DE9315049U1 - Multiple roller - Google Patents

Description

The invention relates to a multiple roller according to the preamble of claim 1.

Such multiple rollers are required, for example, in forklift trucks or similar. The rollers of a forklift truck are subjected to high static and dynamic loads, especially when cornering. With wider rollers, the additional problem when cornering is that the rollers are subject to high wear due to different running paths between the inner and outer ends of the roller, which leads to short downtimes.

Another problem is protecting the roller bearings of the rollers, which are mounted on a shaft, from contamination. The seals usually work according to the gap seal principle and are designed to protect against dust and

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Accounts:

*. I .SeL Oppenheimjr.&Cie.. Cologne (bank code 37030200) account no. 1O76O J J.;. *DejjtscheBankAG, Cologne (bank code 37070060) Account no. 1165018 · P

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Postgiro Cologne (bank code 3701005O) account no. 654-500

Splash water is also provided. In addition, for example, an external thrust washer is provided for rollers, which prevents the penetration of coarse dirt particles and at the same time forms a thread guard. This thread guard is essential because the bearings of rollers can be destroyed very quickly by packaging cords etc. Another disadvantage here is that the position of the thrust washer, e.g. in rollers, can be changed by impacts from the outside, so that the seal is compressed and slips out of position or is exposed to greater wear, so that the bearing is no longer protected after a short time and becomes inoperable.

Conventional gap seals also have the disadvantage that they only protect against splash water, so that the bearings can be damaged if high-pressure cleaning equipment is used.

The invention is based on the object of creating a multiple roller whose load-bearing capacity on one axle is increased, in which the speed difference when cornering is reduced, which is largely insensitive to shock loads and can be subjected to pressurized water.

The features of the main claim serve to solve this problem.

The invention advantageously provides for several rollers to be arranged next to one another on an axle, with the roller bearings of axially adjacent rollers arranged next to one another sitting on a common radially inner bush. Furthermore, a saddle ring is arranged between the axial end faces of adjacent rollers. The arrangement of several

Rollers on an axle, with adjacent rollers being coupled via a common, radially inner bushing, has the advantage of increasing the load capacity on the axle, with the individual rollers being able to rotate at different speeds when cornering. This reduces friction losses and wear. The common, radially inner bushing couples adjacent rollers in such a way that a defined axial distance between the rollers is precisely maintained. The constant axial distance enables the arrangement of a saddle ring between the rollers, which performs a radial and axial sealing function and forms a gap guard between the individual rollers. This gap guard protects the inner bearings of the multiple rollers, which are not accessible without considerable assembly effort, and prevents threads or cords from becoming wrapped up between the rollers and destroying the roller bearings.

A significant advantage of the multiple roller according to the invention is that the multiple roller can be assembled from several modular rollers. Compared to a single roller, only two additional parts are required, namely the common inner bushing and the saddle ring. In this way, multiple roller systems can be assembled cost-effectively.

The saddle ring is preferably made of a highly wear-resistant polyurethane, e.g. Aclathan with good sliding properties to compensate for the relative movements between the rollers.

In an advantageous embodiment, the saddle ring is flush with the surface of the roller coverings. This has the advantage that the load pressure on the multiple roller improves the sealing in the load area.

-A-

It can also be provided that the saddle ring engages in ring grooves in the axial end faces of adjacent rollers. In this case, the saddle ring can have a smaller diameter than the rollers.

The saddle ring can also consist of a cell ring made of foamed PUR elastomer, e.g. Aclacell. Such a saddle ring can also perform a dampening function between the rollers in the event of axial impacts.

Furthermore, the cell ring can be greased or soaked with oil to improve the sealing and the sliding behavior between the adjacent rollers and the cell ring.

In a further development of the invention, it is provided that the saddle ring is also designed as an axial seal for the axially inner roller bearings of adjacent rollers. Such a saddle ring reduces the assembly effort for a multiple roller system and thus reduces the manufacturing costs.

The axial seal, which is preferably used on the rollers at least for the axially outer roller bearings, creates a cavity for a sealing ring and maintains a defined wall distance from the roller bearing. This enables the use of a sealing ring that is constantly in contact with the sealing surfaces on the thrust washer and on the roller bearing with the same preload, so that the roller bearing is protected from pressurized water from high-pressure cleaning equipment. The axial seal is also highly protected against external shock loads, since the thrust washer is precisely fixed in its position on the radially inner bushing relative to the roller bearing.

Preferably, the sealing ring of the axial seal and/or the saddle ring is essentially V-shaped and symmetrical in cross section. Such a symmetrical design of the sealing ring or saddle ring, which opens radially outwards in a V-shape, ensures that essentially the same sealing force is exerted on the sealing surfaces.
The V-shaped design of the sealing ring or saddle ring allows subsequent greasing of the rolling bearings from the inside without any assembly work.

The sealing ring or saddle ring can also be mounted floating in a cavity. The floating arrangement allows the rotation speed of the sealing ring or saddle ring to be halved and thus the wear on the sealing lips to be evenly distributed over both sealing lips.

In the following, embodiments of the invention are explained in more detail with reference to the drawings.

Show it:

Fig. 1 shows a first embodiment of an inventive
Twin roller,

Fign.2 further embodiments for the gap and axial
up to 10 seals coupled together according to the invention
roll.

Fig. 1 shows a multiple roller as a twin roller with two rollers 1, the structure of which is explained below:

Each roller 1 has a roller covering 5 attached to an outer bushing 4. The outer bushing 4 accommodates a roller bearing 6 with its outer bearing at each of the axial ends.

ger shell 38. A spacer bush 7 is arranged between the radially inner bearing shells of the rolling bearings 6. With their inner bearing shells, the rolling bearings 6 sit on an inner bush 3, e.g. for a shaft not shown.

The rolling bearings 6 are slightly axially offset inwards with respect to the roller 1 in order to enable the bearings to be sealed to the outside using an axial seal.

The axial seal preferably consists of a symmetrical sealing ring 2 made of aclathane with a V-shaped cross-section, which is arranged between a thrust washer 8 and the roller bearing 6. The sealing ring 2 opens radially outwards in a V-shape and rests with its sealing lips 11 on the one hand on the thrust washer 8 and on the other hand on the outer bearing shell of the bearing 6. When installed, the sealing lips 11 are pre-tensioned and prevent the ingress of dirt and water. When the cavity 16 is pressurized from the outside, the pressure of the sealing lips 11 on the sealing surfaces on both sides is even increased, so that a reliable seal is also achieved against pressurized water.

The sealing ring 2 and the thrust washer 8 interact with the inner bushing 3 or the common inner bushing 19. The inner bushings 3, 19 have a stop 9 for this purpose, which in the embodiment of Fig. 1 consists of a radially protruding shoulder 10 of the bushing 3, 19.

The bushings 3, 4, 19 are simple to manufacture, e.g. from sintered metal, easy to assemble and easy to replace. The thrust washer 8 has a shoulder 20 which sits radially on the step 10 of the bushing 3, 19 and gives the thrust washer a high level of stability. The sealing ring 2 can in turn sit on this shoulder 20 or, floating in the space between

The thrust washer 8 and the roller bearing 6 are mounted in a cavity 16. The cavity 16 is preferably filled with grease.

The thrust washer 8 has a radially inwardly projecting collar 12 which, in the embodiment of Fig. 1, rests against the shoulder 10. The collar 12 can be pushed onto the bushing 3,19 with radial preload.

A wall 14 of the thrust washer 8 extends radially outward from the shoulder 20 and is preferably conically inclined axially inward toward the bearing 6. The conical inclination of the wall 14 ensures permanent centering of the sealing ring 2, particularly when the sealing ring 2 is arranged in a floating manner.

The thrust washer 8 can also be made in one piece with the bushing 3 or 19. In this case too, the bushings 3, 19 have a shoulder 10 which serves as a stop for the rolling bearing 6.

The spacer bushing 7 has an opening 15 which serves to regrease the bearings via a grease chamber 17. The sealing lips 11 of the sealing ring allow the grease to pass through the roller bearing 6 and past one of the sealing lips to the outside, whereby any dirt in the cavity 16 can be pressed out.

The common inner bushing 19 enables the coupling of two or more rollers 1 in a cost-effective manner, without the need for a large number of different components. As a gap seal between two rollers 1, a saddle ring 24 is provided in conjunction with the common bushing 19 between the axial end faces 22 of the roller lining 5 or the outer bushings 4.

: -I

In the embodiment of Fig. 1, the saddle ring 24 is flush with the covering surface 32 of the roller covering 5, whereby the opposite end faces 21 of the roller covering 5 can be tapered and widen radially outwards in order to accommodate a saddle ring 24 that is essentially trapezoidal or V-shaped in cross section. The load pressure on the multiple roller consisting of at least two rollers presses this saddle ring 24 into its seat more strongly in the load area, so that a reliable sealing of the gap between two rollers 1 is ensured. The V-shaped design of the saddle ring 24 also advantageously allows the multiple roller to be re-greased up to the area of the gap 18 arranged between the rollers 1.

In the embodiment of Fig. 2, a saddle ring 24, which is also essentially trapezoidal or V-shaped in cross section, is guided in annular grooves 28 arranged in the axial end faces 22.

The saddle ring 24 preferably consists of a highly wear-resistant polyurethane, preferably Aclathan with good sliding properties, in order to compensate for relative movements between the adjacent rollers 1.

The saddle ring is mounted with preload against the axial end faces, or conical end faces 21.

The inner bushing 19 can keep the adjacent rollers 1 at a predetermined constant distance due to the radially projecting shoulder 20, so that the saddle ring 24 arranged between the axial end faces 21 and 22 cannot be damaged.

Q

Despite the coupling of adjacent rollers 1, the individual rollers can rotate at different speeds when cornering.

The embodiment of Fig. 3 shows a saddle ring 24 which is essentially V-shaped or trapezoidal in cross section and has an annular collar 23 which projects into the intermediate space 18.

In the embodiment of Fig. 4, the axial end faces 22 of the roller covering 5 facing each other are conically inclined and form conical end faces 21. A saddle ring 24 with a V-shaped cross section is mounted in a floating manner between these conical end faces 21, whereby the saddle ring 24 centers itself automatically due to the conical end faces 21. Such a saddle ring 24 is flexible against internal pressure, e.g. during regreasing, whereas this saddle ring 24 is pressed particularly firmly against the sealing surfaces on the conical end faces 21 when subjected to external pressure, e.g. during high-pressure cleaning.

Fig. 5 shows an embodiment of a saddle ring 24, which in its cross-sectional shape essentially corresponds to the sealing ring 2 and has two V-shaped protruding legs that rest against the axial end faces 22. This saddle ring 24 also has a radially inwardly protruding annular collar 23, which can be firmly clamped on one side, for example between the thrust washer 8 and the outer bushing 4.

Fig. 6 shows an embodiment of a hollow cylindrical saddle ring 24, which engages in annular grooves 28 of the roller covering 5 coaxially to the axis of rotation of the rollers 1.

In the embodiment of Fig. 7, the saddle ring 24

a cell ring, preferably made of a foamed polyurethane, e.g. Aclacell, is provided. The cell ring 34 can be greased or soaked with oil. With axially recessed end faces 22, the cell ring 34 can rest on the outer bushings 4 of adjacent rollers 1.

Fig. 8 shows a saddle ring according to Fig. 2, which is combined with a different type of axial seal for the roller bearings 6 compared to Fig. 1. For this purpose, the inner bushing 19 is provided with a symmetrically arranged radially outwardly projecting ring web 26, which does not touch the outer bushings 4 of the adjacent rollers 1. Between the outer bearing shells of the opposing roller bearings 6 and the ring web 26, a sealing ring 2 with a V-shaped cross section is provided as an axial seal. This sealing ring 2 is preferably mounted in a floating manner.

In the embodiment of Fig. 9, a single sealing ring 2 with a V-shaped cross section is arranged in a floating manner between the outer bearing shells of the opposing roller bearings 6 of the adjacent rollers 1, wherein a saddle ring 24 according to the embodiment of Fig. 1 is also provided.

Fig. 10 shows an embodiment of a saddle ring 24 which also performs the function of the axial seal for the opposing roller bearings 6 of adjacent rollers 1. The saddle ring 24 according to Fig. 10 can touch the shoulder 20 of the inner bushing 19 and thereby additionally seal the gap between the rollers 1 radially.

Claims (17)

Protection claims 1. Multiple roller, with several rollers (1) with radially inner and outer bushings (3,4,19) that accommodate rolling bearings (6), with pressure-tight axial seals (2,8) for the rolling bearings (6) and with at least two highly wear-resistant roller linings (5) sitting on the outer bushings (4),
characterized in that the opposing rolling bearings (6) of axially adjacent rollers (1) are seated on a common radially inner bush (19), and that a saddle ring (24) is arranged between the axial end faces (22) of adjacent rollers (1). 2. Multiple roller according to claim 1, characterized in that the saddle ring (24) is flush with the covering surface (32) of the roller coverings (5). 3. Multiple roller according to one of claims 1 or 2, characterized in that the saddle ring (24) is V-shaped in cross section. 4. Multiple roller according to claim 1, characterized in that the saddle ring (24) engages in annular grooves (28) in the axial end faces (22) of adjacent rollers (1). 5. Multiple roller according to one of claims 1 to 4, characterized in that the saddle ring (24) consists of a cell ring (34) made of foamed PUR elastomer. 6. Multiple roller according to claim 5, characterized in that the cell ring (34) is greased or impregnated with oil. 7. Multiple roller according to claim 5 or dgr;, _{characterized} in that the roller coverings (5) in the region of adjacent rollers (1) axially recede relative to the outer bushings (4) in such a way that the cell ring (34) sits at least partially on the outer bushings (4). 8. Multiple roller according to one of claims 1 to 7, characterized in that the saddle ring (24) seals under pre-tension against the front edges (22) of adjacent rollers (1). 9. Multiple roller according to claim 3, characterized in that the saddle ring (24) is mounted in a floating manner between the adjacent rollers (1). 10. Multiple roller according to claim 9, characterized in that the axial end faces (22) of adjacent rollers (1) are conical. 11. Multiple roller according to one of claims 1 to 10, characterized in that the common inner bushing (19) has a radially outwardly projecting annular web (26) symmetrically between the roller bearings (6). 12. Multiple roller according to claim 11, characterized in that the opposing roller bearings (6) of adjacent rollers are each provided with sealing rings (2) with a V-shaped cross section against the - 13 ring webs (26) are sealed. 13. Multiple roller according to claim 12, characterized in that the sealing ring (2) is arranged floatingly. 14. Multiple roller according to claim 1, characterized in that the saddle ring (24) is also designed as an axial seal for the inner roller bearings (6) of adjacent rollers (1). 15. Multiple roller according to claim 14, characterized in that the saddle ring (24) seals against the radially inner bushing (3). 16. Multiple roller according to one of claims 1 to 15, characterized in that at least the outer roller bearings (6) are provided with an axial seal, in which the inner bushing (3, 19) has a stop (9) against which a thrust washer (8) with a radially inwardly projecting collar (12) axially rests, the collar (12) of the thrust washer (8) forms a stop for the roller bearing (6), and the thrust washer (8) with a radially outwardly projecting wall (14) forms a cavity (16) for the axial seal in the form of a sealing ring (2) with a defined distance from the roller bearing (6). 17. Multiple roller according to one of claims 1 to 15, characterized in that the axial seal between two adjacent roller bearings (6) consists of a single sealing ring (2) which rests with the sealing lips (11) against the axial end faces (36) of the radially outer bearing shells (38).