1. A ground-working machine (10), such as a road milling machine, a reclaimer, a stabilizer or a surface miner, comprising a support structure (30) and a working assembly (28) for ground working, which is mounted on the support structure (30) so as to be rotatable about a drive axis (A) relative to the support structure (30), wherein the drive axis (A) defines an axial direction (A1, A2) running along the drive axis (A), a radial direction running orthogonally thereto and a circumferential direction (U1, U2) running around the drive axis, wherein, in a reference state in which the working assembly (28) is ready to be rotated about the drive axis (A), the working assembly (28) is mounted on a drive axial end region (28a) so as to be rotatable on a first support structure region (30c) by means of a first rotary bearing (57), and is rotatably supported on a second bearing region (30a) by means of a rotary bearing arrangement (77) at a fixing-mechanism axial end region (28b) remote from the drive-mechanism axial end region (28a) in the axial direction (A2), wherein the rotary bearing arrangement (77) has a second rotary bearing (76), an assembly-side bearing configuration (74a) connected to the working assembly (28) and a structure-side bearing configuration (86) connected to the support structure (30), wherein the fixing-mechanism axial end region (28 b; 128b) has one of a bearing pin (74a) and a bearing sleeve (86; 186) as the assembly-side bearing configuration (74a) and the second support-structure region (30a) has the respective other of a bearing pin (74a) and a bearing sleeve (86; 186) as the structure-side bearing configuration (86; 186), wherein the bearing sleeve (86; 186) surrounds the bearing pin (74a) in a reference state, wherein the bearing pin (74a) and the bearing sleeve (86; 186) are arranged so as to be rotatable about the drive mechanism axis (A) relative to a second bearing region (30a) in the reference state, and wherein the bearing pin (74a) and the bearing sleeve (86; 186) can be moved away from one another in the axial direction as required and can thus be separated from one another for maintenance, retrofitting and installation purposes,

characterized in that the working assembly (28) has a driving formation (88; 188) with a driving surface (88 a; 188a) directed in a first circumferential direction (U1), and the structure-side bearing formation (86; 186) has a driving counter formation (90; 190) with a driving counter surface (90a) directed in a second circumferential direction (U2) opposite to the first circumferential direction, wherein in a reference state the driving surface (88 a; 188a) and a movement space (92, 94) of the driving counter surface (90a) about the drive mechanism axis (A) coincide.

2. The floor-processing machine (10) according to claim 1, characterized in that the driving surface (88 a; 188a) and the driving surface (90a) are in abutting engagement transmitting force in the circumferential direction (U1, U2).

3. A machine (10) according to claim 1 or 2, characterized in that the driving counter-formation (90; 190) has a recess (90 d; 190d) or/and a projection (90 c; 190 c).

4. A machine (10) as claimed in claim 3, characterized in that the driving counter formation (90; 190) has a projection (90 c; 190c) which is inserted into a recess (90 d; 190d) in the bearing formation (86; 186) on the construction side and is fixed there in a manner specified so as to be releasable.

5. A floor processing machine (10) according to any one of the preceding claims, characterized in that the working assembly (28) has a drive configuration (46) which is supported on the first support structure region (30c) on the drive means axial end region (28a) rotatably about the drive axis (a) by means of the first rotary bearing (57) and projects axially away from the first support structure region (30c), wherein the drive configuration (46) carries the carrying configuration (88).

6. A floor processing machine (10) according to claim 5, characterized in that the drive configuration (46) has an end face (60c) directed in the axial direction (A1) on its longitudinal end (46b) remote from the first rotary bearing (57), wherein the end face (60c) carries the driving configuration (88).

7. A machine (10) according to claim 5 or 6, wherein the drive configuration (46) accommodates the milling roller (32; 132) in a manner that can be disengaged, wherein the drive configuration (46) has a projecting transmission member (80, 80 ') for transmitting a torque to the milling roller (32; 132) arranged on the drive configuration (46), wherein at least one of the transmission members (80') has a driving configuration (88).

8. A ground processing machine (10) as claimed in any one of claims 5 to 7, characterized in that the drive configuration (46) has a milling roller (32; 132) which is coaxial with the drive configuration (46) in a reference state, wherein the milling roller (32; 132) comprises a milling roller housing (42) on the outside of which a milling chisel holder (33a) is arranged, which is configured to accommodate a milling chisel (33b), wherein the milling roller (32) has a connecting structure (73) running transversely to the drive axis (A) in a fixing means axial end region (28b), wherein a driving configuration (88) carried by the drive configuration (46) runs axially past the connecting structure (73; 173) or through the connecting structure (73; 173), from which the connecting structure (73; 173) extends to a structure-side bearing formation (86; 186).

9. A ground working machine (10) according to any one of the preceding claims, characterized in that the working assembly has a milling roller (132), wherein the milling roller (132) comprises a milling roller housing on the outside of which a milling chisel holder is arranged, which milling chisel holder is configured to accommodate a milling chisel, wherein the milling roller (132) carries the carrying formation (188).

10. A machine (10) according to claim 8 or 9, wherein the milling drum (132) has in the securing means axial end region (128b) a connecting structure (173) extending transversely to the drive means axis (a) which connects the milling drum cover with a bearing formation on the assembly side, wherein the connecting structure (173) carries the carrying formation (188).

11. A floor processing machine (10) according to any one of the preceding claims, characterized in that a driving formation (88; 188) has an adjustment face (88 b; 188b) which is directed axially away from the drive means axial end region (28a) in the reference state, and the driving counter formation (90; 190) has an adjustment counter face (90b) which is directed axially toward the drive means axial end region (28a) in the reference state, wherein the adjustment face (88 b; 188b) is inclined relative to a reference face (BE) orthogonal to the drive means axis (A) such that the adjustment face (88 b; 188b) approaches the drive means axial end region (28a) in the second circumferential direction (U2) with increasing circumferential spacing from the driving face (88 a; 188a), and the adjustment counter face (90b) is opposite to the reference face (BE) orthogonal to the drive means axis (A) ) Is inclined such that the adjustment counter surface (90b) is distanced from the drive mechanism axial end region (28a) in the first circumferential direction (U1) with increasing circumferential distance from the driving counter surface (90 a).

12. A floor processing machine (10) according to claim 11, characterized in that the adjustment surface (88 b; 188b) is inclined at an angle (α) of at least 25 ° relative to the reference surface (BE) or/and the adjustment counter surface (90b) is inclined at an angle (β) of at least 25 ° relative to the reference surface (BE), wherein preferably the inclination angle (α) of the adjustment surface (88 b; 188b) and the inclination angle (β) of the adjustment counter surface (90b) are equally large in value.

13. A machine (10) as claimed in any of the preceding claims, characterized in that the second support structure area (30a) and the structure-side bearing formation (86; 186) are pivotable away from the first support structure (30c) about a pivot axis which is at least inclined, preferably orthogonal, with respect to the drive mechanism axis (A) starting from the reference state.

14. A floor processing machine (10) according to any of the preceding claims, characterized in that the support structure (30) is connected with a frame (12) of the floor processing machine (10) in the reference state.

15. Support structure (30), in particular a milling roller box (30), for a floor processing machine (10) according to any one of the preceding claims, the support structure (30) having a plurality of connection configurations for the purpose of being connected in a defined manner detachably to a machine frame (12) of the floor processing machine (10), wherein the support structure (30) comprises a working assembly (28) for floor processing, which is rotatably supported on the support structure (30) relative to the support structure (30) about a drive axis (A), wherein the drive axis (A) defines an axial direction (A1, A2) running along the drive axis (A), a radial direction running orthogonally thereto and a circumferential direction (U1, U2) running around the drive axis (A), wherein, in a reference state in which the working assembly (28) is ready to be rotated about the drive axis (A), the working assembly (28) is rotatably mounted on a first mounting region (30c) at a drive-mechanism axial end region (28a) by means of a first rotary bearing (57) and on a second mounting region (30a) at a fastening-mechanism axial end region (28b) remote from the drive-mechanism axial end region (28a) in the axial direction (A1) by means of a rotary bearing arrangement (77), wherein the rotary bearing arrangement (77) has a second rotary bearing (76), a component-side bearing configuration (74a) connected to the working assembly (28) and a structure-side bearing configuration (86; 186) connected to the mounting structure (30), wherein the fastening-mechanism axial end region (28 b; 128b) has one of a bearing pin (74a) and a bearing sleeve (86; 186) as the component-side bearing configuration (74a), and the second bearing structure region (30c) has the respective other of the bearing pin (74a) and the bearing sleeve (86; 186) as a structure-side bearing structure (86; 186), wherein the bearing sleeve (86; 186) surrounds the bearing pin (74a) in a reference state, wherein the bearing pin (74a) and the bearing sleeve (86; 186) can be arranged in the reference state about the drive axis (A) in a rotatable manner relative to the second bearing structure region (30a), and wherein the bearing pin (74a) and the bearing sleeve (86; 186) can be moved away from one another in the axial direction as required and can thus be separated from one another for maintenance, retrofitting and installation,

characterized in that the working assembly (28) has a driving formation (88; 188) with a driving surface (88 a; 188a) directed in a first circumferential direction (U1), and the structure-side bearing formation (86; 186) has a driving counter formation (90; 190) with a driving counter surface (90a) directed in a second circumferential direction (U2) opposite to the first circumferential direction, wherein in a reference state the driving surface (88 a; 188a) and a movement space (92, 94) of the driving counter surface (90a) about the drive mechanism axis (A) coincide.

Background

A ground-working machine of this type in the form of a road milling machine and a support structure of this type in the form of a milling roller box are known from EP 3406798a 1.

The second support structure region of the known floor-working machine as a service flap or service door of the milling roller magazine can be pivoted about a pivot axis which is substantially parallel to the yaw axis of the floor-working machine in order to achieve accessibility to the milling rollers or the drive configurations supporting the milling rollers accommodated in the milling roller magazine by pivoting the service door, the milling rollers or the drive configurations being part of the known working assembly. When the service door is opened, the milling roller can be pulled out of the drive configuration supporting it in the axial direction and replaced, for example, by another milling roller.

The bearing pin and the bearing bush are designed such that, when the service door is opened, the bearing arrangement on the structure side, in the known case the bearing bush, is pulled out axially from the bearing arrangement on the assembly side, in the known case the bearing pin, by a pivoting movement of the service door. Due to this pivoting movement, the pull-out movement of the bearing sleeve from the bearing pin is not a pure axial relative movement, but rather the main axial translational component of the pull-out movement is superimposed on the numerically smaller radial translational and rotational movement components of the bearing sleeve.

Since the bearing configurations on the structure side and the bearing configurations on the module side of the rotary bearing device can be advantageously easily and quickly separated, the bearing configurations are only coupled in a frictional manner with one another in the reference state in order to jointly perform a rotary movement about the drive axis. During ground-working operation of the ground-working machine, in certain operating situations, temporarily increased radial loads of the rotary bearing of the work module, for example when starting the work module or/and when placing the work module on the ground to be worked or/and when the engagement depth of the work module orthogonal to the drive axis changes, high loads can occur on the rotary bearing arrangement, such that the bearing pattern on the structure side and the bearing pattern on the module side undesirably rotate relative to one another. Such relative rotation that occurs can cause undesirably high wear on at least one of the bearing configurations.

Disclosure of Invention

The object of the present invention is therefore to improve the mounting of working components on a rotary bearing arrangement having bearing configurations which can be separated from one another as intended, and thereby to avoid the increased wear which is possible.

The invention achieves this object in a ground-working machine of the type mentioned at the outset in that the working assembly has a driving formation with a driving surface which points in a first circumferential direction about the drive axis, and the structure-side bearing formation has a driving counter formation with a driving counter surface which points in a second circumferential direction about the drive axis, which is opposite to the first circumferential direction, wherein, in the reference state, the driving surfaces and the driving counter surfaces coincide in terms of the movement space about the drive axis.

The invention is achieved by the same means on a machine support structure for such ground working of the type mentioned at the outset, namely a support structure according to claim 15. Since the invention is implemented on a support structure of a floor-processing machine, which is detachably connected to the floor-processing machine as intended, the following description and refinements of the invention apply both to the floor-processing machine and to the support structure itself. The support structure is preferably a casing which surrounds the working assembly on several sides, for example a known milling roller box which has the milling roller or at least one drive configuration for the purpose of being able to be coupled detachably to the milling roller, which is mounted so as to be rotatable about a drive axis. In principle, however, the support structure may be any structure that supports the first rotary bearing and the rotary bearing arrangement.

If no specific explanation is explicitly given to the contrary, the invention is described in the initially defined reference state in which the working assembly is ready for rotation about the drive axis.

Maintenance, retrofitting and installation purposes, for which the bearing pin and the bearing sleeve previously could be axially distanced from each other, involve maintenance or/and retrofitting or/and installation of components of the second rotary bearing other than the rotary bearing arrangement. The second rotary bearing may be or include a rolling bearing or a plain bearing. The objects given above with respect to maintenance, retrofitting and mounting relate to work on the work module, for example to remove a milling roller from a drive configuration or/and to mount a milling roller to a drive configuration.

As a result of the above-described driving formations and driving counter-formations being arranged with faces directed in opposite circumferential directions about the drive mechanism axis: the driving surface and the driving counter surface (the movement spaces of which coincide around the drive axis) are not moved past one another along a circumferential path around the drive axis. In this way, when the bearing configuration on the structure side of the rotary bearing device and the bearing configuration on the module side are connected, even if the driving surfaces and the driving counter surfaces are at a maximum distance from one another in the circumferential direction about the drive axis, a relative rotation of less than a full revolution of the two bearing configurations is only possible until the driving surfaces come into abutting engagement with the driving counter surfaces and, owing to the positive-locking engagement achieved thereby, the bearing configurations of the rotary bearing device rotate synchronously and without a relative rotation about the drive axis. If a relative rotation of less than 360 ° is desired, a plurality of driving formations and/or driving counter-formations can be arranged distributed over the circumference. According to a development of the invention, a plurality of driving configurations and driving counter configurations can also be arranged in order to ensure uniform loading of the configurations. Preferably, the plurality of driving formations or/and the driving counter-formations are arranged equidistantly in the circumferential direction about the drive mechanism axis, so that no care needs to be taken about the relative orientation of the driving formations and the driving counter-formations with respect to one another when establishing the reference state. Due to the preferably equidistant arrangement, the angular spacing between two adjacent driving formations or driving counter-formations is an integer part of 360 °.

The movement space of one of the surfaces is the space through which the driving surface or one of the driving surfaces passes during rotation about the drive axis.

Because the path of the driving torque usually extends from the working assembly to the bearing configuration on the construction side and also because the working assembly can usually only be driven in rotation, the first circumferential direction in which the driving surface is directed is the circumferential direction in which the working assembly is driven in rotation.

The floor-processing machine preferably has a drive motor as a rotary drive for the working module, from which drive motor a drive torque can be transmitted to the working module. In order to drive the working assembly with a suitable rotational speed or a suitable rotational speed range, at least one transmission, in particular a planetary transmission, can be provided in the torque transmission path from the drive motor to the working assembly. The drive train from the drive motor to the working assembly can have a traction drive, in particular a belt drive, and a so-called planetary drive, preferably in the stated order along the torque transmission path, for reasons of installation space. In order to provide sufficient hydraulic energy, a pump distribution gear can additionally be arranged in the drive train, preferably between the drive motor and the traction gear. The last transmission, in particular the planetary transmission described above, in the torque transmission path from the drive motor to the working assembly can be arranged at least partially in a drive configuration which is continuously rotatably supported by means of the first rotary bearing of the support structure.

The gear unit itself can have a first rotary bearing as a planetary gear unit. The first part of the gear mechanism housing can be fixed in position on the support structure, and the second part of the gear mechanism housing can be mounted on the first gear mechanism housing part so as to be rotatable relative to the first gear mechanism housing part about the drive mechanism axis. The second gear mechanism housing part is coupled in a rotationally fixed manner to the drive configuration or/and is part of the drive configuration.

The first rotary bearing is therefore preferably a so-called fixed bearing of the rotary support of the working assembly. As a fixed bearing, the first rotary bearing has no axial play with respect to the components connected thereto, said components being: a first support structure area and a task module. The fixed bearing is usually kept unchanged during its working life, apart from unavoidable wear on the floor-working machine or on the supporting structure. The rotary bearing arrangement forms a rotationally mounted floating bearing of the working assembly, which allows a defined axial relative movement between the second support structure region and the working assembly. The rotary bearing device is even as intended for repeatedly disconnecting and reconnecting its above-described bearing configuration.

Preferably, the bearing configuration on the structure side is a bearing sleeve. In order to keep the number of components low, the bearing sleeve can in principle be the inner ring of the second rotary bearing, which is preferably designed as a rolling bearing, but this is not preferred because of the high hardness and the associated poor processability of the inner ring of the rolling bearing. Preferably, the bearing configuration on the structure side is a bearing sleeve which is indirectly or directly supported by the inner ring of the second rotary bearing, which is preferably designed as a rolling bearing. Since the bearing sleeve is preferably pushable by a pivoting movement of the second bearing region onto the bearing pin forming the bearing pattern on the component side and can be pulled off therefrom, the bearing sleeve is preferably configured with a recess which narrows in the direction away from the axial end region of the drive mechanism. Therefore, the bearing sleeve is preferably substantially funnel-shaped. For the same reason, the bearing pin, which preferably forms the bearing configuration on the component side, is preferably configured so as to taper towards its projecting longitudinal end.

The second rotary bearing is preferably arranged functionally between the second support structure region (one end) and the two bearing configurations (the other end), whereby the two bearing configurations can be rotated relative to the second support structure region.

In order to avoid undesirable auxiliary forces between the driving configuration and the driving counter configuration during ground processing, it is preferred that at least one of the driving surface and the driving counter surface is configured flat, the auxiliary force having a component orthogonal to an imaginary peripheral circular path through the contact area of the driving surface and the driving counter surface. The planar surface lies in a plane containing the axis of the drive mechanism, whereby the planar surface is oriented orthogonally to its motion trajectory at any time during rotation about the drive mechanism axis. The respective other of the driving surface and the driving-fit opposite surface can have a convexly curved configuration lying on a flat surface, for example as a spherical or elliptical crown, or can also be preferably flat for reasons of simple manufacture and as low a surface pressure as possible. In order to avoid an undesirably high load due to the surface pressure at the contact point between the driving surface and the driving counter surface, the driving surface and the driving counter surface preferably engage in a surface-to-surface manner against one another, and thus are parallel to one another during the abutting engagement. Preferably, therefore, the respective other flat surface of the driving surface and the driving counter surface is also in a plane containing the drive axis.

Although a spacing between the driving surfaces and the driving counter surfaces can be produced immediately after the bearing formation has been brought into connection with one another along a peripheral circular path about the drive axis, it is preferred if the driving surfaces and the driving counter surfaces are in an operating condition in a force-transmitting abutting engagement in the circumferential direction. This operating condition advantageously occurs automatically when relative rotation occurs between the bearing configurations if it was not previously present.

In order to reliably establish the abovementioned torque-transmitting abutting engagement between the driving surfaces and the driving counter surfaces, the driving counter formations can have recesses into which the projections of the driving formations engage. Alternatively, the driving counter formation may have a projection which engages or can form an abutting engagement with a projection or recess of the driving formation. As a further alternative, the driving counter-formation can have a recess and a projection, for example, which is inserted into a recess of the bearing formation on the structure side when the driving counter-surface is formed on a separate projection element. The projecting element with the snap-fit counter surface is therefore anchored as permanently and positionally fixed as possible to the bearing structure on the structure side. The protruding member with the snap-fit opposite face may then protrude from the recess over the surrounding surface of the bearing formation.

The driving counter formation as a projection or recess can be formed in one piece in combination with the bearing formation on the structure side, for example by deformation production and optionally subsequent reworking or as a recess only by appropriate machining. More flexible and particularly more suitable for retrofitting, the driving counter formation can be connected as a projecting element to the bearing formation by a joining process. The driving counter formation can thereby be connected to the bearing formation material, in particular by welding, if appropriate also by soldering or adhesive bonding, which results in a very high connection strength. Alternatively, the projecting element forming or included in the driving counter-form (projecting element having the driving counter-face) is connected in a defined manner to the bearing form in a releasable manner, for example by a screw connection, so that the projecting element having the driving counter-face can be replaced by an unworn projecting element when the predetermined wear state is reached.

The driving counter surface, which can transmit high torques and at the same time can be easily replaced, can be obtained in that the driving counter formation has a projection, in particular a projecting member, which is inserted into a recess of the bearing formation on the structure side and is fixed in place so as to be able to be detached. Preferably, the projection or the projecting member is connected by means of a screw with a bearing formation on the structure side in a fixed, but at the same time detachable, connection.

The above statements with regard to the driving partner configuration also apply, where appropriate, to the driving configuration. The driving formations may also comprise protrusions or/and recesses. Correspondingly, the driving arrangement can also comprise a projecting element which is accommodated in a recess of the element carrying it, so that as high a torque as possible can be transmitted from the driving arrangement normally used for driving to the driving counter-arrangement normally driven.

The driving means can also be connected to the component carrying it in a manner that can be detached, i.e. for example by screwing, or in a manner that cannot be detached, i.e. for example by welding, soldering, gluing, etc.

The main difference between the driving engagement and the driving counter-engagement is that the driving counter-engagement is arranged on the bearing arrangement on the structure side so that it rotates synchronously with the working assembly, but the driving engagement need not necessarily be arranged on the bearing arrangement on the assembly side, but can be arranged on any suitable point of the working assembly for movement therewith. Of course, the driving formation can be arranged on the bearing formation on the component side.

As already mentioned, the working assembly can have a drive configuration which is mounted on the first bearing region on the axial end region of the drive means so as to be rotatable about the drive means axis by means of a first rotary bearing and projects axially away from the first bearing region. The working device, for example a milling roller, can be pushed axially from the side of the axial end region of the fastening means onto the drive configuration and connected for common rotation therewith. The working device can also be pulled out or pushed out of the drive configuration in the axial direction in the opposite direction.

The working assembly may have only a drive configuration.

Since the drive structure is permanently supported in a rotatable manner on the first support structure region, the drive structure advantageously carries the carrying structure. The drive configuration is thus always present on the support structure and thus on the floor-processing machine with the support structure.

In the reference state, the second support structure region is usually arranged axially at a distance from the longitudinal end of the drive configuration which projects from the first support structure region. In order to be able to ensure, with little construction effort, that the driving surfaces of the driving means arranged on the drive means can be brought into torque-transmitting engagement with the driving counter surfaces of the bearing means on the construction side, it is advantageous if the drive means has an end face directed in the axial direction at its longitudinal end remote from the first rotary bearing, wherein the end face carries the driving means. On the one hand, such an end face provides a sufficiently large surface for arranging the driving configuration. On the other hand, the end face or the end face component having the end face is constructed with sufficient strength to transmit the required torque.

The end face is preferably arranged orthogonally to the drive axis, but this is not essential. The end face pointing in the axial direction can be stepped or/and conically configured radially outward from the drive mechanism axis, wherein preferably half of the opening angle of the end face cone is greater than 45 ° in order to avoid an excessively large axial extension of the end face. In this case, the end face is also always directed predominantly in the axial direction.

The drive configuration can have a tube section, in particular a cylindrical section, whose tube axis or cylinder axis is the drive mechanism axis. At least a part of the above-mentioned transmission means can be arranged in at least a part of the tube section, preferably in a tube section which is closer to the first support structure region than the second support structure region.

The cylindrical section can be partially or preferably completely obscured by the end face member at its protruding longitudinal end remote from the rotary bearing, whereby the drive configuration preferably comprises a basin-like configuration, the bottom of which is formed by the end face member.

As already mentioned, the drive configuration serves for different work tasks, preferably for the defined releasable accommodation of the milling roller. The drive configuration can thus accommodate a plurality of milling rollers in succession in time, which differ in type or/and number or/and arrangement from the ground-material-stripping milling chisel arranged thereon. Thus, the working assembly may include a working configuration and a milling roller.

In order to avoid relative rotation between the drive configuration and the milling roller accommodated by the drive configuration, the drive configuration preferably has projecting transmission members for physically transmitting a torque to the milling roller arranged on the drive configuration. In general, a torque is introduced into the drive configuration from the drive motor of the floor-processing machine in the axial end region of the drive. When the milling roller is arranged in the drive configuration and the working assembly has the drive configuration and the milling roller, the torque transmission path now extends within the working group from the drive configuration to the milling roller.

In order to keep the number of components of the working group as low as possible, it is preferred that at least one of the transmission components has a driving configuration.

In the reference state, in particular in the reference state ready for ground machining, the milling drum accommodated on the drive configuration is arranged coaxially to the drive configuration. The milling roller comprises a milling roller shield which surrounds the drive configuration radially on the outside. In order to transmit the torque from the drive configuration to the milling roller as simply and reliably as possible, the milling roller preferably projects onto the drive configuration at a longitudinal end of the drive configuration remote from the axial end region of the drive mechanism.

When the first rotary bearing is arranged between the two transmission housing parts, the milling roller surrounds the first rotary bearing radially on the outside to achieve a large axial working width and projects axially away from the axial end region of the fastening means.

On the outside of the milling roller housing, a plurality of milling chisel holders are arranged, which are designed to accommodate milling chisels. The milling chisel holder is preferably designed as a milling chisel changing holder with a holder element arranged permanently on the milling roller housing on the housing side and a holder changing element which is connected thereto in a manner that can be detached. Since the milling chisel is subjected to high wear during ground machining operations, the milling chisel is preferably also arranged in the respective milling chisel holder in a replaceable manner. The milling chisel holder is preferably arranged helically on the milling roller housing in order to facilitate transport of the stripped ground material away from the working assembly.

The milling roller is preferably supported in the drive configuration at its longitudinal end closer to the axial end region of the drive mechanism. This is achieved in a particularly simple and stable manner here, since the drive configuration bears on the first support structure region in the axial end region of the drive mechanism, and therefore has a high support strength here due to the small axial projection length from the first support structure region. In order to re-support the milling drum in the drive configuration with an axial spacing relative to the first-mentioned support, the milling drum may preferably have a connecting structure extending transversely to the drive axis in the axial end region of the fastening means. Preferably, the connecting structure is axially adjacent to the end face in the reference state, so that an advantageously large bearing distance is achieved between the two support points of the milling drum. The end face of the drive configuration can have, for example, an axially projecting centering pin on which the milling roller is supported in a form-fitting manner.

The above-mentioned driving formations carried by the drive formations can extend in the axial direction at the connecting structure past or through the connecting structure, whereby the bearing formations project onto the connecting structure towards the structure side. Preferably, a driving formation extending at or through the connecting structure is formed on the above-mentioned transmission member. The section of the transmission member axially coinciding with the connecting structure can thereby transmit a torque from the drive configuration to the milling drum, and the section of the transmission member extending axially beyond the connecting structure towards the second support structure region forms a driving configuration and transmits a torque to the structure-side bearing configuration. Preferably, the driving formation is an axial end region of the transfer member axially protruding from the driving formation. Such a transmission member may be realized, for example, by a protruding peg or pin. The transmission member and the driving structure connected thereto are preferably also arranged in a releasable manner in the drive structure, for example by means of a screw, in particular a screw running centrally through the transmission member.

In addition to or instead of the drive configuration, the milling roller can carry a driving configuration. Since the milling roller can be connected to and disconnected from the drive configuration as a separate structural unit, the present application also relates to a milling roller as described and improved in the present application, which has a driving configuration.

When the milling roller carries the driving means or at least also a driving means, the driving means can then be arranged on the connecting structure. As mentioned above, the connecting structure, which preferably extends transversely, particularly preferably orthogonally, to the drive mechanism axis, can connect the milling roller shell to the bearing configuration on the module side. Preferably, the bearing configuration on the component side is a bearing pin which projects in the axial direction away from the axial end region of the drive means on the side pointing away from the axial end region of the drive means. On the side of the connecting structure facing the axial end region of the drive, a recess can be formed in the region of the bearing pin, into which recess the above-mentioned centering pin projects on the end side of the drive in the reference state.

The working assembly may comprise at least one fixing device, for example one or more fixing screws, by means of which the milling drum is fixed in the reference state in the drive configuration. The milling drum is thereby accommodated in the drive configuration in a manner that is releasable, and the at least one fastening device is also accommodated in the remaining part of the working assembly in a manner that is releasable. The driving means can be arranged or formed on the fastening device, in particular as a fastening screw. If the fastening device in the reference state, in addition to the fastening screw, also has a shim, which is fastened by the fastening screw to the drive structure and/or to the milling drum, the driving member can alternatively or additionally be arranged or formed on the shim.

In order to keep the number of components for forming the working assembly low, the fixing means preferably comprise a fixing screw which is screwed into the above-mentioned centering pin of the drive configuration such that the screw axis of the fixing screw is coaxial in the reference state with the drive mechanism axis.

In particular, if the driving formation is formed on the fastening device, the driving mating formation can then be formed on a component which is formed separately from the bearing sleeve or the inner ring of the second rotary bearing and which is preferably connected to the bearing sleeve or the inner ring of the second rotary bearing in a manner that can be detached.

It is possible that all these components, which are connected to the drive configuration after the bearing sleeve has been pulled out of the bearing pin from the reference state, are part of the working assembly.

In contrast to the case discussed above (in which the driving formation and the driving counter formation are spaced apart from one another in the circumferential direction about the drive axis when the reference state is established), it is also possible for the driving formation and the driving counter formation to coincide with one another in the circumferential direction when the reference state is established. In this case, the coincidence acts as a barrier to the entity preventing the establishment of the reference state or attempting to establish the reference state at full force may damage one of the configurations. In order to avoid such disadvantageous consequences for the floor-working machine or the support structure in the event of a coincidence, the driving arrangement can have an adjustment surface which is axially directed away from the axial end region of the drive in the reference state, and the driving counter arrangement can have an adjustment counter surface which is axially directed toward the axial end region of the drive in the reference state. The adjustment surface is inclined relative to a reference plane orthogonal to the drive mechanism axis such that the adjustment surface approaches the drive mechanism axial end region as the circumferential spacing from the driving surface in the second circumferential direction increases. The adjustment counter surface is inclined relative to a reference plane orthogonal to the drive mechanism axis such that the adjustment counter surface is spaced away from the drive mechanism axial end region with increasing circumferential spacing from the driving counter surface in the first circumferential direction. In the above-described overlapping situation, the driving formation and the driving counter formation are therefore slid past one another in the circumferential direction along their adjustment faces and adjustment counter faces by relative rotation until the second bearing formation can axially approach the first bearing formation, so that a reference state can be established. Under axial pressure, the adjustment surfaces and the adjustment counter surfaces of the bearing configuration on the working assembly and structure side force a short screw relative movement, which takes the drive mechanism axis as the screw axis.

If the inclination of the surfaces (adjustment surface and adjustment counter surface) relative to the reference surface is sufficiently large in value, then no self-locking occurs, but the working assembly and the bearing arrangement on the structure side are moved out of the initially existing overlap condition by the connection process in which the bearing arrangement on the structure side and the bearing arrangement on the assembly side are axially adjacent to one another. For this purpose, it is advantageous if the adjustment surface is inclined at an angle of at least 25 °, preferably at least 30 °, relative to the reference surface, or/and the adjustment counter surface is inclined at an angle of at least 25 °, preferably at least 30 °, relative to the reference surface. In order to provide as planar as possible a contact with low surface pressure between the adjusting surface and the adjusting counter surface, the inclination angles of the adjusting surface and the adjusting counter surface are preferably as large as possible.

As already mentioned above with respect to the prior art, it is preferred according to the invention that the second bearing region and the bearing configuration on the structure side can also be pivoted away from the first bearing structure, starting from the reference state, about a preferably orthogonal pivot axis which is at least curved relative to the drive axis. The pivot axis preferably extends parallel to a yaw axis of the floor treatment machine, which yaw axis extends in the height direction of the floor treatment machine, in order to avoid the effect of gravity on the pivoting movement. The axis of oscillation is at least preferably inclined by not more than 15 ° with respect to the yaw axis. Preferably, the second support structure area is configured as a service door of a jacket, e.g. a milling roller box, enclosing a large part of the working assembly.

Although the support structure may be provided at the construction site in the reference state for connection to the frame of the floor-processing machine, the support structure is preferably connected to such a frame in the reference state. The connection of the support structure to the machine frame is preferably releasable as required, for example by a screw connection or/and an actuator lock by means of at least one form-fitting locking element which can be actuated by the actuator, so that maintenance and, if necessary, repair of the support structure is simplified. However, the support structure can also be connected to the machine frame in a manner that cannot be detached, for example by welding.

Drawings

The present invention is described in detail below with reference to the accompanying drawings. In which is shown:

figure 1 shows a rough side view of an embodiment of a ground-working machine according to the invention in the form of a large milling machine,

fig. 2 shows a schematic longitudinal section of the support structure and the working assembly of the floor-working machine of fig. 1 in a state ready for floor working, wherein the cutting plane contains the drive mechanism axis of the working assembly,

figure 3 shows an enlarged partial longitudinal section of the working assembly including the drive configuration and the longitudinal end of the milling roller on the right in figure 2,

figure 4 shows a perspective view of the drive configuration of figures 2 and 3,

figure 5 shows a top view of the drive configuration of figure 4 in a direction orthogonal to the drive mechanism axis,

fig. 6 shows a perspective view of a transfer member having a driving configuration, which engages with a driving counter-configuration on the bearing sleeve of fig. 2 and 3,

FIG. 7 shows a top view of the transmission member of the bearing housing of FIG. 6 along the machine height, orthogonal to the drive mechanism axis, and

fig. 8 shows a perspective view of a connecting structure and a bearing sleeve according to a second embodiment of the invention of a ground working machine or a support structure of the present application.

Detailed Description

A first embodiment of a ground-working machine according to the invention in the form of a ground-milling machine or road milling machine is designated generally by 10 in fig. 1. The floor-processing machine comprises a frame 12 which forms the basic framework of a machine body 13. Body 13 includes a frame 12 of machine 10 and components connected to the frame that are movable relative to the frame as necessary.

The body 13 includes a front lifting column 14 and a rear lifting column 16, which are connected at one end to the frame 12 and at the other end to a front travel mechanism 18 or to a rear travel mechanism 20. The spacing of the frame 12 from the travel mechanisms 18 and 20 can be varied by the lift posts 14 and 16.

The running mechanisms 18 and 20 are shown as chain running mechanisms, for example. Individual or all travel means 18 and/or 20 can also be wheel travel means in a different way.

The observer of fig. 1 looks in a machine transverse direction Q, which is orthogonal to the plane of the drawing of fig. 1, towards a ground-working machine or simply "machine 10". The machine longitudinal direction orthogonal to the machine transverse direction Q is denoted by L and runs parallel to the drawing plane of fig. 1. The machine height direction H likewise runs parallel to the drawing plane of fig. 1 and is orthogonal to the machine longitudinal direction L and to the machine transverse direction Q. The arrow point of the machine longitudinal direction L in fig. 1 points in the forward direction. Machine height direction H runs parallel to the yaw axis of machine 10, machine longitudinal direction L runs parallel to the roll axis and machine transverse direction Q runs parallel to pitch axis Ni.

The floor treating machine 10 may have a cab 24 through which a machine operator may control the machine 10 via a console 26.

Disposed beneath the machine frame 12 is a working assembly 28, which is, for example, a milling assembly, which has a milling roller 32 accommodated in a milling roller magazine 30, which milling roller is rotatable about a milling axis R extending in the machine transverse direction Q, whereby during ground machining starting from the bearing surface AO of the foundation U, ground material is stripped off at a milling depth determined by the relative height position of the machine frame 12. Thus, the milling roller 32 is the working device in the present application. The milling roller box 30, which is detachably connected to the frame 12, forms the support structure in the present application.

The height adjustability of frame 12 via lift posts 14 and 16 also serves to set the milling depth or generally the working depth of machine 10 during ground machining. The exemplary floor-processing machine 10 shown is a large milling machine, for which it is customary to arrange the working assembly 28 in the machine longitudinal direction L between the forward running gear 18 and the rearward running gear 20. Such large mills or floor stripping machines typically have a conveyor belt to transport the stripped floor material away from the machine 10. In fig. 1, the conveyor belt, which is present in principle in the machine 10, is not shown for the sake of clarity.

In the side view of fig. 1, machine 10 is not visible, in its front end region and its rear end region, each having two lifting columns 14 and 16, respectively, and a travel mechanism 18 and 20, respectively, connected thereto. The front lifting columns 14 are each coupled in a known manner to the travel means 18 by means of travel means connection structures 34, the travel means connection structures 34 being, for example, connecting forks which straddle the travel means 18 in the machine transverse direction Q. The rear lift columns 16 are connected with their respective travel mechanisms 20 via travel mechanism connection structures 36 that are configured the same as the travel mechanism connection structures 34. Travel mechanisms 18 and 20 are substantially identical and form a mechanical chassis 22. The travel mechanisms 18 and 20 are driven by motors, typically hydraulic motors, not shown.

An internal combustion engine 39 housed on frame 12 forms the drive power source for machine 10. In the embodiment shown, the milling roller 32 is driven in rotation by an internal combustion engine. A hydraulic reservoir is also provided on machine 10 by the power of internal combustion engine 39, through which hydraulic motors and hydraulic actuators on the machine may be driven. Accordingly, internal combustion engine 39 is also the source of motive power for machine 10.

In the example shown, the travel mechanism 18, the direction of travel of which is indicated by the double arrow D, has a radially inner receiving and guiding structure 38 on which a circulating travel chain 40 is arranged and performs a circulating movement.

The lifting column 14 and the travel mechanism 18 together with it can be rotated about a steering axis S by means of a steering device, not shown in detail. Preferably, but alternatively, the lifting column 16 and the travel mechanism 20 therewith can be rotated by a steering device about a steering axis parallel to the steering axis S.

Fig. 2 shows a longitudinal section through the work module 28 and the milling roller 32 from fig. 1 in a sectional plane containing the axis of rotation R of the milling roller. Fig. 2 also shows the components of the milling roller box 30.

The milling drum 32 comprises a substantially cylindrical milling drum tube 42, on the radial outside of which a chisel holder or chisel-changing holder 33a and a milling chisel 33b accommodated replaceably therein are arranged in a known manner. For the sake of clarity, only one example is shown in each case. The dotted line 44 gives the effective diameter (cut-through cylinder) of the milling roller 32, which is defined by the milling chisel edge of the milling chisel 33 b.

Working assembly 28 includes a drive configuration 46 having an inner tube 48, a support cone 50, and a portion 52a of a transmission housing 52 that is rotatable relative to frame 12. The support cone 50 and the inner tube 48 are connected to each other and as an assembly with the transmission housing part 52a for jointly rotating about the drive mechanism axis a of the drive configuration 46. In the reference state of the working assembly 28, the drive mechanism axis a of the drive configuration 46 and the axis of rotation R of the milling roller 32 are coaxial.

In fig. 2, the working assembly 28 is in a reference state ready for rotation about the drive mechanism axis a. For this purpose, the milling roller 32 is connected in a torque-transmitting manner to a drive configuration 46 of the working assembly 28. The milling roller 32 surrounds the drive profile 46 radially on the outside.

A planetary gear set for reducing the rotational speed and increasing the torque is accommodated in the gear case 52. A part 52b of the gear housing 52, which is co-rotatable with the inner tube 48 and is located on the right in fig. 2, is coupled for co-rotation with the ring gear of the planetary gear. The part 52b of the transmission housing 52 on the left in fig. 2 is fixed relative to the support structure and is therefore fixed to the part of the machine body 13 fixed to the machine frame.

The milling roller tube 42 is supported on a support cone 50 of the drive profile 46 by a mating support cone 51 of concave conical shape.

Furthermore, the drive configuration 46 is connected with a drive torque transmission device 54, which in the example shown comprises in particular a belt pulley 55. The belt pulley 55 is connected to an input shaft (not shown in fig. 2) of the planetary gear in the gear housing 52. The input shaft, which is connected for rotation with the belt pulley 55, extends through a shaft channel 56, which is fixed in the embodiment shown to the support structure and is rigidly connected to the transmission housing part 52 b.

The drive arrangement 46 forms, together with the assembly of the shaft channel 56 fixed to the support structure and the transmission housing part 52b, a drive assembly 47 which projects axially into the milling drum 32 starting from the drive mechanism axial end region 28a of the working assembly 28. Preferably, the milling roller 32 protrudes axially on both sides over a drive profile 46 as part of a drive assembly 47, which is rotatable relative to the milling roller box 30 as a support structure and thus relative to the frame 12.

The drive assembly 47 and the drive arrangement 46 associated therewith are supported in the region of the shaft channel 56 on the first support region 30c of the milling roller box 30. More specifically, the drive arrangement 46 and the rotatable transmission housing part 52a are supported on the frame-fixed transmission housing part 52b and on the first support structure region 30c by means of a first rotary bearing 57, said first rotary bearing 57 being arranged between the rotatable transmission housing part 52a and the frame-fixed transmission housing part 52 b. In fig. 2, only the first rotary bearing 57 is shown in dashed lines and symbolically. The first rotary bearing 57 forms a fixed bearing of the drive configuration 46. Thus, the axial longitudinal end 46a of the drive profile 46 which is closer to the pulley 55 is also referred to as the fixed bearing side longitudinal end 46 a.

The milling roller 32 extends axially along its axis of rotation (milling axis) R, which coincides with the drive mechanism axis a in the ready-to-operate state, between a fastening mechanism axial end region 28b of the drive assembly 28 and a drive mechanism axial end region 28a, which drive mechanism axial end region 28a is closer to the drive torque transmission device 54 in fig. 2. In the fixing means axial end region 28b, the milling roller 32 is positionally fixed in the reference state on the drive configuration 46 by means of a central fixing screw 78. Set screw 78 is part of working assembly 28.

At the floating bearing-side longitudinal end 46b, which is axially opposite the fixed bearing-side longitudinal end 46a, the drive configuration 46 has a bearing ring 58 and an end-face cover 60 connected to the bearing ring 58 as end-face components of the present application. In the illustrated embodiment, the support ring 58 is welded to the inner tube 48. The cap 60 may also be welded or alternatively screwed to the support ring 58. The cover is connected to the support ring 58 and the inner tube 48 for common rotation about the drive mechanism axis a.

The radially outer regions of the support ring 58 and the cover 60 can be designed in different ways. Its configuration is not essential. It is also conceivable to dispense with the bearing ring 58 and to connect the cover 60 directly to the inner tube 48, in particular by welding.

In the embodiment shown in fig. 2, a hydraulic cylinder 62 is accommodated in the interior 49 of the drive arrangement 46, which hydraulic cylinder is arranged with its cylinder axis coaxial with the drive mechanism axis a of the drive arrangement 46. The hydraulic cylinders 62 may be supplied with hydraulic fluid via hydraulic link lines 64 through power through-holes 66 in the cover 60.

At its longitudinal end remote from hydraulic cylinder 62, hydraulic coupling line 64 can exit from hydraulic cylinder 62 and enter the same again around piston rod 63 in a coupling configuration 68, which can be connected to a mating coupling configuration of a supply line, not shown, in order to supply hydraulic cylinder 62. In order to operate the preferred double-acting hydraulic cylinder, two hydraulic connecting lines 64 can be provided, one for each direction of movement of the piston rod 63.

After the central fixing screw 78 provided for axially positionally fixing the milling roller 32 on the drive profile 46 has been loosened, the milling roller 32 is pressed axially away from the drive profile 46 by means of the piston rod 63 for removal or pulled onto the drive profile 46 for installation.

In the region closer to the fastening means axial end region 28b, a connecting ring 70 is arranged radially inwardly on the milling roller tube 42 and is connected for common rotation with the milling roller tube 42, in the example shown by welding.

In this embodiment, milling roller tube 42 is rigidly connected to a connecting flange 74 via a connecting ring 70 by means of bolts 72. The connecting ring 70 and the connecting flange 74 jointly form the connecting structure 73 of the milling roller 32, as described in the introduction of the description.

A bearing pin 74a is provided on the connecting flange 74, which is screwed, welded or preferably formed in one piece with the connecting flange 74, and which projects from the connecting region of the connecting flange 74 with the connecting pipe 70 in the axial direction toward the fastening means axial end region 28b or away from the drive means axial end region 28 a.

In contrast to the exemplary embodiment shown, the connecting flange can be connected, in particular welded, directly to the milling roller tube without a connecting ring, with corresponding dimensions.

In addition or alternatively, the bearing pin can be designed separately from the connecting flange and mounted on the connecting flange, in particular releasably screwed, unlike the exemplary embodiment shown.

In the ready-to-operate state of the milling roller 32, a second rotary bearing 76, which supports the drive configuration 46 and is intended for bearing rotation about the drive axis a, is arranged on the bearing pin 74a, the second bearing being intended to form a rotationally mounted floating bearing. In the exemplary embodiment shown, the two rotary bearings 57 and 76 are designed as rolling bearings.

The second rotary bearing 76 is part of the rotary bearing arrangement 77 together with a bearing sleeve 86 and a bearing pin 74a arranged on an inner ring of the second rotary bearing 76. The bearing pin 74a is a component-side bearing configuration of the rotary bearing device 77, and the bearing sleeve 86 is a structural-side bearing configuration. The second pivot bearing 76 forms a pivot bearing arrangement 85 with the bearing sleeve 86, which pivot bearing arrangement 85 is only jointly movable in normal operation.

The second rotary bearing 76 can be accommodated, for example, in a side plate as a second support structure region, or in the side door 30a (see fig. 3). The side gate 30a is part of a milling roller box 30 and is axially opposite, on the end side, a milling roller 32 on the fastening means axial end region 28 b. Fig. 2 shows only the component 30b, which is rigidly connected to such a side door 30a as a second bearing region and serves as a bearing surface for the outer bearing ring of the second pivot bearing 76.

Preferably, the side door 30a is pivotably arranged on the frame 12 in order to be able to access the drive profile 46 or/and the milling roller 32 in the interior of the milling roller box 30 by simply swinging up and down. Preferably, the side door 30a can swing about a swing axis parallel to the machine height direction H, because the side door 30a thus swings in any swing direction without overcoming the gravity. Preferably, the rotary bearing assembly 85 is supported on the side door 30a such that the rotary bearing assembly 85 can swing together with the side door 30 a. Here, the opening of the side door 30a pulls the pivot bearing assembly 85, i.e., the second pivot bearing 76, together with the bearing sleeve 86, axially away from the bearing pin 74 a.

Preferably, the distance of the side door pivot axis from the side door 30a is greater than the radius of the sectional cylinder of the milling drum 32 shown in fig. 2, so that the circular path of the rotary bearing assembly 85 has as large a radius as possible and as small a curvature as possible when pivoting together with the side door 30 a. Thereby allowing the rolling bearing assembly 85 to be simply pulled off the bearing pin 74a or pushed onto the bearing pin 74 a.

In fig. 3, the support ring 58, the cover 60 and the connecting flange 74 have a slightly different configuration than the illustration in fig. 2. The configuration of the components does not differ from the different points in the schematic diagram in fig. 2 in the influence of the implementation of the invention.

In fig. 3, the hydraulic cylinder 62 and its piston rod 63 are omitted for clarity. Also, for clarity, the bolts 72 for connecting the connecting flange 74 with the connecting ring 70 are not shown.

On the cover 60, a centering structure 60a in the form of a centering pin is preferably formed integrally therewith, which pin projects from the cover 60 in the direction of the longitudinal end 46a of the drive structure 46 on the fixed bearing side or away from the drive mechanism axial end region 28a of the working assembly 28 toward the second support structure region 30 a. The centering pin 60a projects into a mating centering formation 74b on the connecting flange 74, which is embodied as a centering recess, and thus centers the milling roller tube 42, which is rigidly connected to the connecting flange 74, about the drive mechanism axis a. The cover 60 has a central recess 60b running axially through the cover, which is axially traversable by the piston rod 63 in fig. 2.

The milling roller 32 is therefore supported on the drive configuration 46 coaxially to the drive mechanism axis a on the mating support cone 51 and the connecting flange 74.

On the end region of the centering pin 60a facing the fixing means axial end region 28b, the recess 60b in the centering pin 60a is provided with an internal thread into which a central fixing screw 78 is screwed.

In an alternative embodiment, the centering pin 60a extends through the connecting flange 74 and projects axially from the cover 60 of the drive configuration 46. The centering pin 60a is now an assembly-side bearing configuration.

The screw head 78b clamps the bearing pin 74a and the connecting flange 74 by means of the bearing pin, and in turn the connecting ring 70 by means of the connecting flange, and the milling roller tube 42 axially abuts against the support cone 50 of the drive profile 46.

Thus, when the milling roller 32 is axially spaced from its operating position, but is arranged at a predetermined position such that the longitudinal end of the centering pin 60a remote from the bearing ring 58 has penetrated into the centering recess 74b of the connecting flange 74, the milling roller 32 can be moved axially with the central fixing screw 78 into its operating position. It should be noted that a transmission member 80, for example in the form of a pin, which is arranged on the cover cap 60 at a radial distance from the drive axis a, can reach into a recess 74c of the connecting flange 74 provided for this purpose, thereby coupling the cover cap 60 with the connecting flange 74 in order to transmit a torque between the drive configuration 46 and the milling roller 32.

Instead of screwing or clamping the milling roller 32 to the drive structure 46 by means of the fastening screw 78, the milling roller 32 can also be pushed onto the drive structure 46 by means of the pivotable side door 30 a. During the pushing-up, the counter-centering formation 74b is pushed not only onto the centering pin 60a, but preferably also the rotary bearing assembly 85 onto the bearing pin 74 a.

In order to simply bring the milling roller 32 into a position ready for operation, just by swinging the side door 30a, as mentioned in the preceding paragraph, into its closed state shown in fig. 3, in which it encloses the milling roller box 30, the floor finishing machine 10 preferably has an actuator which assists the swinging of the side door 30a at least in one direction of movement and at least in a range of movement which encompasses the closed state. Particularly preferably, the end range of movement when the side door 30a is moved into the closed state is referred to herein. Thus, the force required to push the milling roller 32 onto the drive profile 46 and the force required to push the slew bearing assembly 85 onto the bearing pin 74a are fully or at least partially applied by the actuator. Such an actuator may have, for example, one or more piston-cylinder arrangements. The cylinder is preferably articulated on the frame 12. When the side door 30a is sufficiently close to the piston rod engagement configuration during the retraction of the piston rod, the side door 30a can engage with the piston rod engagement configuration, preferably in a form-fit manner that transmits particularly high forces, so that the one or more piston-cylinder arrangements at least assist, preferably automatically, in performing the residual closing movement of the side door 30 a.

Preferably, the actuator can assist the swing movement of the side door 30a in the movement starting region of the swing movement of the side door 30a from the closed state toward the entry state, or even cause the swing movement to be carried out, together with the slew bearing assembly 85, through which the slew bearing assembly 85 is pulled out of the bearing pin 74 a. Alternatively or additionally, the actuator may also be an electromechanical actuator.

Fig. 4 shows a perspective view of the floating bearing-side longitudinal end 46b of the drive arrangement 46 and the section of the inner tube 48 connected thereto. The hydraulic coupling configuration 68 shown in fig. 2 is not shown in fig. 4 for clarity on end face 60 c.

The observer of fig. 4 looks at the end face 60c of the cover 60, from the center of which the centering pin 60a projects and which is surrounded with radial spacing by, for example, three transmission members 80 arranged at equal spacing from one another in the circumferential direction. In this case, the upper transmission member in fig. 3 is formed with a driving formation 88 at its freely projecting longitudinal end remote from the end face 60 c. In the example shown, only the upper transfer member 80 'is configured with the driving formation 88 and is therefore indicated with a prime symbol as transfer member 80' in order to distinguish it from the remaining two transfer members 80.

All the transmission members 80 and 80' are fastened to the cover 60 by a screw 80a passing through it in the center. The flange 80b of the unmodified transmission member 80 surrounding the head of the screw 80a terminates with an end surface orthogonal to the drive mechanism axis a, while a transmission member 80 'with a driving profile 88 protrudes further in the axial direction from the end face 60c, wherein the circumferential section of the flange 80 b' surrounding the securing screw 80a is configured as the driving profile 88 (see also fig. 5).

The drive arrangement 46 can be driven for rotation by the above-described rotary drive for machining of the stripping floor in only one direction of rotation, which is the first circumferential direction indicated by U1 in fig. 4. The driving formation 88 has a driving surface 88a, in the example shown a flat driving surface 88a, which is directed in the first circumferential direction U1. Preferably, the flat driving surface 88a lies in a plane containing the drive mechanism axis a.

Starting from the driving surface 88a, an adjusting surface 88b, which is directed predominantly in the axial direction, extends in the opposite second circumferential direction U2, which is inclined, as shown in fig. 7, relative to a reference plane BE that is orthogonal to the drive mechanism axis a, so that the adjusting surface approaches the drive mechanism axial end region 28a of the drive assembly 28 in the second circumferential direction U2, or also the longitudinal end region 46a of the drive configuration 46 on the fixed bearing side in the axial direction, with increasing distance from the driving surface 88 a.

The torque-transmitting engagement of the driving formations 88 with the driving counter-formations 90 on the bearing sleeve 86 is shown in fig. 6 and 7. In order to be able to show the engagement of the driving formations 88 with the driving counter-formations 90 as clearly as possible, only the transmission member 80' with the driving formations 88, its fastening screw 80a, the driving counter-formations 90 and the bearing sleeve 86 supporting them are shown in fig. 6 and 7. However, in conjunction with the aforementioned fig. 2 to 5, it is clear how the components shown in fig. 6 and 7 are arranged on the milling roller box 30 or on the road milling machine 10.

The driving counter formation 90 has a preferably flat driving counter surface 90a pointing in the second circumferential direction U2, which is in torque-transmitting abutting engagement with the driving surface 88 a. The adjustment counter surface 90b, which is also predominantly directed in the axial direction, extends in the first circumferential direction U1 from the driving counter surface 90a, which is inclined relative to the reference plane BE, as can BE seen in fig. 7, in such a way that the adjustment counter surface is axially also remote from the drive mechanism axial end region 28a of the drive assembly 28 and from the fixed bearing-side longitudinal end 46a of the drive assembly 46 in the second circumferential direction U2 with increasing distance from the driving counter surface 90 a.

As with the driving surface 88a and the driving counter surface 90a both pointing in the circumferential direction, but in the opposite circumferential direction U1 or U2, both the adjustment surface 88b and the adjustment counter surface 90b point in the axial direction, but in the opposite axial direction a1 or a2 (see fig. 7).

Functional surface of the driving mating formation 90: the driving counter surface 90a and the adjusting counter surface 90b are formed on a projecting element 90c which is inserted as a separate element into a recess 90d in the bearing sleeve 86 and is releasably fastened there by, for example, three screws. The recess 90d is a functional component of the driving counterpart 90.

Thus, torque transmitted from the driving formation 88 to the driving counterpart formation 90 may be transmitted from the protruding member 90c via the fastening screw of the protruding member 90c and via the side of the recess 90d to the bearing sleeve 86 and to the rotary bearing assembly 85. A flat fastening face for arranging the protruding member 90c may also be provided by the recess 90 d.

In principle, the projecting element 90c can also be welded to the bearing sleeve 86. A releasable fastening for replacing a worn protruding member is preferred. The transmission member 80 'can also be replaced quickly, simply and reliably with a transmission member 80' that is not worn, in the event of excessive wear, by loosening its unique fastening screw 80 a.

The flat driving surface 90a preferably lies in a plane containing the drive axis a.

As can BE seen in fig. 7, the adjusting surface 88b and the adjusting surface 90b are also inclined in value at substantially the same angle α or β relative to the reference plane BE, so that these surfaces can lie flush against one another and are parallel or coplanar.

Preferably, the angles α and β are each at least 25 °, better still at least 30 °, in order to avoid self-locking in the event of the adjustment surface 88b and the adjustment counter surface 90b abutting against one another, and for this purpose such that the driving formation 88 and the driving counter formation 90, during an attempt to establish the reference state described above and shown in fig. 2 and 3, not only coincide with one another in the circumferential direction, but also exert a force in the axial direction toward one another, by means of which the abutting joint of the adjustment surface 88b and the adjustment counter surface 90b is driven to rotate relative to one another and can slide past during the axial approaching movement toward one another. This prevents the driver contour 88 and the driver counter contour 90 from being damaged in the event of a crash.

The movement space of the driving surface 88a is indicated by reference numeral 92 and the movement space of the driving surface 90a is indicated by reference numeral 94 in fig. 7. This is the space 92 and 94 that passes over the corresponding face 88a or 90a during rotation about the drive mechanism axis a. The overlapping region which is jointly occupied by the two movement spaces 92 and 94 is shown partly hatched in fig. 7 and indicated by 96, in which overlapping region the movement spaces 92 and 94 overlap. Due to this overlap region 96, the driving surface 88a is now also in abutting engagement with the driving counter surface 90a when the driving surface and the driving counter surface are arranged at a distance from one another in the circumferential direction about the drive axis a immediately after the reference state has been established and a relative rotation about the drive axis a occurs between the bearing pin 74a and the bearing sleeve 86 during the machining operation. But such relative rotation between bearing pin 74a and bearing sleeve 86 will not be one revolution at a time due to adjustment surface 88b and adjustment mating surface 90 b.

In contrast to the merely exemplary illustrations in fig. 4 to 7, the driving means 88 can be arranged on the milling drum, preferably on the connecting structure 73. For example, the driving means can be arranged on the connecting flange, for example in a recess, preferably detachably. Such a second embodiment is shown in fig. 8. The components and component sections that are identical to the components and function in the first embodiment are provided with the same reference numerals in the second embodiment, but the numerals are increased by 100. Only the differences of the second embodiment from the first embodiment will be described below.

In the second embodiment shown in fig. 8, the driving profile 188 is arranged on the connecting structure 173. In the connecting structure 173, the bearing pin is formed as a separate component from the connecting flange 174. The separate bearing pin member and the bearing pin itself are obscured in fig. 8 by the bearing sleeve 186.

The driving formation 188 comprises a projecting member 188c on which the driving surface 188a and the adjusting surface 188b are formed and oriented in the manner described above, and which is inserted into a recess 188d of the driving formation 188 and is fixed here as intended releasably with a screw. The recess 188d is formed in the end face of the connecting flange 174.

The driving counter formation 190 corresponds to the driving counter formation 90 of the first embodiment. Alternatively, the projecting members 90c and 188c may be identical, such that only a single type of projecting member need be manufactured in order to form an engagement assembly that includes a driving configuration and a driving mating configuration.

The rest of the floor-processing machine of the second embodiment is unchanged from that shown in fig. 1.