The present invention relates to a ground processing roller which can be used to compact a soil, such as asphalt, for example.
To be able to achieve a higher and more uniform degree of compaction, in particular when compacting asphalt, it is known to use ground processing rollers to carry out such compaction processes, which have an unbalance arrangement with a plurality of unbalanced masses arranged at a circumferential distance from one another about the roller axis of rotation, wherein each unbalanced mass can be driven to rotate about an unbalance axis of rotation assigned thereto. Due to the rotation of these unbalanced masses, depending on the phase position and direction of rotation of the unbalanced masses or the centers of mass thereof relative to one another, a substantially tangentially acting oscillation torque can be superimposed on the rotational movement of such a ground processing roller about the roller axis of rotation in oscillatory operation, or a force which is substantially orthogonal to the roller axis of rotation can be applied to the ground processing roller in vibration operation.
The various components provided to achieve such an oscillatory operation or vibration operation are substantially positioned and movable in a roller interior of such a ground processing roller, which interior is surrounded by a roller shell. In order to provide sufficient lubrication for these rotating or/and torque-transmitting components, which are rotatably mounted in different bearing areas, it is necessary to provide lubricant or a lubricant circulation in the roller interior.
It is the object of the present invention to provide a ground processing roller, in particular for a soil compactor, in which reliable lubrication of components provided in different radial areas with respect to a roller axis of rotation of the ground processing roller in a roller interior is achieved.
According to the invention, this object is achieved by a ground processing roller, in particular for a soil compactor, comprising:
Providing two radially staggered lubricant sumps creates the option in the area of the radial levels covered by these lubricant sumps to wet components located there or moving through these areas with lubricant and thus to protect them from excessive stress or aging. At the same time, this radial staggering of the lubricant sumps and the conveyance of lubricant from the first lubricant sump into the second lubricant sump as well as the option to release excess lubricant from the second lubricant sump back into the first lubricant sump results in a cascade-like arrangement of the lubricant sumps with a guided circulation of the lubricant therethrough. Thus, while using a comparatively small amount of lubricant overall and thus avoiding the need to fill the interior of the roller with excess lubricant, system areas positioned at different radial distances from the roller axis of rotation can be reliably supplied with the amount of lubricant required for their lubrication.
For low-wear and reliable torque transmission, at least one drive gear, preferably each drive gear, can be in meshing engagement with at least one driven gear, or/and at least one driven gear, preferably each driven gear, can be connected to the unbalanced mass assigned to it for common rotation about the unbalance axis of rotation of this unbalanced mass. To be able to generate the operative direction tangential or orthogonal to the roller axis of rotation by means of the unbalance arrangement, it is proposed that the unbalance axis of rotation of at least one unbalanced mass, preferably each unbalanced mass, is eccentric or/and parallel to the roller axis of rotation. This leads to efficient lubrication of components arranged in different height areas or radial levels with respect to the roller axis of rotation using a comparatively small amount of lubricant and thus avoids the need to fill the roller interior with an excessively large amount of lubricant.
To be able to collect lubricant conveyed or distributed upwards from the first lubricant sump by the lubricant conveying arrangement and to direct it into the second lubricant sump, it is proposed that a lubricant collecting unit, which is open at the top in the height direction, is provided above the roller axis of rotation, and that a lubricant flow connection is provided between the lubricant collecting unit and the second lubricant sump for directing lubricant collected in the lubricant collecting unit into the second lubricant sump.
For an efficient collecting effect, the lubricant collecting unit can comprise a trough-like lubricant collecting element, which preferably widens like a funnel in the vertical direction.
The roller shell can be rotatably supported on a support arrangement about the roller axis of rotation, wherein the support arrangement comprises a rotatable support arrangement part which is non-rotatably connected to the roller shell and a fixed support arrangement part which rotatably supports the rotatable support arrangement part. The first lubricant sump and the second lubricant sump can be provided in a support arrangement interior formed in the support arrangement. This creates the option of providing the two lubricant sumps in the two support arrangement parts closed to prevent the escape of lubricant to the outside.
To achieve efficient use of the interior space provided in the support arrangement, it is proposed that the first lubricant sump is substantially completely provided in the rotatable support arrangement part, or/and that the second lubricant sump is substantially completely provided in the fixed support arrangement part.
For force transmission coupling or torque transmission coupling with the roller shell, the unbalanced masses can be carried rotatably about their unbalanced axes of rotation on the rotatable support arrangement part on which the roller shell is also supported.
The at least one drive gear and the driven gears can be arranged in a first region of the support arrangement interior formed substantially in the rotatable support arrangement part. This makes it possible, particularly if the first lubricant sump is also provided in this area, to position a driven gear positioned in the height direction below the roller axis of rotation at least partially in the first lubricant sump. In this context, it should be noted that, when the ground processing roller rotates about its roller axis of rotation, the unbalanced masses also move with their unbalanced axes of rotation about the roller rotation axis and thereby successively reach such a position under the roller rotation axis and in the first lubricant sump.
To ensure that the lubricant collecting unit is always positioned in an area that is in an upper area in the height direction or an area located above the roller axis of rotation, it is proposed that the lubricant collecting unit is provided on the fixed support arrangement part, and that the lubricant flow connection is in the fixed support arrangement part or/and is formed substantially in the second region of the support arrangement interior formed in the fixed support arrangement part.
To be able to easily provide a flow connection between the two lubricant sumps, it is proposed that a limiting element delimiting the second lubricant sump in the direction of the roller axis of rotation is provided on the fixed support arrangement part, and that at least one lubricant passage opening of the overflow connection is provided in the limiting element.
To easily enable drive access to the at least one drive gear, the roller axis of rotation can pass through the lubricant passage opening or/and the lubricant passage opening can be arranged substantially concentrically to the roller axis of rotation.
To drive the unbalanced masses, the unbalance transmission system can comprise two drive gears and an unbalance transmission unit, wherein at least one of the drive gears can be driven to rotate by the unbalance motor via the unbalance transmission unit.
In a particularly advantageous embodiment, one of the drive gears can be driven by the unbalance motor via the unbalance transmission unit to rotate about a drive gear axis of rotation that is preferably concentric with the roller axis of rotation, and another of the drive gears can be driven directly by the unbalance motor to rotate about the drive gear axis of rotation. In this context, it should be noted that a direct drive connection means that the drive gear driven in this way is coupled to a drive element of the unbalance motor for common rotation without the option of rotational speed transmission or reversal of the direction of rotation or change of the phase position, for which purpose, for example, a torque-transmitting shaft or the like can be used.
The unbalance transmission unit can be designed as a rotational position adjustment gear, wherein the unbalance transmission unit can adjust a rotational position of one of the drive gears about the drive gear axis of rotation with respect to a rotational position of the other of the drive gears about the drive gear axis of rotation. For example, the unbalance transmission unit can include a planetary gear. In such a configuration, there preferably is also no change in rotational speed caused by the unbalance transmission unit itself or that the drive gear driven to rotate by said transmission unit rotates at the same speed as the drive gear driven directly by the unbalance motor. Only in a phase in which a change in the relative rotational position of the two drive gears is to be effected, it is inevitable they temporarily have different speeds.
For a compact design, the unbalance transmission unit can be arranged in a second region of the support arrangement interior which is substantially formed in the fixed support arrangement part.
To be able to lubricate in particular the unbalance transmission unit or components thereof by means of the second lubricant sump, a part of the unbalance transmission unit positioned in the height direction below the roller axis of rotation can be positioned at least partially in the second lubricant sump. It should also be taken into account that during operation, due to the movement of components of the unbalance transmission unit about the roller axis of rotation, they periodically reach the area of the second lubricant sump and can be wetted with lubricant there.
For a lubricant conveying arrangement that is simple to design but still operates efficiently, this can include at least one driven gear, preferably all driven gears, or/and at least one drive gear, preferably all drive gears.
For an efficient conveying effect, the lubricant conveying arrangement can further comprise a plurality of conveying projections provided on the rotatable support arrangement part.
The invention further relates to a ground processing machine, preferably a soil compactor, comprising at least one ground processing roller constructed according to the invention.
The present invention is described in detail below with reference to the attached drawings. Wherein:
In
A front carriage, generally designated 20, is articulated to the rear carriage 12. On the front carriage 20, a ground processing roller 22 is rotatably supported about a roller axis of rotation which is orthogonal to the drawing plane of
It should be noted that the ground processing machine 10 shown in
An unbalance arrangement, generally designated 28, is provided in the roller interior 26. In the exemplary embodiment shown, the unbalance arrangement 28 comprises two unbalanced masses 301, 302 arranged at a circumferential distance from one another about the roller axis of rotation W or arranged opposite one another with respect to the roller axis of rotation W. Each of the unbalanced masses 301, 302 is rotatable about an unbalance axis of rotation U which is parallel to the roller axis of rotation W and eccentric thereto, wherein the unbalanced axes of rotation U of the unbalanced masses 301, 302 preferably have the same radial distance from the roller axis of rotation W. The unbalanced masses 301, 302 can be driven to rotate about the respective unbalance axis of rotation U, such that a center of mass M of the unbalanced masses 301, 302, which is located eccentrically with respect to the respective unbalance axis of rotation U, rotates about the respectively assigned unbalance axis of rotation U.
The unbalanced masses 301, 302 of the unbalance arrangement 28 are rotatably supported in the roller interior 26 at their two axial end regions via respective bearing arrangements 36, 40. For this purpose, two support rings 32, 34 are provided in the roller interior 26, which rings are arranged at an axial distance from one another along the roller axis of rotation W and are fixed to the inside of the roller shell 24, for example by welding, and are generally also referred to as blanks. The unbalanced masses 301, 302 are rotatably supported on the support ring 34 shown on the right in
The support arrangement 42, which can be seen in more detail in
The rotatable support arrangement part 44 comprises a substantially disc-like housing part 48, which is fixed in its radially outer region, for example by screwing, to the support ring 32 and on which the unbalanced masses 301, 302 are rotatably supported via the bearing units 40.
On a cylindrical extension 49 of the housing part 48, another substantially disk-like housing part 50 of the rotatable support arrangement part 46 is fixed in its radially outer region, for example by screwing. At its radially inner region, the housing part 50 is rotatably mounted about the roller axis of rotation W via a bearing unit generally designated 52 on a substantially ring-like housing part 54 of the fixed support arrangement part 44, which is elongated in the direction of the roller axis of rotation W.
An unbalance motor 58 of an unbalance drive 59 is carried on an end cover 56 fixed to the housing part 54 of the fixed support arrangement part 44, for example by screwing. The unbalance motor 58 can be, for example, a hydraulic motor or electric motor, which drives the unbalance masses 301, 302 to rotate about their respective unbalance axes of rotation U by means of a drive member 60, for example a drive pinion, in the manner described below.
A first hollow shaft 62 is in meshing engagement with the drive member 60, such that the first hollow shaft 62 can be driven by the drive member 60 to rotate about the roller axis of rotation W. A drive shaft 64 meshes with the first hollow shaft 62 and carries a first drive gear 66 at its axial end region remote from the hollow shaft 62 and is rotatably mounted on the housing part 48 of the rotating support arrangement part 46. The first drive gear 66 is in meshing engagement with a driven gear 681 assigned to the unbalanced mass 301 or connected to it for common rotation about its unbalance axis of rotation U. The first drive gear 66, which is coupled to the unbalance motor 58 via the first hollow shaft 62 and the drive shaft 64 directly for rotation about a drive gear axis of rotation A corresponding to the roller axis of rotation W, drives the unbalanced mass 301 to rotate.
The first hollow shaft 62 forms, at its axial end distal from the unbalance motor 58 and coupled to the drive shaft 64 for common rotation, a first sun gear 70 of an unbalance transmission unit designed as a planetary gear and generally designated 72. On a second hollow shaft 74 surrounding the drive shaft 64, a second sun gear 76 of the unbalance transmission unit 72 is formed at its axial end adjacent to the first sun gear 70.
Sets of planet gears 80, 82 which are axially adjacent to one another and are each assigned to the two sun gears 70, 76 are rotatably supported on a planetary gear support 78 which surrounds the roller axis of rotation W in a ring-like manner. The set of planet gears 70, which are in meshing engagement with the first sun gear 70, is assigned a first ring gear element 86 that surrounds them and provides a first ring gear element 84. The planet gears 82, which are in meshing engagement with the second sun gear 76, are assigned a second ring gear 88, which is in meshing engagement with them, on a second ring gear element 90. While the second ring gear element 90 is firmly, in particular non-rotatably, supported on the housing part 54 of the fixed support arrangement part 44, the first ring gear element 86 is rotatably supported in the second ring gear element 90 by an actuator 92 indicated in
A second drive gear 94 is non-rotatably connected to the second hollow shaft 74 at its axial end distal from the second sun gear 76. The second drive gear 94 lies axially directly next to the first drive gear 66 and is in meshing engagement with a drive gear 682 assigned to the unbalanced mass 302.
If the first hollow shaft 62, which also directly drives the drive shaft 64, is driven by the unbalance motor 58 to rotate about a drive gear axis of rotation A corresponding to the roller axis of rotation W, then due to the fact that, in the illustrated embodiment of the unbalance transmission unit 72, the two sun gears 70, 76, the two ring gears 84, 88, and also the planet gears 80, 82 each have the same diameter, the rotation of the drive member 60 is transmitted to the second drive gear 94 without changing the rotational speed, which second drive gear drives the unbalanced mass 302 to rotate at the same speed and direction of rotation with which the unbalanced mass 301 rotates.
If the phase position of the unbalanced masses 301, 302 rotating at the same speed is to be changed with respect to one another, the first ring gear element 86 is rotated about the roller axis of rotation W, which in the course of this rotational movement leads to a change in the speed of the second hollow shaft 74 with respect to the speed of the first hollow shaft 62 and accordingly also a temporary change in the speed of the unbalanced mass 302 driven via the second drive gear 94. This leads to a change in the phase position of the center of mass M of the unbalanced mass 302 with respect to the phase position of the center of mass M of the unbalanced mass 301. If the desired extent of the change in phase position is reached, the rotational movement of the first ring gear element 84 is stopped, such that both unbalanced masses 301, 302 then rotate again at the same speed.
By adjusting the phase position of the centers of mass M of the two unbalanced masses 301, 302, it becomes possible to switch the unbalance arrangement 28 between different operating states. The two unbalanced masses 301, 302 are arranged in such a way that, as can be seen in
It should be noted that the unbalance arrangement 28 can also be constructed with a different number of unbalanced masses. For example, four unbalanced masses can be provided with an angular distance of 90° with respect to each other about the roller axis of rotation W, wherein unbalanced masses diametrically opposite one another with respect to the roller axis of rotation W each form a pair of unbalanced masses, in which the two unbalanced masses are rotated together by one of the two drive gears, i.e. for joint rotation at the same speed and in the same direction of rotation. By acting on the unbalance transmission unit 72, the phase position of the centers of mass of the two pairs of unbalanced masses can be changed with respect to one another, which makes it possible to vary the size and orientation of a force oriented substantially orthogonally to the roller axis of rotation W in the vibration operation of the unbalanced arrangement 28 during rotational operation of the unbalanced masses.
To achieve this rotational movement of the unbalanced masses 301, 302, the unbalance transmission unit 72, the drive gears 66, 94 and the driven gears 681, 682 driven by them to rotate form an unbalance transmission system of the unbalance drive 59, generally designated 96. To protect the various components of this unbalance transmission system 96 which are rotating and in meshing engagement with one another and also to protect the bearing units supporting these components from excessive wear, liquid lubricant, for example oil or the like, is contained in a support arrangement interior 98 formed in the support arrangement 42. In order to seal this support arrangement interior 98 against the escape of lubricant, on the one hand the unbalanced masses 301, 302 are assigned sealing units 100 which seal against the escape of fluid with respect to the housing part 48 of the rotating support arrangement part 46. The rotating support arrangement part 46 is tightly sealed with respect to the fixed support arrangement part 44 by a sealing unit 101.
The support arrangement interior 98 comprises a first region 102, which, in particular with regard to its axial extent, is substantially formed in the rotatable support arrangement part 46 and is delimited between the housing parts 48, 50 of the same. The two drive gears 66, 94 and the driven gears 681, 682 are also contained in the first region 102 of the support arrangement interior 98.
The support arrangement interior 98 comprises a second region 104, which, in particular with regard to its axial extent, is substantially formed in the fixed support arrangement part 44 and is delimited radially outwards by the housing part 54 of the same and axially by the end cover 56 supporting the imbalance motor 58. On the second ring gear element 90, which is firmly supported on the housing part 54, a disc-like limiting element 106 having a lubricant passage opening 108, for example concentric to the roller axis of rotation W, is supported at the axial end thereof facing the first region 102 of the support arrangement interior 98.
In the support arrangement 42, a first lubricant sump 110 is formed substantially in the first region 102 of the support arrangement interior 98 and a second lubricant sump 112 is formed substantially in the second region 104 of the support arrangement interior 98. When the ground processing roller 22 is not rotating and the unbalanced masses 301, 302 are not driven to rotate, the first lubricant sump 110 contains lubricant up to a first lubricant sump level N1. Due to gravity, the first lubricant sump level N1, which is fundamentally located in the height direction H below the roller axis of rotation W, has a first distance D1 in the height direction H from the roller axis of rotation W.
The second lubricant sump 112 has a second lubricant sump level N2, which is substantially defined by the lubricant passage opening 108, which substantially also provides an overflow connection 114, or its region which has the greatest distance to the roller axis of rotation W in the downward height direction H. As
During rotational operation of the ground processing roller 22 and in particular also when unbalanced masses 301, 302 are driven to rotate, the unbalanced masses 301, 302 arranged at a radial distance from the roller axis of rotation W and the driven gears 681, 682 connected to them for common rotation move successively into the area of the first lubricant sump 110 or through the same. Not only are the areas of the driven gears 681, 682 moving through the first lubricant sump 110 or the unbalanced masses 301, 302 driven by them moved into or through the first lubricant sump 110 and thereby wetted with lubricant, but, due to the rotation in particular of the driven gears 681, 682, lubricant from the first lubricant sump 110 is thrown substantially into the entire volume of the first region 102 of the support arrangement interior 98 and in particular upwards in the height direction H. Due to the contact with the driven gears 681, 682, the drive gears 66, 94 which are in meshing engagement with the driven gears 681, 682 also contribute to the fact that lubricant flows into the first region 102 of the support arrangement interior 98 and in particular is also thrown upward in the height direction H. The driven gears 681, 682 moving through the first lubricant sump 110 and possibly also the drive gears 66, 94 thus substantially form a lubricant conveying arrangement 116, through which lubricant from the first lubricant sump 110 is distributed in the first region 102 of the support arrangement interior 98 and is conveyed upwards in the height direction H, as indicated by arrows in
To distribute lubricant substantially throughout the entire volume of the first region 102 of the support arrangement interior 98, there can also be provided conveying projections 115 which act as conveyor blades, follow one another in the circumferential direction and extend approximately radially, as can be seen in
A lubricant collecting unit, generally designated 118, is arranged on the fixed support arrangement part 44, in particular the housing part 54 thereof, in an area lying above the roller axis of rotation W in the height direction H. This comprises a lubricant collecting element 120, which is described in more detail below with reference to
If, in the standstill state, the first lubricant sump 110 is filled with lubricant up to the first lubricant sump level N1, the level of the first lubricant sump 110 drops below the first lubricant sump level N1 present in the standstill state in rotational operation due to the fact that lubricant is also thrown into the upper part of the first region 102 of the support arrangement interior 98 and is partially injected via the lubricant flow connection 122 into the second region 104 of the support arrangement interior 98, but not to such an extent that sufficient wetting of components of the lubricant conveying arrangement 116 moving through the first lubricant sump 110 were no longer possible. However, the fill level of the second lubricant sump 112 always substantially corresponds to the second lubricant sump level N2.
In working operation, i.e. when the ground processing roller 22 and in particular also the unbalanced masses 301, 302 rotate, components of the unbalance transmission unit 72, which is accommodated substantially in the second region 104 of the support arrangement interior 104, move through the second lubricant sump 112. This applies in particular to the two ring gears 84, 88, the planet gear support 78 and the planet gears 80, 82 rotatably supported thereon. As a result, all areas of the unbalance transmission unit 72 successively come into contact with the lubricant present in the second lubricant sump 112. The sun gears 70, 76 are also wetted with lubricant through contact with the planet gears 80, 82.
The continuous conveying of lubricant by means of the lubricant conveying arrangement 116 from the first lubricant sump 110 into the second lubricant sump 112 ensures that the portion of the lubricant conveyed into the second region 104 of the support arrangement interior 98, which would lead to the second lubricant level N2 being exceeded, leads to a permanent outflow of lubricant from the second lubricant sump 112 or the second region 104 of the support arrangement interior 98 via the overflow connection 114 or the lubricant passage opening 108 into the first lubricant sump 110. Thus, a lubricant circulation is established in which the conveying or centrifugal effect of the drive gears 66, 94, the driven gears 681, 682, 683 and the conveying projections 115 ensures that all components present in the first region 102 of the support arrangement interior 98, in particular the unbalance transmission system 96, are wetted with lubricant. This particularly applies to the bearing units present in this region and used to mount rotating system components. Part of this lubricant distributed in the first region 102 of the support arrangement interior 98 reaches the second region 104 of the support arrangement interior 98 and the second lubricant sump 112 provided there via the lubricant collecting element 120 and the lubricant flow connection 122 and thus serves to sufficiently lubricate the unbalance transmission unit 72 in particular. Due to the cascade-like arrangement of the two lubricant sumps 110, 112, it is ensured that lubricant can be reliably distributed to components positioned at significantly different levels in the height direction H or moving in these regions.
The substantially trough-like lubricant collecting element 120 shown in
A passage opening 130 is formed in the end wall 124 to be positioned adjacent to the fixed support arrangement part 44, through which passage opening lubricant collected in the lubricant collecting element 120 can flow into the lubricant flow connection 122. It should be noted that, with an appropriate structural design, the end wall 124 can also be provided directly by the fixed support arrangement part 44, or/and that the lubricant collecting element 120 can also be constructed in one piece, for example as a cast element.
To be able to achieve an improved collecting effect for the lubricant collecting element 120 with a comparatively compact design, the end wall 126, which is further away from the fixed support arrangement part 44, can extend upwards in its area extending beyond the bottom wall element 128 in the height direction H be bent away from the fixed support arrangement part 44 to further support the funnel-like design of the lubricant collecting element 120.
Finally, it should be pointed out that in the support arrangement 42, as can be seen in particular in
Number | Date | Country | Kind |
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10 2022 133 785.5 | Dec 2022 | DE | national |