WO2014166539A1

WO2014166539A1 - Cone crusher with main shaft centring assembly

Info

Publication number: WO2014166539A1
Application number: PCT/EP2013/057591
Authority: WO
Inventors: Johan Gunnarsson; Mats HJERTHEN; Konstantin Belotserkovskiy
Original assignee: Sandvik Intellectual Property Ab
Priority date: 2013-04-11
Filing date: 2013-04-11
Publication date: 2014-10-16

Abstract

A cone crusher (100) is provided having a bushing and eccentric weight support assembly (112) positioned below a region of the main shaft (106) of the crusher within the internal crushing chamber (110) defined by the crusher main frame (102). The support assembly comprises a pair of arms (202) supported upon a base (200, 201, 212) and configured to move towards and away from one another to trap and hold the bushing (118, 119) and/or the eccentric assembly (107) in fixed axial position within the crusher independently of support by the main shaft.

Description

Cone Crusher with Main Shaft Centring Assembly

Field of invention

The present invention relates to cone crusher maintenance apparatus and in particular, although not exclusively to apparatus to support and centre selected components of the crusher associated with the main shaft during maintenance procedures.

Back round art Gyratory crushers are used for crushing ore, mineral and rock material to smaller sizes.

Typically, the crusher comprises a crushing head mounted upon an elongate main shaft. A first crushing shell (typically referred to as a mantle) is mounted on the crushing head and a second crushing shell (typically referred to as a concave) is mounted on a frame such that the first and second crushing shells define together a crushing gap through which material to be crushed is passed. A driving device positioned at a lower region of the main shaft is configured to rotate an eccentric assembly about the shaft to cause the crushing head to perform a gyratory pendulum movement and crush the material introduced in the crushing gap. Typically, the frame of the crusher that, in part, defines the crushing zone is divided into a top shell and a bottom shell.

More recently, a further generation of crusher has emerged that offers enhanced material processing by combining aspects of conventional crushing and grinding principals. An example next generation crusher is described in US 2010/0102152. In order to achieve an enhanced material processing action, the main shaft that carries the head and mantle is mounted in such a way that it is capable of swinging unrestrained inside the crushing chamber with respect to the concave mounted at the top shell.

However, and common with earlier crusher types, the main shaft and crushing head are required to be lifted routinely from the crushing chamber to replace the mantle and other wear parts. As a region of the main shaft is surrounded by an eccentric weight and an intermediate cylindrical bushing, the lifting and reassembly process is commonly a multi- stage operation so as to avoid loss of the bushing and weight into the crushing chamber as the main shaft is raised vertically upward. Currently, three hydraulic cylinders axially mounted at a lower region of the crusher are actuated to provide a common support platform for the eccentric weight and bushing to maintain their position within the crusher as the main shaft is extracted from the chamber.

However, the necessary full extension of these cylinders is problematic by introducing fluid leakage problems and instability as the cylinders are incapable of withstanding lateral loading forces. Commonly, additional supports are required under the eccentric weight due to the risk of failure of one or more of the cylinders. Furthermore, the cylinders do not ensure the bushing and weight are 'centred^'' immediately prior to reassembly into the crusher which in turn necessitates adding further steps to the reassembly process and delays in crusher downtime. Finally, access by service personnel to at least some of the support cylinders is typically difficult if not impossible. What is required is apparatus that facilitates the maintenance and repair of the crusher including its wear parts and addresses the above problems. Summary of the Invention

It is an object of the present invention to provide maintenance apparatus for a cone crusher and in particular a means of supporting selected components (for example a bushing and/or eccentric weight) mounted about the main shaft of the crusher so as to prevent such components from falling downwardly into the crushing chamber as the main shaft is lifted vertically upward for repair and maintenance. It is a further objective to provide a support assembly that is configured to automatically centre the bushing (and eccentric weight) during the maintenance process so as to greatly facilitate reintroduction of the main shaft into the crushing chamber.

The objectives are achieved by providing maintenance and centring apparatus forming an integral part of and positioned within the body of the crusher having a pair arms configured to move back and forth relative to one another and to catch' and hold the bushing.

Optionally, the arms are actuated via operation of a linear actuator aligned in a plane corresponding to the movement plane of the arms. Preferably, the arms are mounted within the crusher via pivot pins so as to be capable of pivoting movement relative to one another. Advantageously, when clamped about the main shaft bushing, the apparatus may further comprise locking elements configured to positionally lock the arms via a mechanical or magnetic latching mechanism. This latch assembly isolates the linear actuator from the loading forces resultant from the weight of the bushing and/or other main shaft components to avoid damage and fatigue to the actuator. Optionally the mechanism comprises moveable locking wedges that are shaped and positioned specifically with respect to the arms to increase the frictional contact force between the arms and the bushing as the wedges are moved towards and into engagement with the arms.

Additionally, the present apparatus is configured to centre the eccentric weight and bushing to allow convenient reintroduction of the main shaft at the end of the maintenance procedure. Reference within the specification to a bushing support assembly encompasses an assembly configured to positionally support the bushing and eccentric weight that is co- located with the bushing. In particular, reference to a bushing and eccentric weight as individual components encompasses the bushing and eccentric weight forming a single unitary structure such that the present support assembly is configured to support the bushing and eccentric weight as a single unit. According to a first aspect of the present invention there is provided a cone crusher comprising: a frame that defines an internal crushing chamber; a main shaft extending through the internal chamber, the main shaft mounting a crushing head at or towards a first upper end and a bushing at or towards a second lower end; a bushing support assembly mounted within the crusher at or below a region of the bushing; the crusher characterised in that the support assembly comprises: a pair of arms supported by a base, each arm having an engaging portion to contact the bushing, the arms capable of moving such that the engaging portions of each respective arm can move away and towards one another to trap and hold the bushing at a fixed axial position within the crusher independently of support of the bushing by the main shaft.

Preferably, the crusher further comprises a linear actuator connecting the arms and operative by linear extension to respectively force together the pair of engaging portions by movement of the arms. Preferably, the crusher further comprises a bias member connected to and acting on the arms to force the engaging portions of each respective arm apart relative to one another. In one embodiment, the bias member forms a component part of the linear actuator. According to further embodiments, the bias member and the linear actuator are separate components and may be positioned at the same or different locations and connection positions at the arms. Preferably, the crusher further comprises a fluid reservoir in communication with the linear actuator. Preferably, the crusher further comprises control means to automatically and remotely control the linear actuator from a region outside the internal chamber.

Preferably, the crusher further comprises a first arm-stabilising component positioned towards a first end of the arms closest to the engaging portions relative to a second end, the stabilising component having a first part that is positioned under the arms and a second part positioned above the arms so that the arms are capable of moving laterally between the first and second part. Preferably, the first part comprises a first substantially planar plate and the second part comprises a second substantially planar plate, the first and second plates being aligned substantially parallel.

Preferably, the crusher further comprises a second arm-stabilising component positioned towards a second end of the arms furthest from the engaging portions relative to a first end, the stabilising component having a first part that is positioned under the arms and a second part positioned above the arms so that the arms are capable of moving laterally between the first and second part. Preferably, the first part comprises a first substantially planar plate and the second part comprises a second substantially planar plate, the first and second plates being aligned substantially parallel.

Optionally, the crusher further comprises a latch or lock assembly mounted adjacent to at least one of the arms and configured to be actuated to engage and lock at least one of the arms in fixed position at the base. Preferably, the lock assembly comprises at least one wedge component moveably mounted at the support assembly to engage and disengage a region of the at least one arm. Preferably, the lock assembly comprises a pair of moveable wedges respectively mounted adjacent each arms. According to further embodiments, the lock assembly comprises a plurality of magnets and corresponding magnetically susceptible components, the magnets being electromagnets such that when energised the arms lock in stationary position.

Optionally, the engaging portions comprise a plate-like body having a part extending perpendicular to a plane in which the arms move relative to one another such that the part of each engaging portion is orientated to be aligned substantially parallel with an axis of the main shaft.

Preferably, the base comprises a frame supported by a plurality of legs.

Preferably, the arms are pivotally mounted at the base via at least one pivot mounting. Alternatively, the arms may be slidably mounted at the base so as to move towards and away from the bushing and/or eccentric weight via a sliding action. Accordingly, the assembly may further comprise rails or suitable guide channels to support the sliding movement of the arms. Preferably, the assembly comprises two pivot mountings to respectively mount each arm at the base. The assembly preferably further comprises additional pivot mountings to attach the linear actuator to the arms. Preferably, the linear actuator and the bias member are located towards a second end of the arms. Optionally, the linear actuator comprises a one-way active hydraulic cylinder configured for extension when actuated. Optionally, the linear actuator comprises a two-way active hydraulic cylinder configured to provide a pull and push action to each arm.

Preferably, the crusher further comprises an inner frame mounted within the internal chamber, the support assembly positioned internally within the inner frame. Preferably, the support assembly is positioned below the bushing relative to a longitudinal axis extending through the crusher within the internal frame.

Optionally, the arms are pivotally actuated via a slide wedge mounted upon a shaft wherein movement of the wedge along the shaft provides actuation of the arms. Preferably, the wedge and shaft comprise cooperating screw threads wherein the wedge is moveable linearly relative to the longitudinal axis via rotation of the shaft. Preferably, the arms are pivotally coupled to the wedge via intermediate and respective link bars. Preferably, an upper region of the wedge comprises a support member configured for positioning to support a region of the eccentric weight and/or a retaining ring located axially below the eccentric weight.

Brief description of drawings A specific implementation of the present invention will now be described, by way of example only, and with reference to the accompanying drawings in which:

Figure 1 is a cross sectional side elevation view of a cone crusher comprising maintenance apparatus configured to clamp and hold a bushing located about a central main shaft of the crusher according to a specific implementation of the present invention; Figure 2 is a perspective view of the maintenance apparatus of figure 1 in an 'open^'' state ready for engagement of the bushing about the main shaft;

Figure 3 is a plan view of the maintenance apparatus, bushing and main shaft of figure 2 in the 'open^'' state disengaged from the bushing and main shaft;

Figure 4 is a further plan view of the apparatus of figure 2 engaging around the bushing and the main shaft in the 'closed' state; Figure 5 is a first perspective view of a cone crusher maintenance apparatus configured to clamp and hold a bushing located about the central main shaft of a crusher according to a further specific implementation of the present invention;

Figure 6 is a further perspective view of the maintenance apparatus of figure 5 according to the further embodiment.

Detailed description of preferred embodiment of the invention

Referring to figure 1 the crusher 100 comprises a main frame 102 that defines an internal crushing chamber 110. An upper adjustable ring frame 114, in part, closes an upper end of chamber 110. An outer crushing shell 104 (typically referred to as a concave) is mounted at the central region at a radially inward position of ring 114 relative to a longitudinal axis 121 extending through crusher 100. A crushing head 100 is supported and mounted upon a central main shaft 106 extending within chamber 110 in the longitudinal axis direction. Head 100 in turn mounts an inner crushing shell 101 (typically referred to as a mantle) positioned radially inward and opposed to outer crushing shell 104. A gap region 105 is defined between shells 101, 104 through which material to be crushed is passed. Crushed material exits gap region 105 via a discharge opening 113 with chamber 110 where it falls downwardly under gravity to be discharged from a lower region of crusher 100 (not shown). An inner frame 103 is positioned radially inward of main frame 102 and extends below a circumferentially outer region of head 100 to a base frame 120 that connects inner frame 103 to main frame 102 to close a lower region of internal chamber 110. Inner frame 103 defines an internal working part zone 111 that accommodates various working components of crusher 100 including in particular the various drive components responsible for the movement of head 101 and shaft 106 within crusher 100 that act to crush material within gap region 105 as the inner crushing shell is moved both radially and axially relative to outer crushing shell 104. An eccentric weight 107 is mounted about shaft 106 below head 100. A cylindrical bushing 118 is positioned radially intermediate weight 107 and shaft 106 to provide a seating collar for weight 107. An axially upper region 108 at bushing 118 is positioned immediately below head 100 whilst an axially lower region 119 of bushing 118 is positioned generally above a support assembly 112 that is mounted immediately above base frame 120. A retaining ring 122 is positioned axially below and supports eccentric weight 107. Retaining ring comprises a substantially planar annular disk- like

configuration having a diameter being greater than bushing 118 such that ring 122 extends radially outward from shaft 116 and bushing 118 to extend underneath weight 107. Figure 1 further illustrates selected components of the drive and movement components responsible for the movement and crushing action of head 100. Such components include a first 'dumbbell' shaped shaft 115 mounted axially above a second 'dumbbell' shaped shaft 116 with both shafts 115, 116 approximately centred upon axis 121 and mounted within a drive assembly 117 extending axially below base frame 120. Selected

components of drive assembly 117, 115, 116 are caused to rotate axially to drive axial rotation of shaft 106 and in turn eccentric weight 107. This configuration provides that head 100 is capable of moving in the x, y and z planes that acts to impart both a crushing and a grinding effect to material passing through gap region 105. Figures 2 to 4 illustrate the mounting assembly 112 in further detail. Referring to figure 2, the assembly 112 comprises a substantially square frame 201 supported at each of its four corners by perpendicular extending legs 200. Each leg 200 terminates at its lowest point in a foot 212 configured for attachment to base frame 120 via attachment bolts (not shown). Frame 201 provides a means of mounting two moveable arms 202 configured for displacement in a single plane extending substantially perpendicular to main axis 121. Each arm 202 comprises a first end 301 and a second end 205. Each arm 202 is pivotally mounted via a mounting pin 211 positioned in one half of each arm 202 along its length closest to second end 205. Pin 211 extends through each arm 202 and connects to frame 201. As illustrated in figure 3, a brace bar 303 extends between the pair of pivot pins 211 to inhibit lateral displacement as each arm 202 pivots relative to frame 201. Accordingly, each arm 202 is capable of pivoting towards and away from one another and the central longitudinal axis 121 to define 'open' and 'closed' (clamping) configurations relative to bushing region 119.

Actuation and control of the pivoting arms 202 is provided by a hydraulic cylinder 203 coupled to the second end 205 of each arm 202 via a respective pivot mounting 206. According to the specific embodiment, cylinder 203 is a one-way hydraulic ram operative by actuation via remote control (not shown) to extend and move the first end 302 of each arm 202 towards one another. A fluid reservoir 300 is coupled to cylinder 203. A bias member in the form of a coil spring 204 is formed as an integral part of cylinder and reservoir arrangement 203, 300 and acts to return arm 202 to the open configuration with first ends 301 being spaced apart relative to one another and axis 121.

According to this specific implementation, the assembly 112 further comprises a mechanical latch mechanism in the form of two wedges 214 positioned at each arm second end 205. Each wedge 214 may be operated by sliding movement into engagement with arm end 205 so as to positionally lock each arm 202 relative to one another in the closed configuration. This latching assembly 214 is configured to isolate linear actuator 203, 300 to provide a mechanical lock such that each arm 202 is clamped in the closed position with first arm ends 301 at a minimum separation distance relative to one another. Assembly 112 further comprise a first pair of substantially parallel stabilising plates mounted at frame 201 and positioned at the first end 301 of each arm 202. In particular, a first plate 209 is positioned axially above each end 301 whilst a second plate 210 is positioned axially below each arm end 301 such that each arm end 301 is capable of moving laterally in the substantially planar gap between the opposed upper and lower plates 209, 210. Similarly, a second pair of stabilising plates 213, 302 is positioned towards each arm second end 205. A substantially planar gap is created between upper plate 302 and lower plate 213 such that each arm second end 205 is capable of pivoting movement within the region between upper and lower plates 213, 302.

Each arm 302 comprises an engaging portion positioned at a radially innermost part of each arm 202 towards each arm first end 301. Each engaging portion comprises a curved plate 207 having a length extending in the lengthwise direction of each arm 202 between first and second ends 301, 205. A corresponding width of each plate 207 is aligned substantially parallel with axis 211 such that a radially inward facing surface 208 of each plate 207 is orientated to be facing axis 121. In use, support assembly 112 is mounted within working part zone 111 adjacent to the lower region 119 at bushing 118 and immediately below eccentric weight 107 and main shaft 106. That is, each engaging plate 207 is positioned at the same axial height and position as lower bushing region 119. Accordingly, as actuator 203 is extended, plates 207 are displaced towards one another to clamp onto the radially outward facing surface of bushing region 119. The mechanical latch 214 may then be engaged to positionally lock each arm 202 and plate 207 into touching contact with bushing region 119. Accordingly, during maintenance and/or replacement of the various wear parts of crusher 100, including in particular crushing shells 101, 104, head 100 and main shaft 106 are raised vertically upward. As bushing 118 and eccentric weight 107 are not attached to main shaft 106, support assembly 112 is operative, via the pivoting motion of arms 202, to clamp, support and maintain the axial position of bushing 118 and weight 107 within zone 111 as the main shaft 106 is removed vertically upward.

Advantageously, assembly 112 via arms 202 is configured to maintain bushing 118 in a radially centred position within zone 111 relative to axis 121 so as to facilitate

reintroduction of main shaft 106. Once shaft 106 is reintroduced into bushing 118, latch 214 and cylinder 203 are disengaged to allow each arm 202 to move away from one another, in turn, allowing unhindered rotation of bushing 118, eccentric weight 107 and main shaft 106 within the chamber 110.

Figures 5 and 6 illustrate a further embodiment in which arms 202 are pivotally rotated towards and against bushing 118 via a different actuation mechanism. In particular, each arm 202 is coupled at end 205 to a common wedge slider 503 via a respective link bar 500. Each link bar 500 is coupled pivotally at a first end 501 to arm end 205 and a second end 502 to wedge 503. The wedge 503 comprises internal screw threads and is in turn mounted upon a threaded elongate shaft 504 and is capable of sliding movement along shaft 504 towards and away from bushing 118 via rotation of shaft 504. Shaft 507 accordingly comprises a first end 505 mounted upon an extension 507 projecting laterally and rearwardly from plate 302. A second end 506 of shaft 504 is positioned in close proximity to brace bar 303. In use, wedge 503 is configured to slide backwards and forwards along shaft 504 (via the screw threads) to force ends 501 of each linkage bar 500 laterally away from shaft 504. This in turn forces each arm second end 205 laterally outward relative to shaft 504 such that engaging portions 207 clamp onto and around bushing 118 at region 119 in a 'closed' state. In a reverse movement of wedge 503 along shaft 504 in a direction away from main shaft 106, arms 202 are returned to the 'open' state allowing free movement of bushing 118 and main shaft 106 within crusher 100.

In particular, the radially inward and outward movement of portions 207 relative to axis 121 is synchronised with the radial movement of wedge 503 relative to axis 121 along shaft 504. In particular, at the start of the extraction process of head 100 from chamber 110, shaft 160 is rotated slowly by the drive assembly 109 to position the eccentric part of weight 107 circumferentially in-line with wedge 503. Arms 202 are then actuated such that engaging portions 207 move towards one another as wedge 503 moves radially towards axis 121. Portions 207 contact lower region 119 of bushing 118 being configured to 'catch^'' region 119 at any position within chamber 111 as shaft 106 may be inclined at any angle. As the movement of portions 207 is mechanically synchronised with the radial linear movement of wedge 503, retaining ring 122 is contacted by an axially upper part of wedge 503. Accordingly, when the present centring apparatus is fully engaged around main shaft 106 (and bushing 118), unbalanced weight 107 is centred by portions 207 and supported vertically by the axially underlying wedge 503 via ring 122. Main shaft 106 may then be lifted vertically upward as with the previous embodiment with bushing 118 and weight 107 having been centred to facilitate reintroduction of main shaft 106.

Claims

1. A cone crusher (100) comprising:

a frame (102) that defines an internal crushing chamber (110);

a main shaft (106) extending through the internal chamber (110), the main shaft

(106) mounting a crushing head (100) at or towards a first upper end and a bushing (118) at or towards a second lower end;

a bushing support assembly (112) mounted within the crusher (100) at or below a region of the bushing (118);

the crusher (100) characterised in that the support assembly (112) comprises: a pair of arms (202) supported by a base (200, 201, 212), each arm having an engaging portion (207) to contact the bushing (118), the arms (202) capable of moving such that the engaging portions (207) of each respective arm (202) can move away and towards one another to trap and hold the bushing (118) at a fixed axial position within the crusher (100) independently of support of the bushing (118) by the main shaft (106).

2. The apparatus as claimed in claim 1 further comprising a linear actuator (203) connecting the arms (202) and operative by linear extension to respectively force together the pair of engaging portions (207) by movement of the arms (202).

3. The apparatus as claimed in claims 1 or 2 further comprising a bias member (204) connected to and acting on the arms (202) to force the engaging portions (207) of each respective arm (202) apart relative to one another.

4. The apparatus as claimed in any preceding claim further comprising a first arm- stabilising component positioned towards a first end (301) of the arms (202) closest to the engaging portions (207) relative to a second end (205), the stabilising component having a first part that is positioned under the arms (202) and a second part positioned above the arms (202) so that the arms (202) are capable of moving laterally between the first and second part.

5. The apparatus as claimed in claim 4 wherein the first part comprises a first substantially planar plate (209) and the second part comprises a second substantially planar plate (210), the first (209) and second (210) plates being aligned substantially parallel.

6. The apparatus as claimed in any preceding claim further comprising a second arm-stabilising component positioned towards a second end (205) of the arms (202) furthest from the engaging portions (207) relative to a first end (301), the stabilising component having a first part that is positioned under the arms (202) and a second part positioned above the arms (202) so that the arms (202) are capable of moving laterally between the first and second part.

7. The apparatus as claimed in claim 4 wherein the first part comprises a first substantially planar plate (213) and the second part comprises a second substantially planar plate (302), the first (213) and second (302) plates being aligned substantially parallel.

8. The apparatus as claimed in any preceding claim further comprising a lock assembly (214) mounted adjacent to at least one of the arms (202) and configured to be actuated to engage and lock at least one of the arms (202) in fixed position at the base (200, 201, 212).

9. The apparatus as claimed in any preceding claim wherein the engaging portions (207) comprise a plate-like body having a part extending perpendicular to a plane in which the arms (202) move relative to one another such that the part of each engaging portion (207) is orientated to be aligned substantially parallel with an axis (121) of the main shaft (106).

10. The apparatus as claimed in any preceding claim wherein the base (200, 201, 212) comprises a frame (201) supported by a plurality of legs (200).

11. The apparatus as claimed in any preceding claim wherein the arms (202) are pivotally mounted at the base (200, 201, 212) via at least one pivot mounting (211).

12. The apparatus as claimed in claim 2 wherein the linear actuator (203) comprises a one-way active hydraulic cylinder configured for extension when actuated.

13. The apparatus as claimed in claim 3 and 12 wherein the linear actuator (203) and the bias member (204) are located towards a second end (205) of the arms (202).

14. The crusher as claimed in any preceding claim further comprising an inner frame (103) mounted within the internal chamber (110), the support assembly (112) positioned internally within the inner frame (103).

15. The crusher as claimed in claim 14 wherein the support assembly (112) is positioned below the bushing (118) relative to a longitudinal axis (121) extending through the crusher (100) within the inner frame (103).