Patent Application
20170113226
The invention relates to a cone crusher having a crushing cone held on a driven eccentric bushing, wherein the eccentric bushing rotates in a radial direction about a crusher shaft, which is designed as a spindle and is clamped fixedly in a receptacle provided in the housing lower part.
Cone crushers of this type, but also gyratory crushers have long been known from the prior art. In accordance with their intended use, the mass comminution of pieces of rock, they are exposed in a harsh environment to large loads and to correspondingly high wear. In order to be able to ensure reliable operation, the wearing parts, including in particular the crushing cone held on the cone carrier and also the mounting of the cone carrier, have to be exchanged from time to time. It is advantageous for the service life if these operations can be performed quickly in situ. Since, however, the external conditions in situ are highly uncomfortable and the personnel used for the maintenance work sometimes become impatient because of the failure-induced delay, the moves have to be able to be performed simply and without a particular outlay on tools. In particular, the use of a heavy tool should be avoided as far as possible because of the risk of damage to the crushers.
Support of the spindle within the housing, as disclosed, for example, in the prior art according to DE 1 027 042, has long proven successful. In this case, a bell-shaped eccentric bushing having a correspondingly bell-shaped crushing cone is pulled over a fixed spindle. The eccentric bushing is set into rotation by an external motor via a bevel gear and a horizontally lying drive shaft. The spindle is clamped in the housing lower part via a conical seat which has a self-locking action. For the vertical securing and for the correction of the fitted position of the spindle, it is known to use a shaft nut at the lower end of the spindle in order additionally to brace the spindle against the housing part.
However, to manufacture the conical seat surfaces on the spindle and in the housing lower part is particularly complicated because of the required precision. This applies especially to modern cone crushers in which the spindles have a length of more than one meter. To manufacture conical seats at this length is at least complicated, if not even impossible—at least to the precision required, in particular where the oil ducts running in the spindle are dependent on the precise axial positioning. Furthermore, it is difficult to remove a spindle, which is being pressed fixedly into its conical bearing by the operation, for repair. Even with the aid of pressurized oil assemblies, the release of a spindle from its conical seat is not always ensured, and therefore a heavy tool is used.
It is now the object of the present invention to design a maintenance-friendly and cost-effective cone crusher, in which the installation and also the removal of the spindle are easily possible even under adverse conditions and without the use of a heavy tool.
This object is achieved by the cone crusher as claimed in claim 1. Advantageous embodiments are described in the dependent claims.
As claimed, the essential aspect of the invention lies in the fact that the conical seat of the spindle, which conical seat is problematic for large cone crushers, can be replaced by a cylindrical seat and the spindle can be braced in a purely mechanical manner with a force fit in said cylindrical seat, wherein said bracing provides the same secure support as a conical seat, but avoids the disadvantages of the complex removal and installation and the difficult positioning of the oil ducts. This is achieved according to the invention in that the crusher shaft, which is designed as a spindle, comprises a cylindrical upper bearing portion which is braced in a bore forming the spindle receptacle. The force-fitting bracing is undertaken here by means of a clamping device which is accessible from the outside and is actuable purely mechanically, wherein the use of a conical clamping set, as is known from the prior art in particular for the production of shaft-hub-connections, is appropriate as such a clamping device.
In order to be able to reliably compensate for the forces caused by the wobbling movement, the bracing of the spindle is advantageously undertaken not only via a single upper clamping device, but rather by means of two mechanical clamping devices which are arranged at an axial distance from each other and are dependent on the bending torque and are held in the housing lower part with a sufficiently large force engagement surface. Accordingly, in addition to the upper bearing portion, the spindle additionally comprises a cylindrical lower bearing portion which is clamped in a corresponding lower region of the annular space provided in the housing lower part by means of the second “lower” mechanical clamping device.
It is of particular advantage, because of the large clamping forces and because of the simple and therefore robust construction, if the two mechanical clamping devices for the production of the force-fitting connection are formed by conical clamping sets as are known per se from the prior art and are commercially available. As is known, such clamping sets have a conical inner ring (inner conical ring) and a correspondingly conical single- or two-part outer conical ring (“pressure ring”), wherein the conical surfaces of the rings slide on each other, and wherein inner ring and pressure ring are pulled over each other with tension means, in particular with clamping screws which are plugged through said rings and are combined into screw assemblies. With the displacement of the conical surfaces, because of the conical rings a radial force component arises from the axial prestressing force of the screws, said radial force component elastically shrinking the inner ring and expanding the outer ring such that compression is produced.
In order to facilitate the shrinkage and the expansion of the rings, it is particularly advantageous specifically in the case of the large-diameter clamping devices required for the present intended purpose, to use slotted inner and outer rings.
It is indeed expedient, for the use according to the invention of the clamping sets, but not absolutely necessary, for the rings to be continuous. As an alternative, clamping sets may also be formed by individual ring segments which are arranged symmetrically around the circumference of the spindle.
However, very generally, care should be taken in the case of the clamping sets to ensure that the cone angles are not too flat and it must be taken into account that there is the risk during the bracing of self-locking, which obstructs the later opening. Instead, the cone angles should be sufficiently steep such that, despite effective bracing, easy opening of the clamping sets when the clamping screws are released is nevertheless guaranteed. The spindle is removed in a simple manner by release of the screw assemblies of the two clamping sets. In particular, no additional aids, such as, for example, pressurized oil assemblies, are required. However, it may be advantageous to provide the pull-off threads which are known from commercially available clamping sets and into which screws can be screwed, which screws are then supported against the outer ring and drive the rings apart.
For the simple and precise installation and for the secure support of the spindle, it is furthermore advantageous to provide an axial stop in the spindle receptacle, against which axial stop the spindle lies with a correspondingly annular support. The spindle is then simply introduced from above into the spindle receptacle as far as the stop. The stop thus defines the exact axial fitted position of the spindle, in which fitted position in particular also the oil lines running in the spindle are reliably positioned. The annular support of the stop is advantageously realized by the fact that, firstly, the spindle and, secondly, the spindle receptacle in the lower region undergo a reduction in diameter. The annular support then arises at the transition between the two different diameters.
It is particularly advantageous here in respect of good accessibility and consequently for simple installation if the reduction in the diameter is provided between the upper and the lower bearing portion of the spindle, wherein the lower bearing portion has a smaller external size than the upper bearing portion. The clamping sets also have correspondingly different diameters. The screw assemblies of the upper clamping set are accessible from above, and those of the lower clamping set from below, during the installation.
In order to be able to securely brace spindles of particularly large diameters, it is advantageous to use conical clamping sets having radially divided pressure rings which lie virtually one behind another. In this case, the clamping sets have a front pressure ring which faces the inner ring, and a rear pressure ring, wherein the two pressure rings are acted upon via the by clamping screws which are assigned thereto and reach through the inner ring.
A particular advantage which arises from the bracing according to the invention of the spindle is, in addition to the robust construction of the cone crusher, especially also the relatively low overall height given a large diameter and correspondingly great efficiency at a high throughput. A further advantage of the bracing according to the invention is the substantially lower structural of complexity of the mounting in comparison to the previous conical bearing. In addition, separate fixing of the vertical fitted position of the spindle that is required in the case of the conical mounting can be dispensed with.
The invention therefore provides a maintenance-friendly and economically expedient alternative to the existing type of shaft fastening.
A particular embodiment of the cone crusher according to the invention is explained in more detail below with reference to the figures, in which:
The driven eccentric bushing 5 rotates radially guided about a spindle 7 which is clamped fixedly in the housing lower part 8. For the axial supporting of the cone carrier 4, use is made of a spherical axial bearing 10 which is arranged on the head of a cylinder piston 9 and absorbs the wobbling movement of the cone carrier 4. The cylinder piston 9 is integrated in an end-side bore of the spindle 7 and permits the axial displacement of the cone carrier 4 with the crushing cone 3 sitting thereon, which leads to the setting of the width of the crushing gap 6. The cylinder piston 9 is supplied with hydraulic oil via oil lines 18 placed into the spindle 7.
The spindle 7 is of rotationally cylindrical design and is pushed into the corresponding spindle receptacle 11, which is provided in the housing lower part 8 and is designed as a bore, wherein a sufficiently large amount of play is provided between the spindle 7 and the spindle receptacle 11. For the purpose of bracing the spindle 7 within the spindle receptacle 11, said spindle has a cylindrical upper bearing portion 15 (
In the present exemplary embodiment, the spindle 7 is additionally held via a second lower bracing means 14.2. For this purpose, said spindle has a cylindrical lower bearing portion 13 which is clamped in a lower region of the the spindle receptacle 11 by means of a corresponding lower mechanical clamping device in the form of a further conical clamping set 14.2 of smaller diameter. In this case, the annular space 16 which receives the clamping set 14.2 is taken out of the spindle. The fastening of the spindle 7 is therefore characterized in that the latter is clamped in the housing lower part 8 via two bending-torque-dependent, differently sized clamping sets 14.1 and 14.2 having a sufficiently large force engagement surface. The clamping sets 14.1 and 14.2 are fitted via the two annular spaces 12 and 16 into two constructional portions, which are provided for this purpose and are designed as cylindrical guides, between spindle and spindle receptacle.
As is apparent from the figures, the spindle 7 lies against a stop 17 which is formed by the spindle receptacle 11. For this purpose, between the upper bearing portion 15 and the lower bearing portion 13 a transition is provided from a small to a larger bore diameter and, in a corresponding manner on the spindle 7, a transition is provided from a larger to a small shaft diameter. This stop 17 in the axial direction defines the fitting depth of the spindle 7 in the spindle receptacle 11.
The clamping sets used in this embodiment each have three elements which are displaceable in relation to one another, wherein the required clamping force is set via corresponding screw assemblies. As is apparent, the upper clamping set 14.1 is oriented in such a manner that the conical inner ring 20 lying against the upper bearing portion 15 tapers downward toward the lower bearing portion 13. By contrast, the lower clamping set 14.2 is oriented in such a manner that the conical inner ring 19 lying against the lower bearing portion 13 tapers upward toward the upper bearing portion 15.
In the embodiment, use is made of commercially available clamping sets 14.1, 14.2 which each comprise a closed inner ring 20 and two closed pressure rings 21.1 and 21.2 lying one behind the other, wherein each of the pressure rings 21.1 and 21.2 is braced via a separate screw assembly 22. The upper clamping set 14.1 is oriented here in such a manner that the heads of the screws 22 are accessible from above when the eccentric bushing is removed, wherein the lower clamping set 14.2 can be braced by screws, the heads of which are accessible from below.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2014 105 046.0 | Apr 2014 | DE | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2015/057014 | 3/31/2015 | WO | 00 |
