DE29512636U1 - Track roller track - Google Patents

Description

PATENT ATTORNEYS

DiPL-iNG. CONRAD KÖCHLING -·.*-·«.- -.-"*·'- -··-«s.·

DlPL-ING. CONRAD-JOACH!M KÖCHLING ^Note - ^: Intertractor Aktiengesellschaft

Hagener Str. 325 P. O. Box 2069, D-58020 Hagen

Fleyer Straße 135, D-58097 Hagen ncoooc

Call(0233i)8ii64 + 85033 ü-döZöd bevelsberg

Fax(O2331) 84840

Telegrams: Patent Cook Hagen

Accounts: Commerzbank AG, Hagen 3 515 095 (bank code 45040042) IAMT Ingenieursesellschaft for

Sparkasse Hagen 100012043(BLZ45050001) or aiii engineering company iur

Postgiro:Dortmund5989-460(BLZ44010046) allgemeine Maschinentechnik mbH.

,, _{co c} - Morgenbergstr. 19

VNR: ¹ IJlJl

...”,., D-08525 Plauen (Vogtland)

Serial No. Lt°.±±(.y..·?.

4 August 1995 ________________

from the

CJK/HI.

Track roller for crawler tracks

The invention relates to a roller for crawler tracks or similar endlessly rotating belts or chains, consisting of a roller body, an axle passing through it and bearings and seals arranged between the roller body and axle, wherein the axle is held fixed to the frame with its ends protruding axially from the roller body, or consisting of a roller body with shaft stubs at its ends, which are rotatably mounted in end caps that can be held fixed to the frame and have bearings and seals.

Such rollers are known, for example, from DE-GM 69 24 259 or DE 37 10 104 C2.

When such rollers are used as intended, considerable loads occur which can lead to

Intertractor 11823/95

O_

Deflection of the axle and/or the roller body. This results in high wear on the bearings that are arranged between the roller body and the axle or between the shaft stubs and the end caps. The bearings, which are usually designed as bearing bushes, wear particularly quickly on the edges where excessive stress occurs when the center line of the bearing bush and the axle are not coaxial due to deformations or tolerances. Slight deformations occur constantly in practical operation, so that the corresponding bearings are constantly subjected to uneven stress or local overstress.

Based on this prior art, the invention is based on the object of counteracting failure of the rollers due to bearing failure, in particular to counteract wear, overloading and edge loading of the bearings.

Intertractor 11823/95

-3-

A first solution to this problem is characterized in that the bearings arranged radially between the roller body and the axle or between the shaft stub and the end cap are designed as spherical bearings, preferably having a spherical cross-sectional contour so that they follow load-related deflections of the roller body or the axle without jamming.

By designing the bearings as spherical bearings or preferably as bearings with a spherical cross-sectional contour, it is ensured that angular errors caused by the deflection of the roller body and/or the axle do not lead to damage to the bearing or bearings, as the bearings can follow the corresponding movements. With a spherical cross-sectional contour, the spherical contour can only be provided on one side of the two corresponding bearings, which simplifies assembly and is also possible with undivided components. The bearings are preferably arranged directly under the running surfaces of the roller body.

Intertractor 11823/95

-4-

Preferably, the bearings consist of a bearing which is rotatable or
a first bearing part arranged non-rotatably or formed integrally with this or this and a second bearing part arranged rotatably or non-rotatably in the roller body or in the end caps
wherein the contact surface between the first and second bearing parts is crowned in cross-section.

The load on the spherical bearings or bearings with a spherical cross-sectional contour is independent of the deflection of the axle, since the contact geometry does not change. For this reason, the axle can also be smaller in diameter than previously common designs.
be executed.

The axial loads can also be absorbed by a pronounced curved contour, whereby
but preferably additional axial contact surfaces
are provided.

Intertractor 11823/95

-5-

It is also preferred that the center axis of the curvature line of the spherical cross section crosses the longitudinal center axis of the roller.

Furthermore, it is preferably provided that for the axial fixing of the roller body on the axle or between the end caps, additional axial contact surfaces or bearings are provided on the end pieces or the end caps or on the front surface of the roller body.

An alternative solution to the problem posed at the beginning is that the bearings arranged between the roller body and the axle or between the shaft stub and the end cap are designed as plain bearing bushes, which are tapered or conically widened in the area of the highest load that occurs when the roller body or the axle bends, so that in the load-free state a corresponding gap is created between the end area of the plain bearing bush and the axle or the shaft stub.

Intertractor 11823/95

-6-

It is preferably provided that the extension is realized by a small radius or a small chamfer, e.g. 1°.

Furthermore, it can preferably be provided that the end of the axle is flattened on one side or has a polygonal shape and can be inserted into a shape-matched recess on the frame side, whereby the step created by the flattening or polygonal shape serves as a contact surface on the frame side.

In addition, it can be provided that the axle ends are cross-perforated and that the frame-side fastening is carried out by means of fastening elements, in particular screws, guided through the cross-perforation.

In the embodiment described above, the bearing bush is tapered in the area of the highest load, i.e. over a radius or a phase, the sliding surface of the bush is adapted to the bending line of the axle or shaft

Intertractor 11823/95

-7-

adjusted. The bearing is somewhat elastic in this area, so that deformation of the axle or shaft is possible without extreme edge loading of the bushing in the bearing. In the area of the most heavily loaded point, relief is achieved.

The flattening or polygonal design of the ends of the axle eliminates the need for the previously used clamping pin as a means of preventing rotation, so that the corresponding end piece is simplified. The contact surface of the axle in the area of the flattening or the polygonal design allows support on the frame, so that the misalignment of the axle due to tolerances is minimized. It is also possible to screw and thus fasten the axle directly to the frame using the cross holes and screws inserted into the cross holes, so that the previously used end piece is completely eliminated. With such a design, only a cover with a seal is required, or the corresponding seal can be integrated into the axle. This also minimizes the

·

Intertractor 11823/95

Tolerances are ensured, which is beneficial for the trouble-free operation of the roller.

Another alternative solution, which can also be used advantageously in conjunction with the solutions according to claims 1 to 8, is that the roller body mounted on the axle consists of two partial bodies which are arranged at an axial distance from one another, with the axle having a support fixed to the frame in the middle part located between the partial bodies, or the partial bodies are arranged coaxially and connected to one another by an elastic bridge, e.g. a metal bellows or an elastomer or rubber element.

It is preferably provided that plain bearings are arranged as bearing elements between the partial bodies and the axle.

Furthermore, it can preferably be provided that both partial bodies are provided with seals at both axial ends, which are arranged between the end faces of the partial bodies and the end faces of the frame-fixed central support or the frame-fixed end pieces.

Intertractor 11823/95

■9-

In such an embodiment, the roller body is no longer one-piece, but consists of two symmetrical, preferably identical half parts. The roller body parts formed in this way are preferably mounted on the axle via plain bearings. The fastening to the frame is carried out via end pieces in which the axle stubs are held, and via a central support in which the axle is also held. In a design in which the roller body with shaft stubs at its ends is rotatably mounted in end caps, this two-part design of the roller body can also be carried out, with an additional frame-fixed bearing point then being formed in the middle area between the two body parts. In principle, the bearing body parts can each have shaft stubs on both ends, which are rotatably mounted in corresponding end caps or in a center cap. This design provides additional support in the middle of the roller, whereby additional seals are required in this middle separation area. The shaft stubs formed in this way

Intertractor 11823/95

-10-

The load is distributed across three support points. The short lever arms lead to less deformation and a smaller bending moment. The axle, end pieces, roller bodies, screw connections and bearings are therefore subjected to less stress.

In the case of an elastic bridge between the parts of the roller, this can be attached to the parts as a tubular metal bellows coupling or a tubular elastomer or rubber coupling.

A further alternative solution, which can also be advantageously combined in connection with the features of claims 1 to 8, is seen in the fact that the roller body provided with shaft stubs at its ends is divided in the middle and provided with shaft stubs, wherein the central shaft stubs are rotatably mounted in a central double cap fixed to the frame.

The advantages have already been described above.

A further alternative solution to the problem, which can be used advantageously in particular in combination with the features of claims 1 to 9,

Intertractor 11823/95

■11-

is seen in the fact that separate partial rollers are arranged for each side of the chain, whereby the partial rollers on one side of the chain are laterally spaced from the partial rollers on the other side of the chain and the partial rollers on one side of the chain are either aligned coaxially with the partial rollers on the other side of the chain or are offset from one another in the running direction of the chain and arranged parallel to one another.

It is preferably provided that each partial roller has two flanges and the bearings have two stop surfaces to absorb the axial forces of the partial roller.

Alternatively, it can also be provided that each partial roller has only one flange and the bearing correspondingly has only one stop surface to absorb the axial forces.

In these designs, the roller body has only one running surface for one side of the chain. The corresponding partial rollers must therefore be placed next to each other

Intertractor 11823/95

-12-

(coaxial with each other) or offset in the direction of travel, whereby they are arranged along the track edges of a chain or the like on the right or left side of the chain.

If each partial roller has two flanges, the corresponding plain bearing has two corresponding contact surfaces to support the axial forces. If only one flange is provided on each partial roller, axial forces only occur in one direction, so that one axial bearing surface is sufficient. Due to the short axle design, deformations and bending moments are low. The loads on axles, end pieces, screws and plain bearings are therefore significantly reduced.

A further alternative solution to the problem, which can also be advantageously combined with the features of claims 1 to 8, is seen in the fact that the axle consists of two axle stubs engaging the front side of the roller body.

&igr;;;&idiagr;

Intertractor 11823/95

-13-

Preferably, it can be provided that the means for holding each axle stub fixed to the frame are formed in one piece with the axle stub.

In addition, it can preferably be provided that the seat for the front seal between the axle stub and the roller body is incorporated into a flange edge of the axle stub.

In some circumstances it is preferred that the bearing between the axle stub and the roller body is designed as a tapered bearing with a cone angle that diverges from the end of the roller body mounted on the corresponding axle stub.

In this embodiment, the roller body is connected to an axle stub via plain bearing bushes. Due to the relatively large axle stub, the screwing surface for fixing to the frame and the seal seat can be provided directly on the axle body. In addition,

:·&iacgr;;&igr;&igr;· °!

Intertractor 11823/95

-14-

A tapered bearing surface can also be provided. The division of the axis makes the entire system softer and results in a certain adjustment flexibility in the area of the bearings. The loads on the screw-on surfaces fixed to the frame become greater, as the bending moment must also be supported. The screw-on surface directly on the axis means that fewer tolerances are superimposed, which means that the angular errors in the bearing can be reduced.

Embodiments of the invention are shown in the drawing and described in more detail below. It shows:

Fig. 1 a first embodiment of a roller seen in central longitudinal section;

Fig. 2 a variant in the same view;

Fig. 3 another variant in the same view, partially sectioned;

Intertractor 11823/95

-15-

Fig. 4 shows a detail of Figure 3 in an enlarged view;

Fig. 5 another embodiment in central longitudinal section ;

Fig. 6 and 7 alternative details of Figure 5

in enlarged view;

Fig. 8 shows another embodiment of a roller seen in central longitudinal section;

Fig. 9 and 10 further embodiments in the same

Opinion;

Fig. 11/llA another variant in a similar representation;

Fig. 12 shows a variant of the embodiment according to Figure 11;

Fig. 13 and 14 show further variants in cross section.

•♦ · · J 5 &iacgr;&idgr; * **· «

Intertractor 11823/95

-16-

Figures 3 to 8 and 10 to 14 show the roller in the installed position. Figures 1, 2 and 9 show the roller turned over to the installed position (top and bottom swapped).

Figure 1 shows a roller for crawler tracks or similar endless belts or chains. It consists of a roller body 1, an axle 2 that passes through it, and bearings 3 and seals 4 arranged between the roller body 1 and the axle. End pieces 5 are attached to the ends of the axle 2 that protrude axially from the roller body 1 and are connected to dowel pins 6 that are fixed to parts of the chassis or the like. Such a roller is shown in Figures 1, 3, 5, 8 and in principle also in Figures 11 and 12.

The embodiment according to Figure 2 shows a roller, which consists of a roller body 1, which has shaft stubs 7 at its ends. The shaft stubs 7 are rotatably mounted in end caps 8 that can be fixed to the frame, for which purpose corresponding bearings 3 and seals 4 are provided.

Intertractor 11823/95

-17-

In the embodiments according to Figures 1 and 2, the bearings arranged radially between the roller body 1 and the axle 2 or between the shaft stubs 7 and end caps 8 are designed as spherical bearings, in particular as bearings with a spherical cross-sectional contour. Due to this design, they can follow load-related deflections of the roller body 1 or the axle 2 without jamming. The bearings 3 can consist of a first bearing part 9 arranged rotatably on the axle 2 or the shaft stub 7 or formed as one piece with it or arranged non-rotatably relative to it and a second bearing part 10 arranged rotatably or non-rotatably in the roller body 1 or in the end caps 8, the contact surface 11 between the first and second bearing parts 9, 10 being spherical in cross-section. The center axis of the curvature line of the spherical cross-section crosses the longitudinal center axis 12 of the roller.

Additional axial contact surfaces or bearings 13 can be designed to axially fix the roller body 1 on the axis 2 or between the end caps 8. As can be seen from the embodiment according to Figure 1

Intertractor 11823/95

-18-

As shown in Figure 1a, the roller body 1 can either rotate around the surface 14, so that the surface 11 is only used for pivoting. Or the rotation and pivoting can take place in the area of the curved surface 11. In this case, the part 9 can also be designed as one piece with the axle 2. The axial loads can be absorbed by a correspondingly pronounced curved contour (at 11). It is also possible, as shown in Figure 1a, to provide the first and second bearing parts 9, 10 with a corresponding rounding (crowned contour 11) on only one side, with this rounding ending on the side facing the other bearing 9, parallel to the central longitudinal axis of the roller. This can simplify assembly.

In the embodiment according to Figure 3, a plain bearing bush is provided as a bearing 3 between the roller body 1 and the axle 2. This is tapered or conical in the area of the highest load that occurs when the roller body 1 or the axle 2 bends.

Intertractor 11823/95

-19-

expanded so that in the load-free state a corresponding gap 14 is created between the outward-facing end area of the plain bearing bush and the axis 2. The force curve is shown by the arrows F and the small arrows in the lower half of the drawing

# The deflection line is at 15

clarified.

As can be seen in particular from Figure 4, the extension 15 is realized by a small radius R or by a small phase of, for example, one angular degree.

In the design according to Figure 5, the configuration is similar, whereby the ends of the axles 2 are flattened. The flattening is shown at 16. This makes it possible to insert the axle ends directly into a shaped recess on the frame side, whereby the step 17 created by the flattening 16 serves as a contact surface.

Intertractor 11823/95

-20-

Because in these embodiments the bearing bush of the bearing 3 is tapered in the area of the highest load, i.e. the sliding surface of the bush is adapted to a bending line comparable to the bending line 15 over a radius or a phase, a certain amount of play is achieved so that the axis 2 can be deformed without extreme edge loading of the bearing. The point subject to the highest load is thus relieved. The flattening 16 eliminates the previously usual clamping pin 6 as a torsion lock and the end piece is structurally simplified. The contact surface 17 on the frame or chassis minimizes the misalignment of the axis 2 due to tolerances.

In the embodiment according to Figure 8, the roller body 1 mounted on the axle 2 consists of two partial bodies 18, which are arranged at an axial distance from one another. The axle 2 has a support 19 in the middle of the gap formed between the partial bodies 18, which is held fixed to the frame. The bearing elements 3 are

Intertractor 11823/95

-21-

between the partial bodies 18 and the axle 2 plain bearings are arranged. Both partial bodies 18 are provided with seals 4 at both axial ends, which are arranged between the end faces of the partial bodies ■ 18 and the end faces of the central support 19 or the end pieces 5. The load is distributed through the three support points fixed to the frame. The short lever arms lead to small deformations on the one hand and to small bending moments on the other. The corresponding elements are therefore subjected to less stress.

In the embodiment according to Figures 13 and 14, a tubular metal bellows coupling (Figure 13) or a tubular elastomer or rubber element is fastened between the partial bodies 18 so that the load-related bending deformation can be absorbed without damage.

In the embodiment according to Figures 9 and 10, a separate partial roller 20 is arranged for each side of the chain (seen to the right and left of the running direction). The partial rollers on one side of the chain are arranged at a lateral distance from the partial rollers 20 on the other side of the chain.

Intertractor 11823/95

The partial rollers 20 on one side of the chain can either be aligned coaxially with the partial rollers on the other side of the chain or they can also be arranged offset from one another in the running direction of the chain and parallel to one another.

In the embodiment according to Figure 9, the partial roller 20 has two flanges 21. The bearings 3 have two stop surfaces 24 for absorbing the axial forces of the partial roller 20.

In the case of the partial roller according to Figure 10, only one flange 22 is provided. The corresponding bearing 3 therefore only has one stop surface 23 to absorb the axial forces. The partial rollers 20 in turn consist of a roller body through which an axle passes, with the bearing 3 arranged between the axle and the roller body. In these embodiments according to Figures 9 and 10, the partial roller bodies 20 each have only one running surface for one side of the chain. The rollers must therefore be arranged next to one another (coaxial) or offset from one another in the direction of travel.

Intertractor 11823/95

-23-

(parallel to the axis). The short axis design means that deformations and bending moments are low. The loads on the axis, end pieces, screws and plain bearings are therefore lower.

In the variant according to Figures 11 and 12, the axle consists of axle stubs 25 that engage the front side of the roller body 1. The means for holding each axle stub 25 fixed to the frame are formed in one piece with the axle stub.

The seat for the front seal 4 is incorporated between a flange collar 26 of the axle stub 25 and the roller body, primarily in the flange edge 26. The bearing 3 between the axle stub 25 and the roller body 1 is designed as a tapered bearing with a cone angle that diverges towards the end of the roller body, according to the embodiment shown in Figure 12. Due to the relatively large axle stub 25, the screw-on surface and the seal seat 4 can be provided directly at the free end of the axle body. The division of the axle

Intertractor 11823/95

the entire system is softer and a certain adjustment flexibility is achieved in the area of the bearings 4. The loads on the screwing surface (frame-mounted bracket) are greater because the bending moment must also be supported. Due to the screwing surface directly at the end of the axle stub 25, fewer tolerances are superimposed, which reduces angular errors in the bearing.

With this design, the end piece can be made as one piece with the axle stub, so that the assembly effort is reduced. The seal between the axle and the end piece is also eliminated. In addition, the corresponding dowel pin is also eliminated. The axle body can also be made of cast iron. However, the roller must be secured against falling apart during transport as a single part in the assembled state. The rollers can again be attached to the frame using a central screw that runs transversely to the roller axis.

All designs increase the load-bearing capacity of the rollers and thus extend their service life.

Intertractor 11823/95

-25-

The invention is not limited to the embodiments, but is variable in many ways within the scope of the disclosure.

All new individual and combination features disclosed in the description and/or drawing are considered essential to the invention.

Claims (19)

Intertractor 11823/95 -26- "Protection claims: 1. A track roller for crawler tracks or similar endlessly rotating belts or chains, comprising a track roller body, an axle passing through the track roller body and bearings and seals arranged between the track roller body and the axle, the axle being held fixed to the frame with its ends projecting axially out of the track roller body, or comprising a track roller body with shaft stubs at its ends which are rotatably mounted in end caps which can be held fixed to the frame and have bearings and seals, characterized in that the bearings (3) arranged radially between the track roller body (1) and axle (2) or between the shaft stub (7) and the end cap (8) are designed as spherical bearings, preferably having a spherical cross-sectional contour, so that they follow load-related deflections of the track roller body or axle without jamming. Intertractor 11823/95 -27- 2. Roller according to claim 1, characterized in that the bearings (3) consist of a first bearing part (9) arranged rotatably or non-rotatably on the axle (2) or the shaft stub (7) or formed integrally therewith and a second bearing part arranged rotatably or non-rotatably in the roller body (1) or in the end caps (8). (10), wherein the contact surface between the first and second bearing parts (9,10) is spherical in cross section. 3. Roller according to claim 1 or 2, characterized in that the center axis of the curvature line of the spherical cross section crosses the longitudinal center axis (12) of the roller. 4. Roller according to one of claims 1 to 3, characterized in that for the axial fixing of the roller body (1) on the axle (2) or between the end caps (8) additional axial contact surfaces •♦ · * Intertractor 11823/95 -28- or bearings (13) are provided on the end pieces (5) or the end caps (8) or on the front face of the roller body (1). 5. Roller according to the preamble of claim 1, characterized in that the bearings (3) arranged between the roller body (1) and axle (2) or between the shaft stub (7) and end cap (8) are designed as plain bearing bushes which are conically or conically widened in the region of the highest load occurring when the roller body or axle bends, so that in the load-free state a corresponding gap is formed between the end region of the plain bearing bush and the axle or the shaft stub. 6. Roller according to claim 5, characterized in that the extension (15) is realized by a small radius or a small chamfer, for example of 1°. Intertractor 11823/95 -29- 7. Roller according to one of claims 1 to 6, characterized in that the end of the axle (2) is flattened on one side or has a polygonal shape and can be inserted into a shapely recess on the frame side, the step (17) produced by the flattening (16) or polygonal shape serving as a contact surface on the frame side. 8. Roller according to one of claims 1 to 6, characterized in that the axle ends are transversely perforated and the fastening on the frame side is carried out by means of fastening means, in particular screws, guided through the transverse perforation. 9. Roller according to the preamble of claim 1, in particular according to one of claims 1 to 8, characterized in that the roller body (1) mounted on the axle consists of two partial bodies (18) which are arranged at an axial distance from one another, the axle (2) having a support (19) held fixed to the frame in the middle part located between the partial bodies (18) or the partial bodies (18) are arranged coaxially and connected by an elastic bridge, e.g. a metal bellows or an elastomer or Intertractor 11823/95 -30- rubber element are connected to each other. 10. Roller according to claim 9, characterized in that plain bearings are arranged as bearing elements (3) between the partial bodies (18) and the axle (2). 11. Roller according to claim 9 or 10, characterized in that both partial bodies (18) are provided at both axial ends with seals (4) which are arranged between the end faces of the partial bodies (18) and the end faces of the frame-fixed central support (19) or the frame-fixed end pieces (5). 12. Roller according to the preamble of claim 1, in particular according to one of claims 1 to 8, characterized in that the roller body (1) provided with shaft stubs (7) at its ends is divided in the middle and provided with shaft stubs, the central shaft stubs being rotatably mounted in a central double cap. Intertractor 11823/95 -31- 13. Roller according to the preamble of claim 1, in particular according to one of claims 1 to 8, characterized in that separate partial rollers (20) are arranged for each side of the chain, the partial rollers (20) of one side of the chain being laterally spaced from the partial rollers (20) of the other side of the chain and the partial rollers (20) of one side of the chain being either aligned coaxially with the partial rollers (20) of the other side of the chain or being arranged offset from one another in the running direction of the chain and axially parallel to one another. 14. Roller according to claim 13, characterized in that each partial roller (20) has two flanges (21) and the bearings (3) have two stop surfaces (24) for absorbing the axial forces of the partial roller (20). Intertractor 11823/95 -32- 15. Roller according to claim 13, characterized in that each partial roller (20) has only one flange (22) and the bearing (3) accordingly has only one stop surface (23) for absorbing the axial forces. 16. Roller according to the preamble of claim 1, in particular according to one of claims 1 to 8, characterized in that the axle (2) consists of two axle stubs (25) engaging at the end face of the roller body (1). 17. Roller according to claim 16, characterized in that the means for securing each axle stub (25) to the frame are formed integrally with the axle stub (25). 18. Roller according to claim 16 or 17, characterized in that the seat for the front seal (4) between the axle stub (25) and the roller body (1) is incorporated in a flange edge (26) of the axle stub (25). Intertractor 11823/95 -33- 19. Roller according to one of claims 16 to 18, characterized in that the bearing (3) between the axle stub (25) and the roller body (1) is designed as a tapered bearing with a cone angle diverging from the roller body end mounted on the corresponding axle stub (25).