Patent Grant
10493459
This application is a § 371 National Stage Application of PCT International Application No. PCT/EP2013/062762 filed Jun. 19, 2013 claiming priority of EP Application No. 12178291.6, filed Jul. 27, 2012.
The present invention relates to a gyratory crusher comprising a crushing head on which a first crushing shell is mounted; and a frame on which a second crushing shell is mounted, which second crushing shell defines, together with the first crushing shell, a crushing gap, the crushing head being arranged to, when the crusher is operated, execute a gyratory movement for crushing of material that is introduced in the crushing gap. The invention also relates to a slide bearing lining for such a crusher.
A gyratory crusher of the kind stated above can be used for crushing, for example, ore and rock material into smaller size. WO 99/22869 discloses an exemplary gyratory crusher, in which a crushing head is mounted on a gyrating vertical shaft. The vertical position of the vertical shaft can be adjusted, so as to allow adjustment of the width of the crushing gap in which material is crushed.
There is a need to reduce the weight of gyratory crushers. There is also a need to reduce the investment and operation costs of such crushers, and to increase their service interval.
It is an object of the present invention to solve, or at least mitigate, parts or all of the above mentioned problems.
To this end, there is provided a gyratory crusher comprising a crushing head on which a first crushing shell is mounted; a frame on which a second crushing shell is mounted, which second crushing shell defines, together with the first crushing shell, a crushing gap; and an eccentric having an inner slide bearing surface and an outer slide bearing surface, the inner slide bearing surface defining, together with an opposing slide bearing surface, an inner slide bearing, and the outer slide bearing surface defining, together with another opposing slide bearing surface, an outer slide bearing, the eccentric being rotatably connected to the frame so as to allow a rotation about an eccentric axis of rotation which is fixed relative to the frame, the eccentric axis of rotation being defined by one of said inner and outer slide bearings, the crushing head being rotatably connected to the eccentric so as to allow a rotation about a crushing head axis which is fixed relative to said eccentric, the crushing head axis of rotation being defined by the other of said inner and outer slide bearings, the crushing head thereby being arranged to, when the crusher is operated, execute a gyratory movement about the eccentric axis for crushing of material that is introduced in the crushing gap, wherein the inner slide bearing has a total height-to-diameter quotient, H1/D1, of less than 1.0. Preferably the height-to-diameter quotient, H1/D1, of the inner slide bearing is less than 0.85, more preferably less than 0.75, and even more preferably less than 0.65. Preferably, the height-to-diameter quotient, H1/D1, is larger than 0.35. Thereby, the weight of the crusher may be significantly reduced. Using such a total height-to-diameter quotient H1/D1 of the inner slide bearing, the total weight of the entire crusher may be reduced by about 2-8%, compared to known crushers, without sacrificing the load resistance of the inner slide bearing. Such a weight reduction is of particular value for mobile crushers, which may be adapted to be transported by e.g. lorry. Such a total height-to-diameter quotient H1/D1 may also reduce the investment and operating costs of crushers, as will be elucidated in detail further below.
According to one embodiment, the outer slide bearing has a total height-to-diameter quotient, H2/D2, of less than 0.5. Preferably the height-to-diameter quotient, H2/D2, of the outer slide bearing is less than 0.45, and even more preferably less than 0.40. Preferably, the height-to-diameter quotient, H2/D2, is larger than 0.15. Thereby, the weight of the crusher may be reduced even further. Using such a total height-to-diameter quotient of the outer slide bearing, the total weight of the entire crusher may be reduced by about 4-8%, compared to known crushers, without sacrificing the load resistance of the outer slide bearing.
According to one embodiment, in which the crushing head is vertically slidable relative to the frame so as to allow changing the width of the crushing gap, a quotient, HL/D, between the maximum vertical travel length of the crushing head and the horizontal diameter of the crushing head exceeds 0.16. Preferably the quotient, HL/D, between the maximum vertical travel length and the horizontal diameter of the crushing head exceeds 0.18, and even more preferably exceeds 0.24. Instead of, or in combination with a weight reduction, the lower bearing height may be benefitted from by increasing the crushing head travel length. Thereby, it is possible to use thicker crushing shells, which enables an increase of the crushing power and/or an increase in the replacement interval of the crushing shells.
According to an embodiment, the eccentric axis of rotation is defined by the outer slide bearing, and the crushing head axis of rotation is defined by the inner slide bearing. Such an arrangement is commonly used in crushers having a top bearing arranged in a top spider.
According to one embodiment the gyratory crusher comprises a hydraulically movable crushing head shaft piston supporting a crushing head shaft on which the crushing head is mounted. An advantage of this embodiment is that a width of a crushing gap formed between the two crushing shells can be adjusted in an efficient manner.
According to one embodiment at least one of the inner and outer slide bearings is at least partly arranged inside an interior cavity of a crushing head shaft piston. An advantage of this embodiment is that a short crusher may be designed, still with a relatively long vertical travel length.
According to one embodiment the inner and outer slide bearings are both at least partly arranged inside an interior cavity of the crushing head shaft piston. With both inner and outer slide bearing at least partly arranged inside of the interior cavity of the crushing head shaft piston, and with at least the inner slide bearing having a low height-to-diameter quotient, a very short and compact crusher design may be obtained.
According to one embodiment an inner bearing lining of the inner slide bearing and an outer bearing lining of the outer slide bearing are both arranged on the eccentric. An advantage of this embodiment is that the inner and outer slide bearings will be aligned with each other, such that crushing forces may be transferred from the crushing head shaft to the frame in the most efficient manner, with no, or only limited, uneven load on the bearing linings. The inner and outer bearing linings could be separate bearing linings mounted on the eccentric, and/or could be bearing linings formed in the eccentric itself, if the eccentric is at least partly made from a bearing material.
According to one embodiment at least one of the inner and outer slide bearings comprises at least one lubricant supply groove. An advantage of this embodiment is that efficient lubrication of the slide bearing may be obtained, thereby increasing its life and ability to withstand high-load situations.
According to one embodiment the lubricant supply groove separates the at least one slide bearing into at least a first portion and a second portion. An advantage of this embodiment is that lubricant may be efficiently distributed to the entire slide bearing.
According to one embodiment at least one of the inner and outer slide bearings comprises a first portion having a first diameter, and a second portion having a second diameter, which is smaller than the first diameter. An advantage of this embodiment is that efficient bearing function may be obtained also in a gyratory crusher involving a crushing head shaft and/or an eccentric that has a varying diameter along its length.
According to one embodiment the eccentric is at least partly made from bearing material, the eccentric forming part of at least one of the inner and outer bearings. An advantage of this embodiment is that the number of parts in the crusher may be reduced, since linings of the slide bearings may be at least partly dispensed with.
According to another aspect of the invention, parts or all of the above mentioned problems are solved, or at least mitigated, by an inner slide bearing lining for an inner slide bearing of an eccentric of a gyratory crusher, wherein the inner slide bearing lining has a height-to-diameter quotient, H1/D1, of less than 1.0. Preferably the height-to-diameter quotient, H1/D1, of the inner slide bearing lining is less than 0.85, more preferably less than 0.75, and even more preferably less than 0.65. Preferably, the height-to-diameter quotient, H1/D1, is larger than 0.35. Using such a total height-to-diameter quotient, the total weight of the entire crusher may be reduced by about 2-8%, compared to known crushers, without sacrificing the load resistance of the inner slide bearing.
According to an embodiment, the inner slide bearing lining has a non-uniform thickness so as to define a circular-cylindrical inner surface which is eccentric with respect to a circular-cylindrical outer surface. Such a slide bearing lining allows an adjustable setting of a total eccentricity of the eccentric.
According to yet another aspect of the invention, parts or all of the above mentioned problems are solved, or at least mitigated, by an outer slide bearing lining for an outer slide bearing of an eccentric of a gyratory crusher, wherein the outer slide bearing lining has a height-to-diameter quotient, H2/D2, of less than 0.5. Preferably the height-to-diameter quotient, H2/D2, of the outer slide bearing lining is less than 0.45, and even more preferably less than 0.40. Preferably, the height-to-diameter quotient, H2/D2, is larger than 0.15. Using such a total height-to-diameter quotient, the total weight of the entire crusher may be reduced by about 2-8%, compared to known crushers, without sacrificing the load resistance of the outer slide bearing.
According to one embodiment an inner and/or an outer slide bearing has a Sommerfeld number, S, which is less than 120. Preferably, the Sommerfeld number, S, of the inner and/or outer slide bearing is less than 70, more preferably less than 40, and even more preferably less than 20. Such values of the Sommerfeld number, S, of the slide bearing has been found to improve the capacity of the slide bearing to operate at high crushing loads also at low height-to-diameter quotients H1/D1, and H2/D2, respectively. Preferably, the Sommerfeld number is higher than 2, more preferably higher than 3, and even more preferably above 4.
According to one embodiment an inner and/or an outer bearing has a relative clearance of between about 2*10−4 and about 5*10−3.
According to yet another aspect of the invention a gyratory crusher comprises
a crushing head on which a first crushing shell is mounted;
a frame on which a second crushing shell is mounted, which second crushing shell defines, together with the first crushing shell, a crushing gap,
an eccentric to which a crushing head shaft, on which the crushing head is mounted, is rotatably connected, the crushing head thereby being arranged to, when the crusher is operated, execute a gyratory movement for crushing material that is introduced in the crushing gap,
an inner slide bearing arranged between the eccentric and the crushing head shaft,
a hydraulically movable crushing head shaft piston supporting the crushing head shaft, the crushing head shaft piston having an interior cavity,
an outer slide bearing arranged between the eccentric and the crushing head shaft piston to allow the eccentric to rotate relative to the crushing head shaft piston, wherein
the inner and outer slide bearings are both arranged, at least partly, inside the interior cavity of the crushing head shaft piston,
and wherein an inner bearing lining of the inner slide bearing and an outer bearing lining of the outer slide bearing both being arranged on the eccentric.
An advantage of this gyratory crusher is that crushing forces may be transferred from the crushing head shaft to the frame, via the eccentric and the crushing head shaft piston via inner and outer slide bearing linings that are aligned with each other, since they are both arranged on the eccentric, regardless of the present vertical position of the crushing head shaft and the crushing head shaft piston. This increases the crushing forces that may be transferred from the crushing head shaft to the frame, and increases the life of the inner and outer slide bearings.
According to one embodiment at least one of the inner and outer slide bearing linings is a separate bearing lining mounted on the eccentric. According to one embodiment the inner and outer slide bearing linings are both separate bearing linings mounted on the eccentric.
According to one embodiment at least one of the inner and outer slide bearing linings is a bearing lining formed in the eccentric itself, wherein the eccentric is at least partly made from a bearing material. According to one embodiment the inner and outer slide bearing linings are both formed in the eccentric itself.
The above, as well as additional objects, features and advantages of the present invention, will be better understood through the following illustrative and non-limiting detailed description of preferred embodiments of the present invention, with reference to the appended drawings, where the same reference numerals will be used for similar elements, wherein:
When the drive shaft 14 rotates the eccentric sleeve 10, during operation of the crusher 1, the crushing head shaft 2 and the crushing head 12 mounted thereon will execute a gyrating movement.
An inner crushing shell 20 is mounted on the crushing head 12. An outer crushing shell 22 is mounted on the frame top part 8. A crushing gap 24 is formed between the two crushing shells 20, 22. When the crusher 1 is operated, material to be crushed is introduced in the crushing gap 24 and is crushed between the inner crushing shell 20 and the outer crushing shell 22 as a result of the gyrating movement of the crushing head 12, during which movement the two crushing shells 20, 22 approach one another along a rotating generatrix and move away from one another along a diametrically opposed generatrix.
At its lower end 26 the crushing head shaft 2 is supported on a thrust bearing 28. The thrust bearing 28 is mounted on an upper face of a crushing head shaft piston 30. The vertical position H of the crushing head shaft piston 30 may be hydraulically adjusted by controlling the amount of hydraulic fluid in a hydraulic fluid space 32 at the lower end of the piston 30. Thereby, the width of the crushing gap 24 may be adjusted.
The crushing head shaft 2 is radially supported in the eccentric sleeve 10 via an inner slide bearing 34, which allows the eccentric sleeve 10 to rotate around the crushing head shaft 2. The inner slide bearing 34 may comprise an optional inner bearing lining 36 of a material different from the material of the crushing head shaft 2 and the eccentric sleeve 10. The inner slide bearing 34 is lubricated in a non-illustrated manner.
The eccentric sleeve 10 is radially supported in the frame bottom part 6 via an outer slide bearing 38, which allows the eccentric sleeve 10 to rotate in the frame bottom part 6. The outer slide bearing 38 may comprise an optional outer bearing lining 40, of a material different from the material of the eccentric sleeve 10 and the frame bottom part 6. Together, the inner and outer slide bearings 34, 38 form an eccentric bearing arrangement 42 for guiding the crushing head 12 along a gyratory path.
In accordance with an alternative embodiment the eccentric sleeve 10 may itself be manufactured from a bearing material. In such a case one or both of the inner and outer bearing linings 36, 40 may be made from the same material as the eccentric sleeve 10. According to a further embodiment, one or both of the inner and outer bearing linings 36, 40 may be integral with the eccentric sleeve 10 itself. The latter may, for example, be achieved by a portion of the inner periphery of the eccentric sleeve 10 being arranged for functioning as an inner bearing lining, and/or a portion of the outer periphery of the eccentric sleeve 10 being arranged for functioning as an outer bearing lining.
Returning now to
The cross-sectional view of
The eccentric sleeve 10 has an outer slide surface 48 for sliding along an inner slide surface 50 of the outer bearing lining 40. The outer bearing lining 40 is fit into, and forms part of the frame bottom part 6. Together, the outer slide surface 48 of the eccentric sleeve 10 and the inner slide surface 50 of the frame bottom part 6 define said outer slide bearing 38.
The inner slide bearing 34 has a diameter D1, which is defined as the diameter of the inner slide surface 46 of the eccentric sleeve 10. Similarly, the outer slide bearing 38 has a diameter D2, which is defined as the diameter of the outer slide surface 48 of the eccentric sleeve 10.
Referring back to
Similarly, the outer slide bearing has a total height H2, defined as the lowest of the total height of the outer slide surface 48 (
Each of the slide surfaces 44, 46, 48, 50 of the inner and outer slide bearings 34, 38 is, in
In accordance with one example, the inner slide bearing 34 may have a total height-to-diameter quotient H1/D1 of about 0.6, and the outer slide bearing 38 may have a total height-to-diameter quotient H2/D2 of about 0.38. Thanks to this the weight, and also the height of the crusher may be significantly reduced. Compared to known crushers, the weight of the bearing arrangement 42, the eccentric sleeve 10, and the frame bottom part 6 may be reduced by 40% or more, using, for example, the total height-to-diameter quotients H1/D1=0.6 and H2/D2=0.38, without sacrificing the load resistance or strength of the inner and outer slide bearings 34, 38. This may typically correspond to a total weight reduction of the entire crusher 1 of about 4-8%, and a height reduction of about 3-6%. Furthermore, the inner and outer slide bearing linings 36, 40 are typically fabricated in a relatively expensive soft metal alloy; the reduction of the height of the bearing linings 36, 40 represents a significant cost saving.
The vertical travel length, depicted with HL in
Even further, lower inner and/or outer slide bearings 34, 38 result in a reduced bearing friction. The reduced friction may reduce the total power consumption of the bearing arrangement 42 by about 30%, which reduces the cost of operating the crusher 1. Moreover, reduced friction reduces the risk of the crushing head 12 starting to spin at high RPM when no material to be crushed is present in the crushing gap 24.
A low inner bearing 34 also allows a greater tilt of the shaft 2 inside the inner bearing 34 without risking causing damage to the bearing 34. Thereby, a shorter inner bearing 34, i.e. an inner bearing 34 having a short vertical extent, may be better suited to carry higher radial loads than a tall bearing, i.e. a bearing with a long vertical extent, and/or may relieve the requirements on the strength of the crushing head shaft 2, since the bearing 34 will be less sensitive to bending of the shaft 2 or any other type of displacement e.g. caused by machining tolerances.
In fact, it is possible to even further reduce the total height-to-diameter quotient, H1/D1, of the inner slide bearing 34 to less than 0.4, and the total height-to-diameter quotient, H2/D2, of the outer slide bearing 38 to less than 0.3, with maintained load resistance of the respective bearings.
Preferably the height-to-diameter quotient, H1/D1 of the inner slide bearing 34 is less than 1.0. Preferably the height-to-diameter quotient, H1/D1, of the inner slide bearing 34 is less than 0.85, more preferably less than 0.75, and even more preferably less than 0.65. Preferably, the height-to-diameter quotient, H1/D1, is larger than 0.35.
Preferably the outer slide bearing 38 has a height-to-diameter quotient, H2/D2, of less than 0.5. Preferably the height-to-diameter quotient, H2/D2, of the outer slide bearing 38 is less than 0.45, and even more preferably less than 0.40. Preferably, the height-to-diameter quotient, H2/D2, is larger than 0.15.
Preferably, for reliable operation, each of the inner and outer bearings 34, 38 has a relative clearance of between about 2*10−4 and about 5*10−3, respectively. By way of example, a diameter D1 of the inner slide bearing 34 may be 300 mm. By multiplying such diameter D1 by a suitable relative clearance a diametral clearance, in mm, can be obtained. For a diameter D1 of 300 mm, and a relative clearance ξ of 3*10−3 a diametral clearance of the inner slide bearing 34 may, for example, be 3*10−3*300 mm=0.9 mm.
The Sommerfeld number, S, described in, for example, Shigley, Joseph Edward; Mischke, Charles R. (1989). Mechanical Engineering Design. New York: McGraw-Hill, page 483, is a number that takes into account both the physical features of a slide bearing and the conditions under which the slide bearing operates. Each of the inner and outer slide bearings 34, 38 may preferably have a Sommerfeld number, S, which is less than 120. Preferably, the Sommerfeld number, S, of each of the inner and outer slide bearings 34, 38 is less than 70, and more preferably the Sommerfeld number, S, is less than 40, and even more preferably the Sommerfeld number, S, is less than 20. Such values of the Sommerfeld number, S, of the slide bearings 34, 38 have been found to improve the capacity of the slide bearings 34, 38 to operate at high crushing loads also at low height-to-diameter quotients H1/D1, and H2/D2, respectively. Preferably, the Sommerfeld number is higher than 2, and more preferably higher than 3, and even more preferably above 4, since a lower Sommerfeld number tends to increase the investment and operating costs. Thereby, the bearing will be suited for a lubricant having a typical viscosity, according to the ISO-VG scale, of between 100 and 460.
A typical RPM of the crusher 1, when operated, may be between about 150 rpm and about 500 rpm as measured at the eccentric sleeve 10; the RPM may typically be selected so as to obtain a sliding speed in each of the inner and outer slide bearings of between about 2 m/s and about 20 m/s.
An outer crushing shell 122 is mounted on the frame top part 108 and forms together with the inner crushing shell 120 a crushing gap 124 in which material is crushed during operation of the crusher 101 as a result of the gyrating movement of the crushing head 112.
At its lower end 126 the crushing head shaft 102 is supported on a thrust bearing 128. The thrust bearing 128 is mounted in the cavity 131 of the “bucket” shaped crushing head shaft piston 130. The “bucket” shaped crushing head shaft piston 130 is arranged in a hydraulic cylinder 133. The hydraulic cylinder 133 comprises a hydraulic fluid space 132 arranged between the lower end of the piston 130 and the bottom of the hydraulic cylinder 133. The vertical position H of the crushing head shaft piston 130 may be hydraulically adjusted by controlling the amount of hydraulic fluid in the hydraulic fluid space 132. Thereby, the width of the crushing gap 124 may be adjusted.
The crushing head shaft 102 is radially supported in the eccentric sleeve 110 via the inner slide bearing 134, which allows the eccentric sleeve 110 to rotate around the crushing head shaft 102. The crushing head shaft 102 may also slide in a vertical direction in the inner slide bearing 134 as an effect of varying amounts of hydraulic fluid being supplied to the hydraulic fluid space 132. The inner slide bearing 134 may comprise an optional inner bearing lining 136. The inner slide bearing 134, and the inner bearing lining 136, if any, are at least partly located inside the “bucket” shaped crushing head shaft piston 130.
The eccentric sleeve 110 is radially supported in the “bucket” shaped crushing head shaft piston 130 via the outer slide bearing 138, which allows the eccentric sleeve 110 to rotate inside of the crushing head shaft piston 130. Also the outer slide bearing 138 may comprise an optional outer bearing lining 140. Together, the inner and outer slide bearings 134, 138 form an eccentric bearing arrangement 142 for guiding the crushing head 112 along a gyratory path. The eccentric bearing arrangement 142 functions according to similar principles as has been described hereinabove with regard to the bearing arrangement 42 and with reference to
The inner slide bearing 134 has a total height H1 which is defined in a similar manner as the total height H1 of the slide bearing 34, and the outer slide bearing 138 has a total height H2, which is defined in a similar manner as the total height H2 of the slide bearing 38, as described hereinbefore.
In accordance with one example, the inner slide bearing 134 may have a total height-to-diameter quotient H1/D1 of about 0.8, and the outer slide bearing 138 may have a total height-to-diameter quotient H2/D2 of about 0.44. Thanks to this the weight, and also the height of the crusher 101 may be significantly reduced, similar as with the crusher 1 described hereinbefore with reference to
The vertical travel length, depicted with HL in
Preferred values of the height-to-diameter quotient, H1/D1, of the inner slide bearing 134, and of the height-to-diameter quotient, H2/D2, of the outer slide bearing 138 are similar as the values for the slide bearings 34, 38 described hereinbefore.
The bearing arrangement 242 which is illustrated in
The eccentric sleeve 210 is radially supported in a frame bottom part 206 via the outer slide bearing 238, which allows the eccentric sleeve 210 to rotate relative to the frame bottom part 206 and the frame, not shown in
The crushing head shaft 202 has a first diameter DS1 at an upper portion 203 of the crushing head shaft 202, and a second diameter DS2 at a lower portion 205 of the crushing head shaft 202. The first diameter DS1 is larger than the second diameter DS2. The inner slide bearing 234 has a first, upper, portion 235 that matches with the upper portion 203 of the crushing head shaft 202 and has the diameter DS1, and a second, lower, portion 237 that matches with the lower portion 205 of the crushing head shaft 202 and has the diameter DS2.
The inner slide bearing 234 has a total height H1 which extends from an upper end 235a of the upper portion 235 to a lower end 237a of the lower portion 237. The total height H1 of the inner slide bearing 234 is related to a diameter D1, which is equal to DS1 and is the largest diameter of the inner slide bearing 234. In accordance with one example the inner slide bearing 234 may have a total height-to-diameter quotient H1/D1 of about 0.70.
The outer slide bearing 238 has a first, upper, portion 239 and a second, lower, portion 241. A lubricant supply groove 243 separates the first, upper, portion 239 from the second, lower, portion 241. The lubricant supply groove 243 is arranged for supplying lubricating fluid, such as hydraulic oil, to the upper and lower portions 239, 241.
The outer slide bearing 238 has a total height H2 which extends from an upper end 239a of the upper portion 239 to a lower end 241a of the lower portion 241. The total height H2 of the outer slide bearing 238 is related to a diameter D2, which is the diameter of the outer slide bearing 238. In accordance with one example the outer slide bearing 238 may have a total height-to-diameter quotient H2/D2 of about 0.42.
Preferred values of the height-to-diameter quotient, H1/D1, of the inner slide bearing 234, and of the height-to-diameter quotient, H2/D2, of the outer slide bearing 238 are similar as the values for the slide bearings 34, 38 described hereinbefore.
In the embodiment of
At its lower end 326 the crushing head shaft 302 is supported on a thrust bearing 328 mounted in the cavity 331 of the “bucket” shaped crushing head shaft piston 330. The crushing head shaft piston 330 is arranged in a hydraulic cylinder 333 which comprises a hydraulic fluid space 332 arranged between the lower end of the piston 330 and the bottom of the hydraulic cylinder 333. The vertical position H of the crushing head shaft piston 330 may be hydraulically adjusted by controlling the amount of hydraulic fluid present in the hydraulic fluid space 332. Thereby, the width of the crushing gap 324 may be adjusted in a similar manner as in the crusher 101 described hereinbefore.
The crushing head shaft 302 is radially supported in the eccentric sleeve 310 via an inner slide bearing 334, which allows the eccentric sleeve 310 to rotate around the crushing head shaft 302. The crushing head shaft 302 may also slide in a vertical direction, as indicated by an arrow VS, in the inner slide bearing 334 as an effect of varying amounts of hydraulic fluid being supplied to the hydraulic fluid space 332. Varying amounts of hydraulic fluid supplied to the hydraulic fluid space 332 will, hence, cause the head shaft piston 330 and the crushing head shaft 302 to move in the vertical direction, along arrow VS, while the eccentric sleeve 310 remains in a constant vertical position.
The inner slide bearing 334 may comprise an optional inner bearing lining 336. The bearing lining 336 is mounted on the eccentric 310. Hence, the bearing lining 336 will have a fixed position in the vertical direction, and will not move in the vertical direction as the crushing head shaft 302 moves vertically under the action of the hydraulic cylinder 333.
According to an alternative embodiment, the eccentric 310 is made, in itself, and at least on the inside thereof, from a bearing material. In such a case the reference 336 of
Returning to
The eccentric sleeve 310 is radially supported in the “bucket” shaped crushing head shaft piston 330 via an outer slide bearing 338, which allows the eccentric sleeve 310 to rotate inside of the crushing head shaft piston 330. Also the outer slide bearing 338 may comprise an optional outer bearing lining 340. The bearing lining 340 is mounted on the eccentric 310. Hence, the bearing lining 340 will have a fixed position in the vertical direction, and will not move in the vertical direction as the “bucket” shaped crushing head shaft piston 330 moves vertically under the action of the hydraulic cylinder 333.
According to an alternative embodiment, the eccentric 310 is made, in itself, and at least on the outside thereof, from a bearing material. In such a case the reference 340 of
Together, the inner and outer slide bearings 334, 338 form an eccentric bearing arrangement 342 for guiding the crushing head 312 along a gyratory path.
Since the bearing lining 336 of the inner slide bearing 334 and the bearing lining 340 of the outer slide bearing 338 are both mounted on the eccentric 310, the two bearing linings 336, 340 will always be aligned with each other, regardless of the present vertical position of the “bucket” shaped crushing head shaft piston 330 and of the crushing head shaft 302. As a result the crushing forces, represented by an arrow FC in
The fact that the bearing linings 336, 340 are always aligned with each other, due to the fact that they are both mounted on the eccentric 310, reduces the risk of damages to the bearings that could occur when crushing forces are transferred via misaligned bearing linings.
The invention has mainly been described above with reference to a few embodiments. However, as is readily appreciated by a person skilled in the art, other embodiments than the ones disclosed above are equally possible within the scope of the invention, as defined by the appended patent claims.
For example, in the crusher 1 illustrated on the appended drawings, the crushing head shaft 2 is eccentrically journalled in the eccentric sleeve 10 in such a manner that it follows the gyratory motion of the crushing head 12. Thereby, the eccentric sleeve axis of rotation C, which is fixed relative to the frame 4, is defined by the outer slide bearing, and the inner slide bearing defines the crushing head axis A, which coincides with the centre of the crushing head shaft 2. However, the teachings disclosed herein are also valid for crushers that are not provided with a top spider, e.g. crushers having a fixed crushing head shaft. In such a crusher, the eccentric sleeve axis of rotation C, which is fixed relative to the frame, will be defined by the inner slide bearing, which rests upon and coincides with the centre of the crushing head shaft. The crushing head will be mounted onto the outer slide bearing, which defines the crushing head axis A. An exemplary crusher of the type with fixed crushing head shaft is described in US 2003/0136865. Furthermore, the teachings disclosed herein are also valid for crushers that are not provided with a top spider and have a rotating crushing head shaft, such as disclosed in U.S. Pat. No. 3,325,108.
| Number | Date | Country | Kind |
|---|---|---|---|
| 12178291 | Jul 2012 | EP | regional |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2013/062762 | 6/19/2013 | WO | 00 |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO2014/016059 | 1/30/2014 | WO | A |
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|---|---|---|---|
| 2833486 | MacLeod | May 1958 | A |
| 4034922 | Coxhill | Jul 1977 | A |
| 4892257 | Stoeckmann et al. | Jan 1990 | A |
| 5152468 | Virtamo et al. | Oct 1992 | A |
| 20020074437 | Savolainen | Jun 2002 | A1 |
| Number | Date | Country |
|---|---|---|
| 560289 | Feb 1958 | BE |
| 103749 | Apr 2011 | RU |
| 2452571 | Jun 2012 | RU |
| 795555 | Jan 1981 | SU |
| 2005075082 | Aug 2005 | WO |
| 2008103096 | Aug 2008 | WO |
| 2011005169 | Jan 2011 | WO |
| Number | Date | Country | |
|---|---|---|---|
| 20150290649 A1 | Oct 2015 | US |
