at least one inner bearing shell and an outer bearing shell, which is associated with two ball bearing rings. From practice, support rollers are known which have a double-row ball bearings, in which therefore two ball bearing rings with balls of at least one inner bearing shell and an outer bearing shell, the two

Ball bearing rings is assigned, are provided. The ball bearing rings, at least one inner bearing shell and an outer bearing shell are each arranged concentrically about a roller axis and together form a roller bearing, wherein the at least one inner bearing shell has a cylindrical receptacle for a connecting member such as a screw or the like, wherein the outer bearing shell has a central peripheral surface for radial support on a guide comprises. If the guide is not formed as a flat guideway, it is necessary to press a complementary profile to the circumferential profile on the outer bearing shell, which is supported not only on the outer circumference of the outer bearing shell, but also on the two end faces of the outer bearing shell. The resulting roll is quite thick and therefore requires a fairly large distance of the guide from a part with respect to which the roll is to be movable. In the known roles also so-called deep groove ball bearings are used, which transmit forces substantially in the plane of the role, but can not transmit more than about 5% of the transmitted in the vertical plane of the roller forces in the perpendicular axial direction of the roller axis. Thus, such roles can indeed use as support rollers, but if even lateral forces are to be transmitted, the load limit of the known roles is quickly exceeded. DE 20 2013 005 565 U1 describes a tarpaulin suspension device to which a support roller is screwed or riveted, wherein a ball bearing ring adapted to a flat track outer bearing shell coupled to an inner bearing shell in the manner of a rolling bearing, wherein the inner bearing shell on the front side of the outer bearing shell may be extended to form a spacer member. This is a pen with a

Threaded through a screw inserted on the opposite side of the inner bearing shell on a base plate of

Tarpaulin hanger set. A disadvantage of the known

Tarpaulin suspension device is that the rollers can hardly transmit forces in a direction perpendicular to the roller plane.

20 2015 006 044 U1 describes a roller for connection to a tarpaulin suspension device, in which the role of a rolling bearing has an outer bearing shell and an inner bearing shell, wherein the inner bearing shell axially overhanging the outer bearing shell

Hollow cylinder portion which is provided with an internal thread, wherein a screw bolt is screwed into the internal thread to connect the roller to a plate body.

DE 20 2014 006 133 U1 describes a roller, in particular a support roller, for a carriage of a top frame for a tarpaulin structure, comprising two inner bearing shells and an outer bearing shell, which are each arranged concentrically about a roller axis and form a roller bearing, wherein both inner bearing shells a have aligned cylindrical receptacle for a separate link. A disadvantage of the known role is that the role and the link must be prepared, delivered and assembled as separate parts, so that the manipulation is complex and error-prone.

It is the object of the invention to provide a roller, in particular a support roller, for a carriage of a top frame for a tarpaulin structure, the forces in a direction perpendicular to the plane of extension of the roller can transmit reliably.

This object is achieved by a roller with the features of the independent claim.

According to one aspect of the invention, a roller is provided, in particular a carrying roller, e.g. for a sleigh of a top frame for a

A tarpaulin structure, comprising two ball bearing rings with balls, at least one inner bearing shell, and an outer bearing shell, which is associated with two ball bearing rings, which are each arranged concentrically around a roller axis and form a rolling bearing, wherein the outer bearing shell has a central

Peripheral surface for radial support comprises on a guide, wherein the at least one inner bearing shell comprises a first inner bearing shell and a second inner bearing shell. Here, the first inner bearing shell on an axial extension, which is an opening of the second inner

Lagerschale interspersed. As a result, it is advantageously possible to axially insert the two inner bearing shells into the outer bearing shell from opposite directions, and at the same time to form the at least one inner bearing shell comprising the first inner bearing shell and the second inner bearing shell such that they are simply attached to a plate body of a slide of the convertible top frame is connectable.

Preferably, the opening of the second inner bearing shell is formed as a hollow cylinder, so that the extension of the first inner

Bearing shell can be easily passed through the opening. In this case, with a corresponding running clearance, the first inner bearing shell can rotate against the second inner bearing shell, but this is not absolutely necessary if the at least one inner bearing shell contacts the plate body

is screwed and thus fixed with respect to this fixed.

According to a preferred embodiment it is provided that the second inner bearing shell with its opening form-fitting manner to the first inner bearing shell and in particular to the outer periphery of the Extension is connected. A positive connection can be realized, for example, by an entering into the opening

Projection of the second inner bearing shell penetrates into a corresponding groove of the first inner bearing shell and prevents twisting.

Alternatively, the inner circumference of the second inner bearing shell can also be polygonal or designed in the manner of a Torx and grip the corresponding circumference of the extension in such a form-fitting manner. Preferably, however, it is provided that the second inner bearing shell frictionally against the first inner bearing shell and here on the outer circumference of the extension

is connected, for example by a defined interference fit, which prevents the second inner bearing shell from the first inner

Laying bowl slides off. It is particularly expedient that

positive and non-positive connection can be combined. According to a preferred embodiment, it is provided that the axial extension of the first inner bearing shell axially over the second inner

Bearing shell protrudes. This makes it possible in particular that the

Connection of the role, for example, with a plate body of a carriage of the top frame, takes place directly over the first inner bearing shell, so that set only small tolerances. In this case, the preferred

Extension used in a bore of a plate body of a carriage, which has a matching inner circumference, so that a very low-tolerance connection takes place. Conveniently, the axial extension of the first inner bearing shell has a bore which is equipped with an internal thread. This makes it possible to screw an externally threaded screw through the plate body of the carriage of the top frame into the extension, so that the roller at a defined distance from the plate is connected thereto. As a result, the rollers can be replaced in a simple manner, for example if they are worn or broken

have become unusable. Furthermore, transfers both the extension and the screw shocks on the plate body, so that the role very robust against attacking loads.

Conveniently, the first inner bearing shell on a prismatic approach to a tool with which the roller or the first inner bearing shell can be held when a screw in the

Thread is screwed, so that it is advantageously avoided that the first inner bearing shell rotates and it comes with it to loss of time. The prismatic approach for a tool is expediently provided on that end face of the first inner bearing shell, which faces the thread or the extension.

The second inner bearing shell is expediently axially over the end face of the outer bearing shell, so that it is not aligned with a thickness of about one millimeter with the outer bearing shell. The annular end face of the supernatant advantageously serves as a contact surface for a

Plate body of a carriage to which the roller is connected. On the one hand, such a defined, very small distance from the roll to the

Plate body created that allows a narrow slide. On the other hand, the second inner bearing shell is then clamped axially when screwing a connecting means such as a screw in the internal thread of the first inner bearing shell against the first inner bearing shell, so that sliding apart of the two inner bearing shells is avoided. Alternatively, it is possible if the outwardly facing end face of the inner

Bearing shell aligned with the front side of the outer bearing shell, this purpose to use a separate lower ring, however, increases the number of parts and also represents a greater installation effort.

According to a favorable embodiment, it is provided that the projection of the axial extension of the first inner bearing shell via the second inner bearing shell corresponds approximately to the diameter of a ball of the ball bearing ring. This makes it possible to achieve a particularly compact design of the roller, which is at a small distance from the plate to which they

connected, can roll. Conveniently, the axial Supernatant of the appendix not more than 6 mm, which is the thickness of the

Plate body or the height of the bore in the plate body corresponds. Preferably, however, the extension passes through more than half the thickness of the plate body and thus more than 3 mm. Particularly preferred is an axial supernatant of about 4 mm to 5 mm, preferably about 4.75 mm.

Appropriately, the first inner bearing shell has a through hole, which is one ends formed as a prismatic approach for a tool and other ends as internal threads. The production of the first inner bearing shell with a through hole facilitates the

Processing of the first inner bearing shell. Alternatively, a middle region between the attachment and the internal thread can remain closed by material of the first inner bearing shell, which advantageously prevents dust and / or moisture from entering the region of the internal thread from the outside.

Conveniently, the internal thread in the first inner bearing ring is longer than the axial projection of the extension, so that a screwed connection means can also fill the area surrounded by the second inner bearing ring portion of the internal thread. Preferably, the length of the internal thread is more than 1.5 times the axial projection of the extension, and more preferably more than 2 times.

The bearing shells are expediently made of steel, furthermore, the approximately 13 balls are also made of steel, so that the role is designed to be very durable overall.

Preferably, it is provided that the bearing shells support the balls of each of the two ball bearing rings obliquely in the manner of an angular contact ball bearing. As a result, a roll is advantageously created, in which on the outer

Bearing shell acting axial forces, that is, having a component in the direction of the roller axis, on the balls of the two

Ball bearing rings can each be introduced into the at least one inner bearing shell, without the role is destroyed here. By selection an oblique support in the manner of an angular contact ball bearing is compared with a conventional deep groove ball bearing effective in the axial direction absorption of forces at least doubled, preferably tripled or quadrupled. Thus, the role is not only used as a supporting role, but also can still allow a guide in the direction of the roller axis, especially if the role as stated above with

Flange sections is formed.

Expediently, the balls of both ball bearing rings are in each case of a rounded circumferential track region on an extension of the inner side of the outer bearing shell and the outer side of the at least one inner

Supported bearing shell. As a result, a transmission of forces on the balls of the ball bearing ring is not only possible in the plane of the ball bearing ring, but also with a component perpendicular thereto, since the corresponding forces are introduced or absorbed by the rounded circumferential track areas.

Appropriately, in this case are pointing to the roller axis

Projecting the inside of the outer bearing shell circumferential track areas provided for balls of both ball bearing rings, so that both ball rings can be supported on an extension.

According to a favorable aspect, the outer bearing shell has the central peripheral surface axially surrounding flange portions, which are radially further spaced from the roller axis than the central peripheral surface. This role makes it possible to unroll with the central peripheral surface not only on a flat guideway, for example the narrow side of a rectangular cross-section flat iron, but also with the central peripheral surface axially surrounding flange portions which are provided on both sides of the central peripheral surface circumferentially, the Guideway to center between them and thus slipping in the direction of

To avoid roll axis. The flange areas thus advantageously grasp the part having the guideway and thus limit the play with which the central peripheral surface with respect to the guide track in the direction of the roller axis can go back and forth. Thus, the role is at the same time to its essential task, namely the vertical introduction of forces as

Carrying roller, a guide element with respect to the guideway, along which the roller is displaced. The role here is narrow construction and has a favorable ratio of roll height to roll width, so that considerable forces can be introduced into the roll on the ball bearing rings, without the roller at the same time a large distance of the guideway of the container, along which the role displaced is required.

Preferably, the flange portions have mutually remote end faces, which are each aligned with one of the end faces of the outer bearing shell. The end faces of the outer bearing shell are in this case arranged in planes perpendicular to the roller axis, and the mutually averted end faces of the flange extend the end faces of the outer bearing shells.

In this way, it is advantageously achieved that the flange regions, which extend the outer bearing shell in the direction of the plane of the roller, do not protrude in the axial direction of the roller axle beyond the end faces of the outer bearing shells, so that a small-sized roller is achieved.

The flange areas expediently face each other

End faces, which may lie in mutually parallel planes, so that the central peripheral surface through the mutually facing end faces of the

Flange areas is sharply limited. However, particularly preferred is a configuration in which the mutually facing end faces of

Flange areas have an angle to a plane perpendicular to the roller axis, which expediently in the manner of angle of incidence and

Corner angle is the same, so that the facing each other

End sides form a slope, which allows the role, at certain loads with an end face of the flange on the

To get to the guideway, for example, when the guideway is deformed and thereby the role is raised. This will be at the same time

Ensures that the role is self - centered so that the central peripheral surface rolls on the guideway. Alternatively, a rounded shape of the facing end faces of the

Flange areas may be provided. A particularly favorable arrangement is achieved when two straight sides extending towards each other intersect in the region of the at least one inner bearing shell, outside of any central bore. Then the chosen opening angle is neither too steep to reach a reasonable transition nor too little steep to limit the guideway sufficiently reliable.

According to a preferred embodiment, it is provided that the

Flange areas are integral part of the outer bearing shell, so that the entire circumference of the outer bearing shell at the same time represents the profile of the role.

Conveniently, it is provided that the two flange areas make up at their widest point less than 40% of the width of the outer bearing shell. This ensures that the central peripheral surface makes up at least 60% of the width of the outer bearing shell and the essential transmission of forces in the plane of the roller is reliably ensured. In this case, it is preferably further provided that the two flange regions make up at their narrowest point less than two thirds of the width of the widest point. This achieves a favorable angle centering the roller on the track.

It is preferably provided that the two flange regions protrude with respect to the central peripheral surface by a distance, measured at the diameter, which is smaller than the width of the central peripheral surface.

Preferably, however, this radial projection is greater than the common width of the two flange portions at their widest points.

Conveniently, the central peripheral surface has a smaller width as the double diameter of a ball of ball bearing rings. The use of two ball bearing rings with correspondingly large-sized balls a reliable unwinding and favorable force is achieved in the plane of the role.

The central peripheral surface advantageously has a radius to the roller axis, which is greater than the width of the bearing shells. As a result, a flat and stable role is created, which rolls easily on a guideway. Preferably, the outer circumference of the at least one inner bearing shell is greater than the width of the outer bearing shell in the direction of the roller axis and expediently also the at least one inner bearing shell in the direction of the roller axis. As a result, on the one hand creates a large receptacle for the connecting member, on the other hand, large balls can be provided for the ball rings.

Preferably, the outer bearing shell is rotationally symmetrical with respect to the roller axis. This allows the outer bearing shell

inexpensive, for example, as a turned part to be produced. The outer bearing shell is also expediently mirror-symmetrical with respect to a plane perpendicular to the roller axis, so that it can stand by which side of the outer bearing shell as the outside and which as

Inside of the roll is used later. The diameter of the balls of the ball bearing rings is preferably greater than the radial thickness of the at least one inner bearing shell. As a result, good rolling conditions of the balls are achieved, at the same time the at least one inner bearing shell is thin-walled and releases a large receptacle. At the same time, it is advantageously achieved that the at least one inner bearing shell has a low mass.

A roller is particularly preferred if the minimum radial strength of the outer bearing shell is greater than the maximum radial thickness of the second inner bearing shell. As a result, quite large forces can be introduced into the outer bearing shell.

Particularly favorable is an embodiment of the role in which two inner bearing shells, namely the first inner bearing shell and the second inner bearing shell, are provided which are respectively pressed to opposite sides in the outer bearing shell. As a result, a particularly simple structure and at the same time reliable running of the roller is achieved. The adjacent balls of the adjacent ball bearing rings are expediently spaced virtually free of play in the direction of the roller axis, so that a small role play arises and also acting in the direction of the roller axis forces which are introduced into the outer bearing shell, supported without torsion of the ball bearing ring by the at least one inner bearing shell become.

A particularly favorable roller configuration is achieved in that the height of the roller about 2.5 to 3.2 times, preferably 2.7 to 2.9 times and optimally 2.8 times the thickness of the outer bearing shell, and thus about the thickness of the roll is. As a result, the narrow-building roller and the guideway leading to it can be arranged close to a container along which the roller is to be displaceable.

Other features, developments and advantages of the invention will become apparent from the following descriptions of a preferred

Embodiment and from the dependent claims.

The invention will be explained in more detail below with reference to the accompanying drawings with reference to a preferred embodiment.

Fig. 1 shows a cross section through a preferred embodiment of a roll according to the invention. Fig. 1 shows a cross section through a roller 33 designed as a roller for a carriage of a top frame for a tarpaulin structure. The support roller 33 is designed as a rolling bearing about a roller axis 309, and has a width of the roller 33 spanning outer bearing shell 301, further two inner bearing shells, namely a pointing to an outside first inner bearing shell 302 and a pointing to an inner second inner

Bearing shell 303. Between the outer bearing shell 301 and the inner bearing shells 302, 303, two ball rings, namely an outwardly facing ball ring 304 and an inwardly facing ball ring 305, are arranged. From the ball ring 304, two balls 304a and a spacer 304b holding the balls 304a are shown, from the ball ring 305 two balls 305a and a spacer 305b. Everyone who

Ball Rings has 13 balls. The two inner bearing shells 302, 303 form a common inner bearing shell arrangement. This is characterized in that it is not symmetrical, but that the first inner bearing shell 302 and the second inner bearing shell 303 are formed very different. The second inner bearing shell 303 has a narrow annular shape, which has a hollow cylindrical opening 303i. The first inner bearing shell 302, however, has an annular portion 302r, to which an extension 302f integrally connects, which passes through the opening 303i and further protrudes axially beyond the first inner bearing shell 302 facing away from the end face of the second inner bearing shell 303. The extension 302 f thus also forms a defined spacer for the connection of the

Roller 33 to a holding plate such as the carriage of a U-shaped spar. The two inner bearing shells 302, 303 are pressed into the outer bearing shell 301 inside, so that the width of the two inner bearing shells 302, 303 in the region of the support of the balls is almost equal to the width of the outer bearing shell 301.

The first inner bearing shell 302 has a through bore 302b, the side facing to an outer side formed as a hexagonal projection 302s is, while it has an internal thread 302g on a side facing the inside. At the hexagonal projection 302s, the roller 33 can be held against rotation when a screw is inserted into the internal thread 302g

is screwed in. It is alternatively possible, the roller 33 to a

Unscrew threaded pin, for which a screwing is introduced into the approach 302s. Between the hexagonal projection 302s and the internal thread 302g, the bore 302b is formed with a center portion 302m connecting the two spaces. The projection 302f projects from the end face of the second inner bearing ring by approximately 4.75 mm and thus approximately as much as the diameter of the ball (3/16 "= 4.7625 mm).

The inner bearing shells 302, 303, the ball rings 304, 305, and the outer bearing shell 301 are arranged concentrically around the roller axis 309, which at the same time forms the cylinder axis of the roller 33. The parts mentioned are each made of steel.

The radial circumference of the outer bearing shell 301 has a central

Peripheral surface 31 1, which serves for the radial support of the roller 33 on a guide, not shown. On both sides of the central peripheral surface 31 1, the outer bearing shell 301 integrally formed with the outer bearing shell 301, the central peripheral surface 31 1 axially, ie in the direction of the roller axis 309, surrounding flange 312, 313, which are radially further spaced from the roller axis 309 than the central peripheral surface 31 1, so that the central peripheral surface 31 1 and facing each other

End faces 312a, 313a of the flange portions 312, 313 a portion of

Include leadership from three sides. It can be seen that the two mutually facing end faces 312a, 313a are at an angle to a plane perpendicular to the roller axis, for example the bisector between the two ball rings 304, 305, and together define an opening angle α which is between 30 ° and 50 ° and in the present case about 40 °. Due to the selected opening angle α, the two mutually facing end faces 312a, 313a of the straight lines extending the flange areas 312, 313 intersect at a point that extends from the roller axis 309 is spaced apart and approximately in the area occupied by the two inner bearing shells 302, 303 area. The mutually averted end faces 312b, 313b of the flange portions 312, 313 are each aligned with one of the end faces of the outer bearing shell 301. In this way, it is advantageously achieved that the flange areas 312, 313, which are provided, the guide track, along which the central peripheral surface 31 1 rolls, also laterally to

not lead to a greater width of the roller 33.

It can be seen that the distance of the mutually averted end faces 312b, 313b of the flange portions 312, 313, which coincides with the width of the two inner bearing rings 302, 303, at the same time defines the width D1 of the roller 33, which is for example 14 mm. The distance between the two

Flange portions 312, 313 of each other, which also forms the width D2 of the central peripheral surface 31 1 of the outer bearing shell 301, is dimensioned so that the width D2 of the central peripheral surface 31 1 is greater than the sum of the widths of the two flange portions 312, 313, and in the present case is about 8.5 mm.

It can further be seen that the maximum diameter of the flange portions 312, 313, which at the same time defines the height H1 of the roller 33, is three times the width D1 and is approximately 42 mm. The diameter of the central

Peripheral surface 31 1 can be seen as dimension H2 and is 34 mm, so that the radial projection of the flange 312, 313 results in 8 mm and thus only slightly smaller than the width D2 of the central peripheral surface 31 first

It can further be seen that the tips of the flange portions 312, 313 are rounded and have a small radius. This will

Damage to the guideway in the event of lifting the support roller 33 carried by the guideway.

The two end faces of the inner bearing shells 302, 303 and the outer bearing shell 301 are concealed by a ball rings 304, 305

Covering 320 closed, the ingress of moisture and Prevents contamination.

Finally, it can be seen that the balls 304a, 305a of the inner

Bearing shell 302, 303 and the outer bearing shell 301 are supported not only in the plane of the roller 33, but also by rounded circumferential track portions 331 on the inside of the outer bearing shell, which is centered on the inside of the outer bearing shell 301 at a common

Projection 330 are arranged. The inner bearing shells 302, 303 have rounded circumferential track areas 332, 333, which with respect to the centers of the balls 304a, 305a diametrically opposite the

Rail areas 331 are arranged and thus the balls 304a, 305a of the ball rings 304, 305 supported in the manner of an angular contact ball bearing in the direction of the roller axis 309. The above-described roller 33 in particular allows the absorption of forces perpendicular to the plane of the roller 33, which arise, for example, that not only the central peripheral surface 31 1 along a

Guideway unrolls, but also the flange portions 312, 313 are pressed against lateral boundaries of the guideway and thus must absorb axial forces.

A dashed portion of a plate body 30 of a carriage is illustrated, which illustrates that an end face 303s forms a contact surface for a surface of the plate body 30, while the projection 302f is insertable into a bore of the plate body 30. Here, the extension 302f passes through the

Bore only partially, whereby a screwed from the opposite side into the thread 302g screw the two inner bearing shells 302, 303 axially braced against each other. It can also be seen that the distal end of the extension 302f has a bevel formed on the outer circumference, which facilitates insertion into the bore.

Claims

1 . Roller, in particular carrying roller, for a carriage of a roof frame for a tarpaulin construction, comprising

two ball bearing rings (304, 305) with balls (304a, 305a), at least one inner bearing shell (302, 303), and

an outer bearing shell (301) associated with both ball bearing rings (304, 305),

which are each arranged concentrically about a roller axis (309) and form a roller bearing,

wherein the outer bearing shell (301) comprises a central peripheral surface (31 1) for radial support on a guide,

wherein the at least one inner bearing shell (302, 303) comprises a first inner bearing shell (302) and a second inner bearing shell (303),

characterized,

in that the first inner bearing shell (302) has an axial extension (302f) which has an opening (303i) of the second inner

Bearing shell (303) interspersed.

2. Roller according to claim 1, characterized in that the second inner bearing shell (303) is positively and / or non-positively connected to the first inner bearing shell (302).

3. A roller according to claim 1 or 2, characterized in that the axial extension (302f) of the first inner bearing shell (302) projects axially beyond the second inner bearing shell (303).

4. Roller according to one of the preceding claims, characterized

characterized in that the axial extension (302f) of the first inner bearing shell (302) has a bore (302b) which is provided with a bore (302b) Internal thread (302i) is equipped.

5. Roller according to one of the preceding claims, characterized

characterized in that the first inner bearing shell (302) comprises a prismatic projection (302s) for a tool.

6. Roller according to one of the preceding claims, characterized

characterized in that the second inner bearing shell (303) projects axially beyond the end face of the outer bearing shell (301).

7. Roller according to one of the preceding claims, characterized

in that the projection of the axial extension (302f) of the first inner bearing shell (302) via the second inner bearing shell (303) corresponds approximately to the diameter of a ball (304a, 305a).

8. Roller according to one of the preceding claims, characterized

characterized in that the first inner bearing shell (302) has a through bore (302b) having an end as

Prismatic approach (302s) for a tool and other end than internal thread (302i) is formed.

9. Roller according to one of the preceding claims, characterized

characterized in that the bearing shells (301, 302, 303) are made of steel.

10. Roller according to one of the preceding claims, characterized

characterized in that the bearing shells (301, 302, 303) support the balls (304a, 305a) of each of the two ball bearing rings (304, 305) obliquely in the manner of an angular contact ball bearing.

1 1. Roller according to claim 10, characterized in that the balls (304a, 305a) of both ball bearing rings (304, 305) each of a rounded circumferential track area (331; 332, 333) on a Projection (330) of the inside of the outer bearing shell (301) and the outside of the at least one inner bearing shell (302, 303) are supported. 12. Roller according to claim 1 1, characterized in that on the roll axis (309) facing projection (330) of the inside of the outer bearing shell (301) circulating track areas (331) for balls (304a, 305a) of both ball bearing rings (304, 305 ) are provided. 13. Roller according to one of the preceding claims, characterized

characterized in that the outer bearing shell (301) has flange portions (312, 313) axially surrounding the central peripheral surface (31 1) extending radially further from the roller shaft (309) than the central peripheral surface (31 1).

14. Roller according to claim 13, characterized in that the

Flange regions (312, 313) have mutually averted end faces (312b, 313b) which are each aligned with one of the end faces of the outer bearing shell (301).

15. Roller according to claim 13 or 14, characterized in that the flange portions (312, 313) facing each other end faces (312a, 313a) having an angle (a) to each other and to a to the roller axis (309) vertical plane.

16. Roller according to one of claims 13 to 15, characterized in that the mutually facing end faces (312a, 313a) extending straight lines in a joint region of a first inner bearing shell (302) and the second inner bearing shell (303) intersect.

17. Roller according to one of claims 13 to 16, characterized in that the flange portions (312, 313) are integral part of the outer bearing shell (301). Roller according to one of claims 13 to 17, characterized in that the two flange portions (312, 313) make up at their widest point less than 40% of the width of the outer bearing shell (301), and that the two flange portions (312, 313) its narrowest point less than two-thirds of the width of its widest point

turn off.

Roller according to one of claims 13 to 18, characterized in that the two flange portions (312, 313) with respect to the central peripheral surface (31 1) protrude by a distance which is less than the width of the central peripheral surface (31 1) and larger than the Width of the two flange portions (312, 313) is at its widest point.

Roller according to one of the preceding claims, characterized

characterized in that the central peripheral surface (31 1) has a smaller width than twice the diameter of a ball (304a, 305a) of the ball bearing rings (304, 305).

Roller according to one of the preceding claims, characterized

characterized in that the central peripheral surface (31 1) has a radius to the roller axis (309) which is greater than the width of the outer bearing shell (301).

Roller according to one of the preceding claims, characterized

in that a thickness of the at least one inner

Bearing shell (302, 303) is greater than a thickness of the outer

Bearing shell (301), respectively in the direction of the roller axis. 23. Roller according to one of the preceding claims, characterized

characterized in that the outer bearing shell (301)

is rotationally symmetric with respect to the roller axis (309). Roller according to one of the preceding claims, characterized

characterized in that the outer bearing shell (301) is mirror-symmetrical with respect to a plane perpendicular to the roller axis (309).

Roller according to one of the preceding claims, characterized

characterized in that the diameter of the balls (304a, 305a) of the ball bearing rings (304, 305) is greater than the radial thickness of the second inner bearing shell (303).

Roller according to one of the preceding claims, characterized

characterized in that the minimum radial strength of the outer

Bearing shell (301) is greater than the maximum radial thickness of the at least one inner bearing shell (302, 303).

Roller according to one of the preceding claims, characterized

characterized in that the first and the second inner bearing shells (302, 303) are each pressed from opposite sides into the outer bearing shell (301).

Roller according to one of the preceding claims, characterized

characterized in that adjacent balls (304a, 305a) of the

Ball bearing rings (304, 305) practically free of play in the direction of

Roll axis (309) are spaced.

Roller according to one of the preceding claims, characterized

characterized in that the height of the roller (33) is 2.5 to 3.2 times, preferably 2.7 to 2.9 times and optimally 2.8 times the thickness of the outer bearing shell (301).

Sled for a roof frame of a tarpaulin construction, with one

Plate body (30) which can be rolled over a support roller on a guide, characterized in that the support roller is formed as a roller (33) according to the preceding claims.

31. Carriage according to claim 30, characterized in that the carrying roller (33) is screwed through a screwed into an internal thread of the roller

Connecting means to the plate body (30) is connected.

32. Top frame for a tarpaulin structure, characterized by at least one carriage according to claim 30 or 31.

Tarpaulin structure, characterized by a roof frame according to claim 32.