RUNNING WHEEL FOR A CRANE

Abstract

A running wheel (1, 2) for a crane (16), in particular gantry crane, comprising a shaft (3), a wheel rim (4) and a hub (5) connecting the shaft (3) to the wheel rim (4) for rotation therewith, at least one connection between the hub (5) and the shaft (3) and/or between the hub (5) and the wheel rim (4) having a press fit (6) and a first form fit established by a first stop surface (8), the first form fit blocking a relative movement of the hub (5) in relation to the shaft (3) or the wheel rim (4) in a first direction (17) running parallel to an axis of rotation (7) of the running wheel (1, 2), wherein the connection additionally has at least one second form fit established by a second stop surface (9), wherein the second form fit blocks the relative movement of the hub (5) in relation to the shaft (3) or the wheel rim (4) in a second direction (18) opposed to the first direction (17).

Claims

1. A running wheel for a crane, comprising a shaft, a wheel rim, a hub connecting the shaft to the wheel rim for rotation therewith, at least one connection between the hub and the shaft or between the hub and the wheel rim, the at least one connection comprising a press fit and a first form fit established by a first stop surface, the first form fit blocking a relative movement of the hub in relation to the shaft or the wheel rim in a first direction that extends parallel to an axis of rotation of the running wheel, and at least one second form fit established by a second stop surface, the second form fit blocking a relative movement of the hub in relation to the shaft or the wheel rim in a second direction opposite to the first direction.

2. The running wheel as claimed in claim 1, wherein the press fit is arranged in a region between the first stop surface and the second stop surface.

3. The running wheel as claimed in claim 1, wherein the press fit at least one of (a) connects a press fit inner surface of the hub that faces the axis of rotation of the running wheel and a press fit outer surface of the shaft that faces away from the axis of rotation of the running wheel to each other with a force fit, or (b) connects a press fit inner surface of the wheel rim that faces the axis of rotation of the running wheel and a press fit outer surface of the hub that faces away from the axis of rotation of the running wheel to each other with a force fit.

4. The running wheel as claimed in claim 3, wherein at least one of (a) the shaft includes the first stop surface and the second stop surface, and the first stop surface and the second stop surface and the press fit outer surface of the shaft are integrally formed in a material of the shaft, or (b) the wheel rim has the first stop surface and the second stop surface, and the first stop surface and the second stop surface and the press fit inner surface of the wheel rim are integrally formed in a material of the wheel rim.

5. The running wheel as claimed in claim 4, wherein at least one of (a) the press fit inner surface of the hub is conical at least in regions, and a smallest inside diameter of the press fit inner surface is adjacent to the second stop surface of the shaft in an operating state of the running wheel, or (b) the press fit outer surface of the hub is conical at least in regions and a largest outside diameter of the press fit outer surface is adjacent to the second stop surface of the wheel rim in the operating state of the running wheel.

6. The running wheel as claimed in claim 1, wherein at least one of the shaft or the wheel rim includes an integrally formed insertion bevel, and the insertion bevel is arranged on a side of the second stop surface that faces away from the press fit.

7. The running wheel as claimed in claim 1, wherein the running wheel includes at least one securing device, and the second stop surface is arranged on the securing device.

8. The running wheel as claimed in claim 7, wherein the at least one securing device is a securing ring which engages in a groove formed on at least one of the wheel rim or on the shaft.

9. The running wheel as claimed in claim 7, wherein the at least one securing device is fastenable or fastened to at least one of the wheel rim or to the shaft.

10. The running wheel as claimed in claim 9, wherein the at least one securing device is releasably fastenable or fastened to allow removal without destruction using connecting elements.

11. A method for producing a running wheel as claimed in claim 1, comprising: (a) pushing the hub in the first direction into the wheel rim, and elastically deforming the second stop surface during the pushing in of the hub, and, in a completely pushed-in joining state, in which the hub is in contact with the first stop surface, the second stop surface elastically returning at least substantially to an original shape with the second stop surface establishing the second form fit and blocking a relative movement of the hub in relation to the wheel rim in the second direction, or (b) pushing the shaft into the hub in the first direction, and elastically deforming the second stop surface during the pushing in of the shaft, and, in a completely pushed-in joining state, in which the shaft is in contact with the first stop surface, the second stop surface elastically returning at least substantially to an original shape with the second stop surface establishing the second form fit blocking a relative movement of the shaft in relation to the hub in the second direction.

12. A crane comprising at least one running wheel as claimed in claim 1.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0033] Further features and details of preferred embodiments of the invention will be explained with reference to the exemplary embodiments of running wheels according to the invention and of a crane according to the invention that are illustrated in the figures, in which:

[0034] FIG. 1 shows a crane which is designed as a gantry crane with running wheels according to the invention;

[0035] FIG. 2 shows a first exemplary embodiment of a running wheel according to the invention as seen in a side view in a direction parallel to the axis of rotation of the running wheel;

[0036] FIG. 3 shows a longitudinal center section in a sectional plane, placed through the longitudinal center axis, of the running wheel according to FIG. 2, with the shaft being illustrated in un-sectioned form;

[0037] FIG. 4 shows the detail A from FIG. 3;

[0038] FIG. 5 shows the components, illustrated in FIG. 4, of the running wheel before being joined together;

[0039] FIG. 6 shows a second exemplary embodiment of a running wheel analogous to FIG. 3;

[0040] FIG. 7 shows the detail B from FIG. 6;

[0041] FIG. 8 shows a third exemplary embodiment according to the invention analogous to FIG. 2;

[0042] FIG. 9 shows an isometric view of the running wheel according to FIG. 8 in a partially sectioned illustration;

[0043] FIG. 10 shows a longitudinal center section of the running wheel according to FIG. 8;

[0044] FIG. 11 shows the detail C from FIG. 10;

[0045] FIGS. 12 to 14 show a fourth exemplary embodiment of a running wheel according to the invention analogously to FIGS. 2 to 4, wherein FIG. 14 shows the detail D of FIG. 13;

[0046] FIGS. 15 to 18 show a fifth exemplary embodiment according to the invention analogously to FIGS. 8 to 11, wherein FIG. 18 shows the detail E from FIG. 17, and

[0047] FIG. 19 shows a sixth exemplary embodiment of a running wheel.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0048] FIG. 1 shows a crane 16, which is designed as a gantry crane, for transporting containers (not illustrated) in a container terminal. The crane 2 is displaceable or movable horizontally along a longitudinal extent of running rails 26, in particular crane running rails. The running rails 26 are merely indicated by chain-dotted lines in FIG. 1. The crane 2 is supported on the running rails 26 via running wheels 1, in particular crane running wheels.

[0049] Furthermore, the gantry crane 16 comprises a crane girder (not labeled specifically) on which running rails 27 of the crane 2 are arranged. These running rails 27 could also be referred to as trolley rails. A trolley 31 of the crane 2 is displaceable in the horizontal direction along the running rails 27. The trolley 31 is supported on the running rails 27 via running wheels 2, also called trolley running wheels. Only one of the two running rails 27 is illustrated in FIG. 1. In an alternative embodiment, the crane 2 could also have two crane girders which are spaced apart from each other and on which in each case one of the running rails 27 is fastened.

[0050] The exemplary embodiments described below are alternative variant embodiments of the connection between a shaft 3 and a hub 5, i.e. a shaft-hub connection of a running wheel 1, 2, and/or between the hub 5 and a wheel rim 4, i.e. a hub-wheel rim connection of a or the running wheel 1, 2. The similarities of the exemplary embodiments shown will be discussed below.

[0051] In the exemplary embodiments shown, the shaft 3 is composed of steel, as is also preferred. The shaft 3 could be composed, for example, of unalloyed or low-alloy tempering steel. In the tempered state, the tempering steel advantageously has tensile strengths of between 500 MPa (megapascal=N/mm.sup.2) and 1000 MPa.

[0052] In the exemplary embodiments, as is also preferred, the hub 5 is likewise manufactured from steel. The hub is advantageously composed of structural steel having tensile strengths of between 350 MPa and 800 MPa. An example of a suitable material for the hub 5 is structural steel S355J2.

[0053] The wheel rim 4 used in the exemplary embodiments is preferably manufactured from steel. The wheel rim 4 is advantageously comprised of a hardenable, low-alloy tempering steel having tensile strengths of between 700 MPa and 1200 MPa. Examples of suitable materials for the wheel rim 4 are 42CrMo4 or 34CrNiMo6 or 30CrNiMo8. It can be provided that a tread 14 of the wheel rim 4 is hardened. Alternatively, the tread 14 may also only be tempered. If the tread 14 of the wheel rim 4 is realized in hardened form, the surface hardness of the tread 14 advantageously has a Rockwell hardness of at least 40 HRC and less than 60 HRC, preferably at least 45 HRC and less than 55 HRC.

[0054] In the exemplary embodiments, a wheel rim 4 having a circular-cylindrical tread 14 is illustrated, i.e. the tread 14 bounds the wheel rim 4 at a largest diameter 15 of the wheel rim 4 in a radial direction facing away from an axis of rotation 7 of the running wheel. The diameter 15 of the tread 14 of the wheel rim 4 simultaneously also defines the diameter of the running wheel 1, 2.

[0055] In the exemplary embodiments, the diameter 15 of the tread 14 of the wheel rim 4 is 630 mm. Other values of the diameter 15 are also conceivable and possible depending on the required loading capacities, as mentioned at the beginning.

[0056] A rail head width of the running rail 26, 27 is advantageously between 50 mm and 150 mm, preferably between 75 mm and 120 mm.

[0057] The radial loading capacity of running wheels 1, 2 according to the invention advantageously lies within the range of 50 kN to 800 kN. At the preferred diameters 15 of the tread 14, i.e. from 500 mm to 710 mm, the radial loading capacity advantageously lies within the range of 200 kN to 500 kN. The axial forces which can be absorbed by the running wheel 1, 2, i.e. lateral forces in a direction parallel to the axis of rotation 7 of the running wheel, are advantageously up to 20% of the radial loading capacities mentioned.

[0058] The details of the connection of the hub 5 to the wheel rim 4 will be discussed with reference to the following first four exemplary embodiments of running wheels 1, 2 according to the invention. In the exemplary embodiments 5 and 6, variants of a connection of the shaft 3 to the hub 5 of a running wheel 1, 2 are shown by way of example. It is emphasized once again at this juncture that a running wheel 1, 2 according to the invention can have only one of the connections mentioned or both connections.

[0059] In the first exemplary embodiment according to FIGS. 2 to 5, a running wheel 1, 2 which has what is referred to as a longitudinal interference fit is shown. A longitudinal interference fit is characterized in that the components to be connected for forming a press fit are essentially at the same temperature and are pushed cold into one another.

[0060] A press fit 6 is formed between the hub 5 and the wheel rim 4, i.e. the hub 5 and the wheel rim 4 are connected to each other with a force fit by the press fit 6. The forces occurring in the radial direction and in the circumferential direction, with respect to an axis of rotation 7 of the running wheel, during the operation of the crane 16 are transmitted via the press fit 6.

[0061] In addition to the press fit 6, it is provided that the connection between the hub 5 and the wheel rim 4 has a first form fit which is established by a first stop surface 8, wherein the first form fit blocks a relative movement of the hub 5 in relation to the wheel rim 4 in a first direction 17 running parallel in the axis of rotation 7 of the running wheel 1, 2, cf. FIG. 4. Furthermore, the connection between the hub 5 and the wheel rim 4 has a second stop surface 9 which secures the second form fit. The second form fit blocks the relative movement of the hub 5 in relation to the wheel rim 4 in a second direction 18 opposed to the first direction 17. As a result, i.e. in the operating state of the running wheel 1, 2, the relative movement of the hub 5 in relation to the wheel rim 4 with respect to directions parallel to the axis of rotation 7 of the running wheel is prevented.

[0062] As illustrated in the first exemplary embodiment, the first stop surface 8 and the second stop surface 9 are advantageously oriented orthogonally to the axis of rotation 7 of the running wheel.

[0063] The press fit 6 of the connection, as is also preferred, is arranged in the region between the first stop surface 8 and the second stop surface 9. The pressing forces bringing about the press fit 6 are preferably oriented in the radial direction with respect to the axis of rotation 7 of the running wheel. In the first exemplary embodiment, the press fit 6 extends between the first stop surface 8 and the second stop surface 9. In the first exemplary embodiment, the first stop surface 8 and the second stop surface 9 are arranged adjacent to the press fit 6.

[0064] The press fit 6 is designed in a force-fitting manner between a press fit inner surface 22, which faces the axis of rotation 7 of the running wheel, of the wheel rim 4 and a press fit outer surface 21, which faces away from the axis of rotation 7 of the running wheel, of the hub 5. The press fit inner surface 22 of the wheel rim 4 therefore bounds the wheel rim 4 inward in the radial direction, with respect to the axis of rotation 7 of the running wheel, in the region of the press fit 6. The press fit outer surface 21 of the hub 5 bounds the hub 5 outward in the radial direction, with respect to the axis of rotation 7 of the running wheel, in the region of the press fit 6.

[0065] In the first exemplary embodiment of a running wheel 1, 2 according to the invention, it is provided that the wheel rim 4 has the first stop surface 8 and the second stop surface 9. The first stop surface 8 and the second stop surface 9 and the press fit inner surface 22 of the wheel rim 4 are connected to one another integrally in terms of material. The tread 14 is also integrally formed in terms of material on the wheel rim 4, and therefore the wheel rim 4 as a whole is formed integrally, in particular integrally in terms of material. In the first exemplary embodiment, the wheel rim 4 furthermore has an integrally formed insertion bevel 25 which, as seen in a direction parallel to the axis of rotation 7 of the running wheel, is arranged on a side of the second stop surface 9 that faces away from the press fit 6. The insertion bevel 25 facilitates the pushing of the hub 5 into the wheel rim 4 and makes it possible to center the hub 5 in relation to the wheel rim 4. In the first exemplary embodiment, it is provided that the insertion bevel 25 is arranged on the wheel rim 4 adjacent to the second stop surface 9.

[0066] In the first exemplary embodiment, the press fit outer surface 21 of the hub 5 is conical in regions, cf. FIG. 4. In the operating state of the running wheel 1, 2, a largest outside diameter 20 of the press fit outer surface 21 is adjacent to the second stop surface 9 of the wheel rim 4, cf. FIGS. 4 and 5. The outside diameter 20 here is measured in the radial direction with respect to the axis of rotation 7 of the running wheel. An angle 32 of the cone 28, i.e. of the conical region of the press fit outer surface 21, is advantageously more than 1 and less than 10. In the exemplary embodiment, the angle 32 is 5. The press fit inner surface 22 of the wheel rim 4 has an internal cone 29 interacting with the cone 28, at least in an operating state of the running wheel 1, 2. In the exemplary embodiment, the inner cone 29 is directly adjacent to the second stop surface 9 of the wheel rim 4, cf. FIG. 5. Irrespective of the fact that, in the first exemplary embodiment, the press fit outer surface 21 of the hub 5 is conical in regions, the remaining press fit outer surface 21 is in the shape of a circular cylinder jacket. The same is true of the press fit inner surface 22 which, apart from the inner cone 28, is in the shape of a circular cylinder jacket.

[0067] The press fit outer surface 21 of the hub 5 and the press fit inner surface 22 of the wheel rim 4, as is preferred, run in an encircling manner in the circumferential direction with respect to the axis of rotation 7 of the running wheel, i.e. over 360, in the first exemplary embodiment.

[0068] In the case of the running wheel 1, 2 of the first exemplary embodiment, i.e., for example, a running wheel 1, 2 with a diameter 15 of the tread 14 of 630 mm, an oversize of the press fit 6 is advantageously between 0.2 mm and 0.4 mm. That is to say, the press fit outer surface 21 of the hub 5 has an outside diameter larger by the specified oversize than the press fit inner surface 22 of the wheel rim 4. In the case of a comparable running wheel according to the prior art, the corresponding oversize is between 0.6 mm and 1 mm, and is therefore larger at least by the factor of 2 than in the case of the running wheel 1, 2 according to the invention. Owing to the significant reduction in the oversize in the case of the running wheel 1, 2 according to the invention, the supporting capacity can be increased in comparison to the prior art and the susceptibility of the running wheel 1, 2 to wear can be considerably reduced. Furthermore, the required pressing-in forces are correspondingly reduced.

[0069] A method according to the invention for producing the running wheel 1, 2 of the first exemplary embodiment will now be explained with reference to FIGS. 4 and 5. The hub 5 of the running wheel 1, 2 is pushed in the first direction 17 into the wheel rim 4. As the hub 5 is being pushed in, the second stop surface 9 is deformed elastically. That is to say, the second stop surface 9 is ineffective during the pushing in of the hub 5. In a completely pushed-in joining state, the hub 5 is in contact with the first stop surface 8, cf. FIG. 4, wherein the second stop surface 9 at least substantially takes up its original shape and forms the second form fit and, furthermore, blocks the relative movement of the hub 5 in the second direction 18 in relation to the wheel rim 4. In this context, substantially means that the second stop surface 9 may be subject to a small amount of wear as the hub 5 is being pushed into the wheel rim 4. However, it is essential that the stop surface 9 establishing the second form fit is effective in the joining state and blocks the relative movement of the hub 5 in relation to the wheel rim 4 in the second direction. The taking up of the original shape of the second stop surface 9 could also be referred to as elastic snapping back. As can easily be visualized in the overview of FIGS. 4 and 5, the cone 28 and the inner cone 29 advantageously lie over the full surface area against each other in the joining state.

[0070] The connection between the hub 5 and the wheel rim 4 can be released again, wherein, for example, the first form fit or the second form fit can then be removed by turning, and the connection is released by pressing the hub 5 out of the wheel rim 4. Subsequently, a new wheel rim 4 could in turn be used for connection to the hub 5. This makes it possible, for example, to replace a worn wheel rim 4 of the running wheel 1, 2.

[0071] A second exemplary embodiment is shown in FIGS. 6 and 7. The structural design of the running wheel 1, 2 with shaft 3, wheel rim 4 and hub 5 has numerous similarities to the first exemplary embodiment, and therefore, in the explanations regarding the second exemplary embodiment, reference is primarily made to the differences over the first exemplary embodiment. Apart from the differences cited below, the explanations regarding the first exemplary embodiment also apply in the second exemplary embodiment.

[0072] The second exemplary embodiment shows what is referred to as a shrink fit. In order to form a shrink fit, the components which are to be joined are brought to different temperatures. For example, it is possible to keep the hub 5 at room temperature and to heat the wheel rim 4 in an oil bath to an extent such that joining of the hub 5 into the wheel rim 4 with joining play is possible. By cooling the wheel rim 4, the wheel rim 4 is shrunk onto the hub 5. The formation of a shrink fit is known in general in the region of mechanical engineering.

[0073] In the second exemplary embodiment, it is provided that the press fit outer surface 21 of the hub 5 is in the shape of a circular cylinder jacket. The mating surface of the wheel rim 4, i.e. the press fit inner surface 22 of the wheel rim 4, is also in the shape of a circular cylinder jacket.

[0074] In the second exemplary embodiment, it is provided that the insertion bevel 25 is arranged spaced apart from the second stop surface 9 with respect to the axis of rotation 7 of the running wheel. However, this is not compulsory. The insertion bevel 25 could also be adjacent to the stop surface 9, as is shown in the first exemplary embodiment.

[0075] The method for producing the running wheel 1, 2 according to the second exemplary embodiment can in principle take place analogously to the above-described method for producing the running wheel 1, 2 according to the first exemplary embodiment. In addition, before the hub 5 is pushed into the wheel rim 4 heating of the wheel rim 4, or cooling of the hub 5 advantageously takes place. As the hub 5 is being pushed into the wheel rim 4, it is also provided, in the case of the second exemplary embodiment, that the second stop surface 9 is ineffective. In a completely pushed-in joining state, the hub 5 is in contact with the first stop surface 8, cf. FIG. 4, wherein the second form fit at least substantially takes up its original shape and the second stop surface 9 establishing the second form fit furthermore blocks the relative movement of the hub 5 in relation to the wheel rim 4 in the second direction 18. The connection can be released analogously to the first exemplary embodiment. As assistance, the wheel rim 4 could be heated before the hub 5 is pushed out.

[0076] FIGS. 8 to 11 illustrate a third exemplary embodiment of a running wheel 1, 2 according to the invention. Apart from the differences cited below, the explanations regarding the first and second exemplary embodiment also apply in the third exemplary embodiment.

[0077] It is also provided in the case of the running wheel 1, 2 shown in FIGS. 8 to 11 that the connection has a second form fit which is established by a second stop surface 9 and blocks the relative movement of the hub 5 in relation to the wheel rim 4 in a second direction 18 opposed to the first direction 17. The press fit 6 according to the third exemplary embodiment can be designed as a longitudinal interference fit or as a shrink fit. Analogously to the second exemplary embodiment, the press fit outer surface 21 of the hub 5 and the press fit inner surface 22 of the wheel rim 4 are in the shape of a circular cylinder jacket, cf. FIG. 11.

[0078] In contrast to the previously mentioned exemplary embodiments, it is provided, in the case of the running wheel 1, 2 according to the third exemplary embodiment, that said running wheel has an additional or separate securing device 10, wherein the second stop surface 9 is arranged on the securing device 10.

[0079] It is provided in the third exemplary embodiment that the securing device 10 comprises a flange ring 12 which is of encircling design in the circumferential direction and has the stop surface 9. The securing device 10 furthermore has connecting elements, in particular screws 13, for fastening the flange ring 12 to the wheel rim 4. As a result, it is possible for the securing device 10 to be able to be fastened to the wheel rim 4 so as to be releasable again without destruction.

[0080] FIGS. 12 to 14 show an alternative embodiment of a running wheel 1, 2 with a securing device 10. With regard to the design of the press fit 6, reference is made to the explanations regarding the exemplary embodiments cited above. An interference or shrink fit for forming the press fit can also be realized in the fourth exemplary embodiment.

[0081] The running wheel 1, 2 of the fourth exemplary embodiment has a securing device 10 designed as a securing ring. Securing rings of this type are also referred to as a grooved ring. For this purpose, a groove 11 is advantageously formed on the wheel rim 4, cf. FIG. 14. It is provided, at least in the operating state of the running wheel 1, 2, that the securing ring engages in the groove 11 formed on the wheel rim 4. The securing device 10, which is designed as a securing ring, according to the fourth exemplary embodiment, has the second stop surface 9.

[0082] The securing ring is fastenable in a simple manner to the wheel rim 4 so as to be releasable again without destruction. In the exemplary embodiment shown, the securing ring has installation aids 30 which are designed as through bores and permit installation of the securing ring with a commercially available tool, see FIG. 12. The securing ring can be elastically deformed for the mounting and removal, as is known per se, wherein, during the elastic deformation, the outer circumference of the securing ring is reduced such that the latter can be inserted into the groove 11 or removed therefrom.

[0083] In contrast to the first two exemplary embodiments, it is provided, in the third and fourth exemplary embodiments, that the second form fit is secured only by fastening the securing device 10 to the wheel rim 4.

[0084] In principle, all of the connections, which are illustrated in the first four exemplary embodiments, between the hub 5 and the wheel rim 4 can also be transferred to the connection between the shaft 3 and the hub 5, i.e. to a shaft-hub connection. In particular, a securing device 10 having the second stop surface can also be provided for the connection between the shaft 3 and the hub 5. A separate illustration of these embodiments has been omitted. However, it is clear to a person skilled in the art that a securing device 10 which is designed as a securing ring then engages in a groove formed on the shaft 3, or a securing device 10 which has a flange ring is fastenable or is fastened to the shaft 3.

[0085] FIGS. 15 to 18 illustrate a fifth exemplary embodiment of a running wheel 1, 2 according to the invention. Apart from the differences cited below, the explanations regarding the preceding exemplary embodiments, in particular regarding the second exemplary embodiment, also apply in the case of the fifth exemplary embodiment. FIGS. 15 to 18 show an example of a shrink fit for forming a press fit 6 between a shaft 3 and a hub 5.

[0086] In the case of the fifth exemplary embodiment according to the invention, it is provided that the press fit 6 connects a press fit inner surface 24, which faces the axis of rotation 7 of the running wheel, of the hub 5 and a press fit outer surface 23, which faces away from the axis of rotation 7 of the running wheel, of the shaft 3 to each other in a force-fitting manner, cf. FIGS. 17 and 18. The shaft 3 here has the first stop surface 8 and the second stop surface 9. The first stop surface 8 and the second stop surface 9 and the press fit outer surface 23 of the shaft 3 are connected to one another integrally in terms of material.

[0087] The press fit inner surface 24 of the hub 5 is designed in the shape of a circular cylinder jacket. The same is true of the press fit outer surface 23 of the shaft 3. In this exemplary embodiment, the shaft 3 has an insertion bevel 25 analogously to the first and second exemplary embodiment, wherein the insertion bevel 25 is integrally formed on the shaft 3. The insertion bevel 25 is arranged on a side of the second stop surface 9 that faces away from the press fit 6, as seen in a direction parallel to the axis of rotation 7 of the running wheel, cf. FIG. 18.

[0088] The connection between the shaft 3 and the hub 5 has a first form fit which is established by the first stop surface 8, wherein the first form fit blocks the relative movement of the shaft 3 in relation to the hub 5 in a first direction 17 running parallel to the axis of rotation 7 of the running wheel 1, 2, cf. FIG. 18. Furthermore, the connection between the shaft 3 and the hub 5 has the second stop surface 9 which secures the second form fit. The second form fit blocks the relative movement of the shaft 3 in relation to the hub 5 in a second direction 18 opposed to the first direction 17. As a result, the relative movement of the shaft 3 in relation to the hub 5 with respect to directions parallel to the axis of rotation 7 of the running wheel is prevented.

[0089] In the case of a method for producing a running wheel 1, 2 according to the fifth exemplary embodiment, it can be provided that the shaft 3 is pushed in the first direction 17 into the hub 5, wherein the second stop surface 9 is elastically deformed during the pushing in of the shaft 3, and, in order to form the second form fit in a completely pushed-in joining state, in which the shaft 3 is in contact with the first stop surface 8, the second stop surface 9 at least substantially takes up its original shape and therefore blocks the relative movement of the shaft 3 in relation to the hub 5 in the second direction 18.

[0090] FIG. 19 illustrates a further alternative embodiment of a running wheel 1, 2 according to the invention. The press fit 6 is realized here as an interference fit and substantially corresponds to the transfer of the longitudinal interference fit of the first exemplary embodiment to the connection between the shaft 3 and the hub 5. Apart from the differences cited below, the explanations regarding the preceding exemplary embodiments, in particular regarding the fifth exemplary embodiment, also apply in the case of the sixth exemplary embodiment.

[0091] The press fit inner surface 24 of the hub 5 of the sixth exemplary embodiment of a running wheel 1, 2 is conical at least in regions. That is to say, the press fit inner surface 24 of the shaft 3 is designed in regions as an inner cone 29, cf. FIG. 19. In an operating state of the running wheel 1, 2, a smallest inside diameter 19 of the press fit inner surface 24 is adjacent to the second stop surface 9 of the shaft 3. The smallest inside diameter 19 of the press fit inner surface 24 should be measured in the radial direction with respect to the axis of rotation 7 of the running wheel. The shaft 3 has the corresponding mating contour, i.e. a cone 28 which is adjacent to the second stop surface 9.

[0092] In a departure from the exemplary embodiments, which are illustrated in the figures, of running wheels 1, 2 having a circular-cylindrical tread 14, it is also conceivable and possible for the wheel rim 4 of a running wheel 1, 2 according to the invention to have an encircling groove. The flanks bounding the groove, as seen with respect to a direction parallel to an axis of rotation 7 of the running wheel, are generally also referred to as wheel flanges. Embodiments of running wheels having only one wheel flange are also conceivable and possible within the scope of the invention.

KEY TO THE REFERENCE NUMBERS

[0093] 1 Running wheel

[0094] 2 Running wheel

[0095] 3 Shaft

[0096] 4 Wheel rim

[0097] 5 Hub

[0098] 6 Press fit

[0099] 7 Axis of rotation of the running wheel

[0100] 8 First stop surface

[0101] 9 Second stop surface

[0102] 10 Securing device

[0103] 11 Groove

[0104] 12 Flange ring

[0105] 13 Screw

[0106] 14 Tread

[0107] 15 Diameter

[0108] 16 Crane

[0109] 17 First direction

[0110] 18 Second direction

[0111] 19 Inside diameter

[0112] 20 Outside diameter

[0113] 21 Press fit outer surface

[0114] 22 Press fit inner surface

[0115] 23 Press fit outer surface

[0116] 24 Press fit inner surface

[0117] 25 Insertion bevel

[0118] 26 Running rail

[0119] 27 Running rail

[0120] 28 Cone

[0121] 29 Inner cone

[0122] 30 Installation aid

[0123] 31 Trolley

[0124] 32 Angle