Crushing machinery is used to reduce by crushing, frangible and friable materials such as quarry products, mineral ore and other materials. The process is known as comminution to those skilled in the art. Comminution by crushing is a process in which high forces are employed to fracture the frangible or friable material which is often both hard and strong. In all crushers except impact crushers, the material to be crushed is fed between strongly mounted rigid metal surfaces and these surfaces are then forced closer together, breaking the material. The rigid metal surfaces then separate, allowing the crushed material to escape, and to be replaced by fresh oversize material and the process is repeated.

To protect the mechanical and structural parts of crushers from damage caused by the hard and abrasive nature of the product material, most crushers have hard, abrasion resistant liners. These are placed to line the mechanical and structural parts so that the latter are not in direct contact with the product.

In jaw crushers, such items are called fixed jaw and swing jaw liners. Gyratory crushers are fitted with a head (mante) and bowl (concave) liners.

The liners are made from a number of wear resistant materials, including elastomers and ceramics. However, for most crushers, they are made of metal.

Common materials include 12-14% manganese steel, also known as Hadfield steel. Hardened high alloy steel and white irons known as Super-chrome and Ni-hard are also common. Special hard facings, commonly high carbon and chrome alloys, are sometimes used to extend liner life. In each case the actual material selected for liners is chosen to best suit operational performance at acceptable cost.

When liners wear out, they are discarded and new liners are fitted. To permit liner replacement, the crusher and its associated feed and discharge systems must be shut down and therefore liner change is always attended by

loss of production. Thus it is vital that the worn liners are removed quickly and replaced easily with new liners using available on site labour.

The materials from which liners are made are hard and abrasion resistant and some of them become harder, by work hardening, when gouged or distorted by the material which the crusher is reducing. These characteristics make it difficult and expensive to machine them with metal cutting equipment and there is a limited accuracy which metal working processes can achieve.

On the other hand the liners are not, first and foremost, structural members and the crushing forces must be transferred to them from the mechanical and structural crusher parts which the liners protect. To transfer these crushing forces which are, by their nature, distributed widely over the liner surfaces, intimate contact is needed between the back of the liners and the adjacent mechanical and/or structural components of the crusher. It follows that an ideal liner will have a back surface exactly matching the shape of the crusher parts it protects. The liners however resist such accurate machining. Any machining, regardless of accuracy, is very time consuming and expensive.

Traditionally, this incompatibility is resolved in gyratory crushers by fitting liners, with little or no machining, to the mechanical and structural parts of the crusher which they protect, leaving an annular gap between each liner and the structural part of the crusher. After assembly, the gap is filled completely by pouring in a low melting point metal such as lead, zinc or a babbit metal or a resinous glue such as epoxy. Thus, each liner is made integral with its structural part. This traditional method achieves full support of the liner and full contact with the crusher parts, and it works very well. The disadvantage is that subsequent removal of a liner from its structural part is very difficult and the pouring process requires acquired skills not always available on site. The replacement of liners using this method takes days rather than hours and adds greatly to the time the crusher is out of service.

The invention seeks to provide an improved method and arrangement for providing a replaceable wear liner for the head of a gyratory crusher.

The invention is particularly well suited for use in relation to a replaceable wear liner for the head of gyratory crushers of the type disclosed in Australian

patent 618545 (AU-B-19935/88), and largely is described in this context.

However, it is to be understood that the invention also can be used for other types of gyratory crushers.

Replacement of crusher liners is required: (a) when the liners are worn to the point where they may fail and thereby expose the underlying crusher parts to damage from the material being crushed; and (b) when the liners still retain structural integrity and strength but have worn so that the surfaces in contact with the product have lost geometry critical to the control of the grade size, which the operator requires.

The present invention facilitates replacement of liners of gyratory crushers at such times in a manner substantially reducing overall capital costs and the costs of down-time and labour required for replacement.

According to the invention, there is provided a fixing and locating means (herein referred to as securement means) suitable for securing a head liner on the head bearing housing of a gyratory crusher, wherein the securement means includes an inner substantially annular band for surrounding an external circumferential surface of the housing within the liner, the inner band has an inner circumferential surface for contacting the external surface of the housing and an outer circumferential surface which tapers frusto-conically ; the locating means further includes an outer substantially annular band which is adapted to concentrically surround the inner band, the outer band has an outer circumferential surface for contacting an internal surface of the liner and an inner circumferential surface which tapers frusto-conically ; the locating means defines a circumferential array of axially extending holes intermediate said inner and outer surfaces whereby, with the locating means positioned around the housing between the external surface of the housing and the internal surface of the liner, fasteners such as bolts are able to be inserted into the locating means to enable application of axial forces to the locating means; and wherein the outer and inner frusto-conical surfaces of said bands are adapted to interact whereby the axial forces generate radially acting force components which force the inner band to contract radially and which force the outer band to expand

radially to enable the securement means thereby to secure the liner in relation to the housing.

In a first embodiment of the securement means, the outer circumferential surface of the inner band tapers frusto-conically from each axial end thereof to a maximum external diameter intermediate those ends, while the inner circumferential surface of the outer band tapers frusto-conically from each axial end thereof to a minimum internal diameter intermediate those ends. The arrangement of the bands in the first embodiment is such that a clearance between the bands decreases wedge-like in radial width over a respective portion from each axial end to a minimum width intermediate those ends. The securement means of the first embodiment further includes first and second tensioning, axially spaced rings each received between the bands at a respective end thereof and each having a cross-section complementary to the surfaces of the bands defining a respective portion of the clearance. The axially extending holes in the securement means, in the first embodiment, extend through one and at least into the other of the rings, with each hole in the first ring axially aligned with a respective hole in the second ring.

In a first form of the first embodiment, the holes in the first ring are clearance holes, while the holes in the second ring are threaded. Each fastener extends through a respective clearance hole of the first ring, into threaded engagement in the aligned threaded hole of the second ring. Thus, by sufficient tightening of the fasteners down onto the first ring, the rings are able to be drawn relatively axially towards each other, to generate the radially acting force components.

In a second form of the first embodiment, the holes in each of the rings are clearance holes. In this form, the securement means is supported between the housing and the liner, on abutment means defined by, and projecting inwardly from the internal surface of, the liner. Each fastener extends through aligned holes of the rings, and beyond the abutment means, into threaded engagement with an aligned threaded hole in a shoulder defined by, and projecting outwardly from the external surface of, the housing. Thus, by sufficient tightening of the fasteners down onto the first ring, and generation of a

reaction force by the abutment means, the rings are able to be forced relatively axially towards each other, to generate the radially acting force components.

A third form of the first embodiment utilises a combination of the first and second forms. That is, the array of holes includes holes in accordance with each of those forms, such as in successive sets, and two different sets of fasteners are used. In the third form, the fasteners in accordance with the second form preferably are tightened first. This serves to force the liner firmly down into engagement with the housing, such as by abutment of a lower skirt portion of the liner with the housing, while it also serves to position the securement means at a required height, between the housing and the liner, defined by the abutment means.

In each form of the first embodiment, the first ring is upper-most in the in-use orientation of the securement means. Typically, the securement means is located adjacent to the upper extent of the liner and housing, and the fasteners are tightened onto the first ring from above.

In each form of the invention, a cap may be provided over the upper end of the housing. Particularly with the second and third forms the cap may be secured by further fasteners, such as bolts, each of which extends down through a respective clearance hole in the cap, through further aligned clearance holes in the rings to engage in a respective threaded hole in the shoulder defined by the housing. Tightening of the fasteners for securing the cap preferably causes a lower peripheral edge of the cap to bear forcefully onto the first ring to thereby further increase axial forces and act to force the first ring axially towards the second ring.

The first ring may be provided with still further holes which are threaded, but which are not aligned with holes in the second ring. These threaded holes in the first ring enable the insertion of bolts which are able to be tightened against the second ring, after removal of all fasteners, to generate sufficient axial forces acting to separate the rings and enable removal of the securement means, such as for replacement of a worn liner or a worn part of a multi-piece liner.

In the first embodiment, each substantially annular band preferably is circumferentially continuous. However, one or each of them may be penannular. One or each of them even made up of successive discrete segments of a substantially complete annulus. However, to ensure substantial uniformity of force transfer from the rings to the bands, the rings preferably are circumferentially continuous or, if not continuous, at least of penannular form.

In a second embodiment of the securement means, the frusto-conical outer surface of the inner band has substantially the same taper angle as the frusto-conical inner surface of the outer band, and the bands abut at those frusto-conical surfaces. Relative to an in-use orientation for the securement means, one of the bands at an axial end of the bands has an upper, end surface of the securement means below which the frusto-conical surfaces extend towards the other end of the securement means. Where the upper end surface is defined by the outer band, the frusto-conical surface of each band has a minimum diameter at or adjacent to that axial end, increasing to a maximum diameter at or adjacent to the other axial end. However, the converse of this variation in diameters applies if it is the inner band which defines the upper end surface below which the frusto-conical surfaces extend. That is, in the converse case, the frusto-conical surfaces of each band has a maximum diameter at that axial end and a minimum diameter at the other axial end where the first band defines the upper end. In each case, each hole of the circumferential array of axially extending holes extends from upper end face, through the abutting frusto-conical surfaces and towards, preferably to, the other axial end. For ease of further description, the band defining the upper end surface is referred to as the clamping band, with the other band referred to as the clampable band, as is the case relative to the in-use orientation.

In a first form of the second embodiment, the axial holes in the clamping band are clearance holes for fasteners, while the holes in the clampable band are threaded. Each fastener extends through a respective clearance hole into threaded engagement with a threaded hole in the clampable band. Thus, by sufficient tightening of the fasteners down onto the upper end surface of the clamping band, the bands are able to be drawn relatively axially to urge the

respective frusto-conical surfaces into tight engagement, to generate the radially acting force components.

In a second form of the second embodiment, the axial holes are clearance holes in each of the bands. In this form, the securement means is supported between the housing and the liner, on abutment means defined by, and projecting inwardly from the internal surface of, the liner. Each fastener extends through the holes, and beyond the abutment means, into threaded engagement with an aligned threaded hole in a shoulder defined by, and projecting outwardly from the external surface of, the housing. Thus, by sufficient tightening of the fasteners down towards the upper end surface of the clamping band, the clamping band is able to be forced towards the abutment and to clamp the clampable band on the abutment whereby the bands are able to be drawn relatively axially to urge the respective frusto-conical surfaces into tight engagement, to generate the radially acting force components.

In the second form of the second embodiment, the fasteners may be tightened down onto the upper end surface of the clamping band. Alternatively, where a cap is provided over the upper end of the housing, the cap may be secured by each fastener extending down through a respective clearance hole in the cap, through holes of the bands, and into threaded engagement with the holes in the shoulder defined by the housing. In that alternative, tightening of the fasteners down on the cap forces a lower peripheral edge of the cap down on the clamping band, to transfer to the clamping band and to the clampable band axial forces generated by the fasteners. However, there may be respective sets of holes in the securement means and the shoulder, and respective sets of fasteners, enabling each of those alternatives to be used simultaneously.

The clamping band may be provided with further holes which are threaded but which are not aligned with holes in the clampable band. These threaded holes in the clamping band enable insertion of bolts which are able to be tightened against the clampable band, after removal of the fasteners, to generate sufficient axial forces acting to separate the bands and enable removal

of the securement means, such as for replacement of a worn liner or a worn part of a multi-piece liner.

In the second embodiment, each band preferably is circumferentially continuous or penannular. However, one or each of the bands may be made up of successive discrete segments of a substantially complete annulus.

In either embodiment in which an abutment means is defined by the liner, to enable the securement means to be supported thereon, the abutment means may be in the form of an annular rib or ledge which is circumferentially continuous. In such case, the rib or ledge may define a circumferential array of holes, on the same pitch circle as holes in the securement means, to enable fasteners to extend therethrough into threaded engagement with the shoulder defined by the housing. However, the rib or ledge may be circumferentially discontinuous, or notched at intervals therearound, to enable fasteners to extend to that shoulder. Similarly, the shoulder may be circumferentially continuous or discontinuous. However, as will be appreciated, a respective section of a discontinuous shoulder would need to be located in line with each opening, notch or the like of the abutment means through which a fastener is to extend.

The invention also provides a gyratory crusher for crushing frangible or friable material, the crusher including a bowl which defines a chamber for receiving frangible or friable material to be crushed and a discharge opening at the base thereof through which crushed material is able to discharge, a crushing head mounted in said bowl at an offset position with respect to a central axis of said bowl, and a drive assembly for driving said crushing head within said bowl for imparting gyratory motion to said head about a gyratory axis incline with respect to and intersecting said central axis, whereby frangible or friable material received into said chamber is subjected to crushing between an inner peripheral surface of said bowl and an outer peripheral surface of said head by the gyratory motion of said head; wherein said head includes a bearing housing on which a head liner is co-axially mounted, the head liner is releasably retained co-axially on the housing by there being provided therebetween a fixing and locating means according to the invention.

In the crusher according to the invention, the fixing and locating means preferably is provided between the housing and an upper part of a two part head liner. The upper part of such liner may be forced by the fixing and locating means so that a lower circumferential surface of the upper part bears against an opposed upper circumferential surface of the lower part. In the latter case, the lower part of the liner may be supported by the housing such that forces transferred to the lower part from the upper part are able to be transferred from the lower part to the housing.

The liner preferably has a protrusion, such as a circumferential rib, on which the fixing and locating means is located. In such case, the second tensioning means preferably engages the housing at a location below the protrusion.

In order that the invention may more readily be understood, description now is directed to the accompanying drawings, in which: Figure 1 is a partially sectional view of a gyratory crusher according to the invention having a first embodiment of fixing and locating means according to the invention; Figure 2 is a view on an enlarged scale of the crushing head and bowl of the crusher of Figure 1 and of the fixing and locating means of the first embodiment ; Figure 3 is a partial perspective view, showing ef one half of the fixing and locating means of the crusher of Figure 1; Figure 4a is a schematic representation of a bolting arrangement for an upper component of the means of Figure 3; Figure 4b is a sectional view of the upper component of the means of Figure 3, taken relative to line IVb-lVb of Figure 4a; Figure 4c is a schematic representation of the bolting arrangement for a lower component of the means of Figure 3; Figure 4d is a sectional view of the lower component of the means of Figure 3 taken relative to line IVd-lVd of Figure 4c;

Figures 5 to 7 show on an enlarged scale detail of the arrangement shown in Figure 2, related to the schematic representation of Figure 4, in successive stages in securement of the fixing and locating means of the first embodiment; Figure 8 is similar to Figures 5 to 7 but illustrates release of the fixing and locating means of the first embodiment; Figure 9a similar to Figures 5 to 7, but illustrates an optional stage in securement of the fixing and locating means of the first embodiment; Figure 9b shows part of a component used in the optional stage to which Figure 9a relates ; Figure 10 is similar to Figure 3, but illustrates a fixing and securement means according to a second embodiment of the invention; Figure 11 a is similar to Figure 4a but shows the bolting arrangement for an outer component of the means shown in Figure 10; Figure 11b is a sectional view of the outer component of the means of Figure 10, taken relative to line Xlb-Xlb of Figure 11a, Figure 11 c shows the bolting arrangement for an inner component of the meant of Figure 10; Figure 11d is a sectional view of the outer component of the means of Figure 10, taken relative to the line Xld-Xld of Figure 11 c ; Figures 12 and 13 correspond to Figures 5 and 7, but illustrate successive stages in the securement of the means of Figure 10; Figures 14 and 15a correspond to Figure 8, but show alternative arrangements for release of the means of Figure 10; Figure 15b is a plan view of part of a component used in the release arrangement of Figure 15a ; Figure 16a corresponds to Figure 9, but illustrates an optional stage in securement of the means of Figure 10; Figure 16b shows part of a component used in the optional stage to which Figure 16a relates ; and Figure 17 illustrates use of the means of Figure 10, after its release, in removing or replacing a head liner part.

In the arrangement of Figure 1, there is shown a gyratory crusher 10 which has an anti-rotation system 12. Much of the construction and operation of the crusher 10 readily will be understood.

The crusher 10 has a bowl 14 and a head 16. The bowl 14 is mounted on a fixed, bowl support frame 18. The bowl 14 is of circular transverse cross- section, and converges frusto-conically from its open upper end to a constriction at 20, and thereafter diverges frusto-conically to its open lower end. The head 16 also is circular in transverse section and comprises an inner bearing housing 22 on which a head liner 24 is secured, and a head cap 26. The liner 24 diverges slightly from its upper end to a region below the constriction 20, and thereafter flares downwardly and outwardly to provide a skirt portion.

The crusher 10 includes an eccentric shaft 28 on which head 16 is rotatably mounted. The shaft 28 has a lower portion 28a which has an axis of rotation substantially co-incident with the axis of bowl 14, and which is rotatable in upper and lower bearing assemblies 30 and 30a. Each of the assemblies 30 and 30a is located in lower support frame 18a which can form part of the frame 18. The shaft 28 also has an upper portion 28b which has an axis which is incline with respect to the axis of the shaft portion 28a, with the respective axes of the shaft portions 28a and 28b intersecting at a fixed point P which is on or closely adjacent to a basal plane of the head 16. That is, point P is so located relative to a plane containing the lower peripheral extremity of the liner 24. Mounting of the head 16 on shaft 28 is by means of an upper bearing assembly 32 and a lower bearing assembly 32a, with each of the assemblies being concentric with and provided between the upper shaft portion 28b and the housing 22 of the head 16.

Below the head cap 26, the interior of the head 16 is protected by a top seal plate 36. At the base of head 16, the interior of the head 16 and of sub- frame 18a is protected by a resilient annular seal provided by anti-rotation system 12.

The shaft 28 is driven by drive assembly 40, so as to rotate on the axis of its lower shaft portion 28a, utilising a drive motor (not shown). The assembly 40 has a drive shaft 42 mounted in support frame 18a by inner and outer bearing

assemblies 44 and 44a. A pinion 46 is mounted on the inner end of the shaft 42, and meshes with a crown wheel 48 secured around portion 28a of the shaft 28. A pulley 50 on the outer end of the drive shaft 42 enables the shaft 42 to be rotated by operation of the motor, via drive belts (not shown), for rotation of the shaft 28.

In operation of the crusher 10, the drive assembly 40 rotates the shaft 28 on the axis of its lower portion 28a. As the axis of the upper shaft portion 28b is incline to the axis of lower shaft portion 28a, and as head 16 is co-axially mounted on portion 28b, rotation of the shaft 28 on the axis of its lower portion 23a causes head 16 to gyrate about the fixed point P. Moreover, as the lower end of head 16 is located proximate to, or coincident with point P, the gyratory motion of head 16 is such that movement of its upper end is predominantly transverse to the axis of bowl 14 and such that movement of the lower end of head 16 is substantially parallel to the axis of bowl 14.

Material to be crushed is fed into the upper end of bowl 14 to a crushing chamber 60 defined within the bowl 14 around the head 16. The movement of the head 16, during rotation of the shaft 28, provides a crushing action in which, where the gap between the crushing surface 62 of bowi 14 and head 16 is a minimum at the upper end of the chamber 60, as shown for a representation of a particle of material to be crushed at location"X", the gap is: -a maximum at the diametrically opposed side of the upper end of chamber 60, -a maximum at the lower end of chamber 60 at the same side, i. e. directly below location X, and -a minimum at the lower end of chamber 60 at the diametrically opposed side, i. e. at the location"Y".

Furthermore, as shaft 28 rotates, the gyratory motion of head 16 causes the location of the upper maximum and minimum gap openings, and of the lower minimum and maximum gap openings to be in successive diametrical planes of bowl 14. Thus, after rotation of shaft 28 through 180° from the position shown in Figure 1, there will be a maximum gap at each of locations X and Y.

As seen most clearly in Figure 2, the liner 24 of head 16 is in two parts.

The liner 24 has an upper frusto-conical part 70 which tapers inwardly to the top, and its inner surface is spaced from housing 22 to define an annular gap 71 therebetween. The liner 24 also has a lower frusto-conical part 72 which flares downwardly and outwardly from an abutment 21 therebetween just below constriction 20. As shown, part 72 has an inner surface spaced from housing 22 to define an annular gap 73 therebetween, although part 72 also has a depending annular rib 72a which projects from its inner surface and by which it is fully supported on an opposed surface of housing 22. Crusher 10 also includes liner fixing and locating means 74 (hereinafter referred to as securement means 74) which fixes parts 70 and 72 relative to each other, on housing 22, in a manner enabling the transference between parts 70 and 72 of axial compressive and bending loads which result from crushing friable and frangible materials fed to chamber 60. As shown, securement means 74 is located around the upper end of housing 22 of head 16, in annular gap 71 between that housing and liner part 70. Means 74 is engaged with each of housing 22 and liner part 70, and is operable to draw liner part 70 axially downwardly on housing 22 and to force the lower end of part 70 into engagement with the upper end of liner part 72 at the abutment 21 between parts 70 and 72.

One half of the securement means 74 is shown on an enlarged scale in the sectioned perspective view of Figure 3. Overall, means 74 has the form of a right circular annulus, and is made up of four parts. These parts comprise an inner band 76 having a right cylindrical inner surface 76a, an outer band 78 having a right cylindrical outer surface 78a and, between bands 76 and 78, an upper ring 77 and a lower ring 79. The bands 76 and 78 are concentrically arranged to define an annular gap 80 therebetween. The opposed surfaces 76b and 78b, respectively of parts 76 and 78 which define gap 80 are parallel over a short mid-section but, above and below the mid-section, the opposed surfaces uniformly diverge from each other in a manner which, viewed in radial cross- sections, gives upper and lower parts of gap 80 a frusto-conical form.

Each of rings 77 and 79 has tapered side surfaces so as to be complementary to, and to closely match, the respective frusto-conical upper and lower diverging parts of the surfaces 76b and 78a of bands 76 and 78.

However rings 77 and 79 are axially spaced at the mid-section of gap 80 defined by the parallel sections of surfaces 76b and 78b. Thus each ring 77,79 has radial cross-sections of bilaterally symmetrical trapezoidal form.

Rings 77 and 79 are located between bands 76 and 78 as shown in Figure 3. It will be appreciated that applying an axial force, acting to draw rings 77,79 together, will cause band 76 to contract in internal diameter and band 78 to expand in external diameter. In the arrangement of Figures 1 and 2, the securement means 74 is positioned as a neat fit in a cavity defined by substantially cylindrical, opposed surfaces 22a, 70a of housing 22 and upper part 70 of head liner 24, respectively. Thus surface 76a of means 74 is adjacent to surface 22a, while surface 78a is adjacent to surface 70a. The arrangement is such that a decrease in the diameter of band 76 and an increase in the diameter of band 78 will bring means 74 into tight and supportive, locking contact with the housing 22 and liner part 70 of head 16, enabling part 70 to be secured in relation to housing 22.

If the contacting surface pairs 22a, 76a and 70a, 78a are formed to very close tolerances, then the supportive, locking contact is achieved by elastic deformation of bands 76 and 78 (assuming bands 76 and 78 are circumferentially continuous). If the tolerances are not so close, then it is advantageous for one or each of the bands 76 and 78 to be discontinuous at a point, such as shown by a narrow gap indicated at 82 for band 78 76. For even wider tolerances, more than one such gap can be provided such that each of bands 76 and 78 is made up of segments of a respective annulus. If required, the rings 77 and 79 can also be made as ring segments.

Specific reference again is made to Figure 2, showing an upper part of crusher 10 of Figure 1 enlarged for greater clarity. In this Figure, a lump X of frangible and friable product is depicted schematically in the crushing chamber 60, at the top left of Figure 2. The lump X is shown as received for crushing between liner 24 of head 16 and the bowl 14. As lump X is crushed, it applies

force to head 16, near the top of part 70 of head liner 24, which tends to push part 70 diametrally to the right in the view of Figure 2. For effective crushing, this force must be resisted so that liner part 70 remains in the desired position relative to bowl 14 and head bearing housing 22.

Provided that securement means 74 is in tight and supportive contact with housing 22 and liner part 70, then part 70 can not move laterally at the level of means 74. However, in the arrangement shown, the force applied by lump X is not applied at that level, but at a higher level such that the force produces a rotating moment about means 74 which can result in undesirably high and destructive forces in the component bands and rings of means 74.

The parts 70 and 72 of head liner 24 are in close contact at opposed respective surfaces at the abutment 21. Liner part 72 is able to resist rotation movement of liner part 70, by the force applied by lump X being transferred to part 72 at a diagonal and diametrally opposite location Y at the contacting surfaces of lower parts 70 and 72, provided that the contact between those parts is adequate. In addition to providing supportive, locking contact between housing 22 and liner part 70, the securement means also is able to ensure sufficient or adequate contact between the opposed surfaces of parts 70 and 72, as detailed in the following.

As will be appreciated, forces so transferred to liner part 72 are able to be transferred to housing 22, via rib 72a. From housing 22, the forces are able to be transferred to and absorbed by support frame 18.

In a uniform circumferential array, the ring 77 of the securement means 74 has a series of holes extending therethrough parallel to the axis of means 74. Successive holes have distinct functions and they therefore are distinguished as repeating sets of holes 82a, 82b, 82c and 82d on a common pitch circle, as shown in Figure 3. While not shown in Figure 3, but evident from consideration of Figure 4, and from respective ones of Figures 5 to 9, ring 79 has a partially similar array of holes in repeating sets 84a, 84b and 84c on the same pitch circle, with each of these in line with the correspondingly designated holes 82a, 82b and 82c. However, ring 79 does not have holes corresponding to hole 82d in ring 77, and there is a resultant larger gap between successive

sets 84a, 84b and 84c. The holes 82d and 84b are threaded for threaded engagement by bolts, while the holes 82a, 82b and 82c of ring 77 and holes 84a and 84c of ring 79 are unthreaded clearance holes enabling the passage therethrough of such bolts.

The arrangement of the holes is shown schematically in Figure 4. The upper half of Figure 4 shows the arrangement for ring 77, while the lower half shows the arrangement for ring 79. While only one respective set of holes is provided with reference numerals, the sets repeat in the same order, as indicated by the different shadings for the holes.

Figure 5 shows an enlarged view of detail of Figure 2, showing the assembled liner 24, with its parts 70 and 72, on housing 22 and securement means 74 providing supportive locking engagement therebetween. The sectional view of Figure 5 shows means 74 supported on an upper surface 85 of a radially inwardly extending ledge 86 defined on liner part 70, above a radially outwardly extending shoulder 88 defined by a step in surface 22a of housing 22.

The sectional view of Figure 5 is through aligned unthreaded holes 82c and 84c of rings 77 and 79. Through those holes, there is inserted a bolt C which also passes through an unthreaded hole or notch 86c in ledge 86, to engage in a threaded hole 88c extending downwardly from shoulder 88. A similar bolt C is provided in each other pair of aligned holes 82c, 84c and the bolts C are tightened to force ring 77 down, between bands 76,78, into cavity 80 and, by a reaction force from ledge 86, to force bands 76 and 78 down on ring 79, to bring ring 79 further into cavity 80. This has two effects, the first of which is to cause bands 76 and 78 into gripping contact with respective surfaces 22a and 70a.

The second is to force upper liner part 70 downwards to produce a firm and unyielding force and constant contact between the opposed surfaces of upper and lower liner parts 70 and 72 at abutment 21.

Figure 6 shows a similar section to Figure 5, but through aligned holes 82b and 84b, respectively of rings 77 and 79. For each such pair of aligned holes 82b, 84b, a respective short bolt B is passed through the unthreaded hole 82b and is engaged in the threaded hole 84b. After bolts C are tightened as described with reference to Figure 5, the bolts B are tightened to draw together

the rings 77 and 79. Thus the bolts B cause bands 76 and 78 to fully engage with housing 22 and liner part 70 until a firm and unyielding connection is achieved by means 74 between housing 22 and liner part 70.

Figure 7 shows a similar section to Figure 5, but through a pair of aligned holes 82a and 84a. After bolts B have been fully tightened, head cap 26 is positioned and, for each such pair of holes, a longer bolt A is passed through an unthreaded clearance hole 26a in cap 26, the unthreaded holes 82a and 84a, and an unthreaded clearance hole or notch 86a in ledge 86, to engage in a threaded hole 88a extending downwardly from shoulder 88. When the bolts B are tightened, they retain cap 26 in position and further lock the connection between housing 22 and liner part 70, and the connection between liner parts 70 and 72.

When liner part 70 is to be removed from housing 22, bolts A are removed, and cap 26 is removed. Bolts B and C then can be removed in any convenient sequence. Bolts D then are engaged in threaded holes 82d, as shown in the section of Figure 8 taken through one such hole 82d. The bolts D are advanced so that the leading end of each bears forcefully against the upper surface of ring 79. Thus, bolts D force rings 77 and 79 apart, out of engagement with bands 76 and 78. Thus, the unyielding connection between housing 22 and liner part 70, and at least the residual of forceful contact between liner parts 70 and 72 is released, and the loosened or freed parts are able to be dismantled.

For some applications, it may be desirable to increase the intensity of the firm and unyielding force and constant contact between liner parts 70 and 72.

For this, securement means 74 is positioned in gap 71, preferably as a neat fit therein, and bolts B and C are placed and entered finger tight into the respective holes designated. In this condition, bolts B and C do not restrict vertical movement of liner part 70 relative to part 72. As shown in the sectional view of Figure 9, corresponding to that of Figure 7, and the accompanying partial plan view, a special assembly plate or jig 90 is provided. The jig 90 has unthreaded clearance holes 90a', 90b'and 90c'which correspond to the similarly designated holes. Each hole 90a'is to receive a special long bolt A'as shown

in Figure 9. With the jig 90 mounted on the top of liner part 70, over housing 22, each bolt A'is inserted down through a hole 90a'and then in a similar manner to bolts A as described above. The clearance holes 90b'and 90c'are not for the insertion of bolts. Rather they are to provide access permitting insertion of a bolt tightening tool through jig 90 for engagement with bolts B and C.

With bolts A'inserted and tightened, they force upper liner part 70 into close contact with lower liner part 72, thereby forcing liner part 72 down so that its rib 72a firmly bears onto the opposed surface of bearing housing 22. The full bolt force is unrestricted by friction between band 74 and housing 22 and between band 76 and liner 70. Thus, the contact force between liner parts 70 and 72 is able to be maximised. Once bolts A'are fully tightened, bolts C and then bolts B are fully tightened as described above, locking the assemblies together. The bolts A'then can be released and withdrawn, and jig plate 90 can be removed to allow assembly of cap 26 and its securement by bolts A as previously described.

Figures 10 to 17 show an alternative liner fixing and locating mean 174 (hereinafter referred to as securement means 174). This also is suitable for securing the head liner or liner parts, such as for a crusher 10 as shown in Figure 1. The securement means 174 is of a less complicated form than means 74 of Figures 1 to 9, but corresponding parts have the same reference numeral, as in Figures 1 to 9, plus 100. The overall arrangement of Figures 10 to 17 will, in large part, be understood from consideration of the description of Figures 1 to 9, and description of Figures 10 to 17 therefore largely is limited to features by which the alternative securement means 174 and its interaction differ from the arrangement of Figures 1 to 9.

As shown most clearly in Figure 10, securement means 174 has the form of a right circular annulus, but is made up of only two parts. These parts comprise an inner band 176 having right cylindrical inner surface 176a, and an outer band 178 having a right circular outer surface 178a. The bands 176 and 178 are concentrically arranged, but do not define a gap therebetween (as required in Figures 1 to 9 in which gap 80 is necessary to accommodate rings

77 and 79). Rather, bands 176 and 178 bear against each other at the outer surface 176b of band 176 and the inner surface 178b of band 178.

In the arrangement of Figures 10 to 17, as seen most clearly in Figure 10, the outer surface 176b of band 176 and the inner surface 178b of band 178 are frusto-conical, but with substantially the same taper angle. Thus surfaces 176b and 178b are of substantially complementary form. The arrangement is such that, by applying opposing axial forces acting to move the bands 176 and 178 axially together relative to each other, in a direction for reducing the spacing between the radially wider upper surface of band 176 and the radially wider lower surface of band 178, band 176 is able to be decreased in internal diameter and band 178 is able to be increased in external diameter. As a consequence, with locating means 174 within the gap 171 between liner part 170 of liner 124 and the head bearing housing 122, part 170, and hence part 172 of liner 124, is able to be secured in relation to housing 122.

As shown in Figure 10, one or both of bands 176 and 178 may be discontinuous at a point, such as shown by radial gap 182 through band 176.

Alternatively, one or both of bands 176 and 178 may be made up of segments of an annulus.

As represented by Figure 11 for each of bands 176 and 178, and shown in Figure 10 for band 178, each of bands 176 and 178 has a respective series of holes extending parallel to the axis of securement means 174. In band 178, there are five sets of holes 182a, 182b and 182c on a common pitch circle. The holes of each series are uniformly spaced circumferentially, while the spacing between centres for each hole 182a and the hole 182c of the preceding series is twice the spacing between centres for the holes of each series. While not shown in Figure 10, but evident from others of Figures 11 to 17, band 176 has five sets of holes 184a, 184b, 184c and 184d which are on the same pitch circle as the holes of band 176. Each of holes 182a, 182b and 182c is able to be positioned in line with a respective hole 184a, 184b and 184c of band 176, while each hole 184d is uniformly spaced from a hole 184c of one set and the hole 184a of the next set.

Figure 12 shows securement means 174 in its assembled condition in which it secures liner 124 in relation to head housing 122. In that condition, liner part 170 of liner 124 is forcefully drawn down on bearing housing 122 of the crusher head 116, and secured by a decrease in the diameter of band 176 and an increase in the diameter of band 178 whereby means 174 is in tight and supportive, locking contact with each of housing 122 and liner part 170. As a consequence, the lower end of part 170 is in forceful engagement with the upper end of liner part 172, at the abutment 121 therebetween. Hence, liner part 172 is held forcefully in engagement with housing 122 at a circumferential rib (not shown, but corresponding to rib 72a of the arrangement of Figures 1 to 9) which is provided on the inner surface of part 172 and bears against an opposed surface of housing 122.

Attainment of the assembled condition for securement means 174, to secure liner 124 in relation to head bearing housing 122, may be achieved solely by the arrangement shown in Figure 12. For this, means 174 is located concentrically between liner part 170 and housing 122. As shown, means 174 is within annular gap 171 and on surface 185 of radially inwardly extending abutment of ledge 186 of part 170, and it is secured and tightened by threaded fasteners or bolts E. With each hole 182a, 182b and 182c of each set of band 178 aligned respectively with a hole 184a, 184b and 184c of each set of band 176, a respective bolt E is inserted through each pair of aligned holes 182c and 184c. Those holes are unthreaded, and each bolt E also passes through a respective hole or notch 186c defined by ledge 186, and is in threaded engagement with a respective hole 188c of radially outwardly extending shoulder 188 defined by housing 122. When bolts E are tightened, they urge band 178 of securement means 174 downwardly towards shoulder 188, thereby causing band 176 of means 174 to bear forcefully down on surface 185 and forcing liner part 124 forcefully down on housing 122. Resultant axially opposing forces, from the force applied by bolts E on band 178 and the reaction force generated by ledge 186 on band 176, generates forceful engagement between the respective surfaces of 176b and 178b of bands 176 and 178 whereby band 176 is caused to resiliently decrease in diameter and band 178 to

resiliently increase in diameter, with limited axial movement between bands 176 and 178. As a consequence, inner surface 176a of band 176 is brought into forceful, gripping contact with surface 122a of housing 122 and the outer surface 178a of band 178 is brought into forceful gripping contact with surface 170a of liner part 170. Also, in being forced downwardly on housing 122 by bolts E, liner part 170 is brought into firm and unyielding contact with liner part 172 at abutment 121, and the latter is similarly brought into firm and unyielding contact at its lower extent with housing 122. Thus, liner 124 is securely and firmly retained in relation to bearing housing 122.

After securement means 176 is assembled, as described with reference to Figure 12, it is further secured as shown in Figure 13. As shown in Figure 13, the head cap 126 is placed in position, within liner part 170 and over the top of housing 122, so that its peripheral skirt rests on means 174. When in position, cap 126 has a respective unthreaded hole 126a aligned with each pair of aligned unthreaded holes 182a and 184a of liner parts 178 and 176. A respective bolt F is inserted through each hole 126a and the holes 182a, 184a aligned therewith, through an unthreaded hole or notch 186a through ledge 186 and into threaded engagement with a respective hole 188a of shoulder 188 of housing 122. The fasteners are tightened and, due to the lower periphery of cap 126 bearing on band 178 of securement 174, they further increase the axial forces acting between bands 176 and 178 and, hence, they increase the forceful contact between band 176 and housing 122 and between band 178 and liner part 170. With bolts E and then bolts F fully tightened, the assembled components are in a working condition for the crusher of which they form part.

From the foregoing description, it will be appreciated that there is a necessary difference between bands 176 and 178 of securement means 174 of Figures 10 to 17, and bands 76 and 78 of means 74 of Figures 1 to 9. In means 74, at least one of bands 76 and 78 (preferably both of them) bear against surface 85 of ledge 86, and there is no requirement for relative axial movement between bands 76 and 78. Rather, bands 76 and 78 are caused to decrease and increase in diameter, respectively, by rings 77 and 79 therebetween being axially drawn together. In contrast, in the arrangement of Figures 10 to 17,

band 176 bears against surface 185 of ledge 186, and it is necessary for band 178 to be able to move axially relative to band 176, towards surface 185 under forces generated by bolts E and F, in order to cause a decrease in the diameter of band 176 and an increase in the diameter of band 178. Thus, if bands 176 and 178 have substantially the same axial dimension, it is necessary that, despite their surfaces 176b and 178b having the same cone angle, the minimum and maximum diameters of surface 178b are slightly less than the corresponding diameters of surface 176b. Alternatively, surfaces 176b and 178b may have substantially the same minimum diameter but, with band 178 having a slightly lesser axial dimension than band 176. This latter situation is illustrated in Figures 10, in which it can be seen that the lower edge of band 178 is slightly above the lower surface of band 178 when surfaces 176b and 178b are abutting but bands 176 and 178 are not subjected to significant axial forces.

However the arrangement may be such that, means 176 is appropriately assembled for use, band 178 is barely arrested against further axial movement relative to band 176 by the lower edge of band 178 abutting against surface 185 of ledge 186.

When head liner 124 or one of its parts 170 or 172 is worn and must be replaced, bolts F are removed, cap 126 is lifted off and bolts E are removed.

The securement means 174 then needs to be released, and alternative arrangements for this are illustrated in Figures 14 and 15, respectively.

It will be appreciated that substantial axial forces are applied to bands 176 and 178, of securement means 174, by appropriate tightening of bolts E and F. As a consequence, bands 176 and 178 will be locked in engagement with each other at their surfaces 176b and 178b. Also, band 176 will be similarly locked at its surface 176a with housing 122, while band 178 will be similarly locked at its surface 178a with liner part 170. The arrangement of Figure 14 utilises a plate 92 which is dimensioned to rest on the top edge of liner 124. On a pitch circle the same as that for holes 182a, 182b and 182c of band 178 and holes 184a to 184d of band 176, plate 92 has a series of unthreaded clearance holes 93. For release of securement means 174, plate 92 is positioned so that each hole 93 is aligned with a respective threaded hole

182b of band 178. A respective shaft S which is threaded at each end is inserted through a sufficient number, or each, or holes 93 and threaded into the hole 182b below each of those holes 93. A nut 94 at the upper end of each shaft S then is advanced down the thread at that end of shaft S and tightened against plate 92. When nuts 94 have been sufficiently tightened, shaft S exerts a sufficient upward force on band 178 to overcome frictional forces that oppose separation of band 178 from liner part 170 and band 176. Shafts S are selected of a sufficient size, strength and number to ensure such separation. Once band 178 is free and removed from gap 171, band 176 also becomes free and can be removed to enable part 170 or parts 170 and 172 of liner 124 to be lifted off for replacement of at least one of those parts.

The alternative arrangement of Figure 15, for release of securement means 174, also uses plate 92. However, in this instance, each hole 93 of plate 92 is aligned with a respective pair of holes 182b and 184b of bands 178 and 176. The holes 182b are threaded, whereas holes 184b are unthreaded clearance holes. A respective bolt G is inserted through each, or a sufficient number, of holes 93 and threadedly engaged in a corresponding hole 182b, and tightened against plate 92. When bolts G have been sufficiently tightened, they exert a sufficient upward force on band 178 to overcome frictional forces that oppose separation of band 178 from liner part 170 and band 176. Bolts G are selected of a sufficient size, strength and number to ensure such separation.

Once band 178 is free, removal of band 176 and replacement of one or each of parts 170,172 again is enabled.

It will be noted that, in contrast to Figure 15, Figure 14 shows a modified form for band 176 in which holes 184b are not provided. However, the arrangement of Figure 15 is preferred since holes 184b enable threaded engagement over the full axial extent of holes 182b. Thus, in the arrangement of Figure 14, band 176 could be provided with holes 184b, if required, as in Figure 15. Also, in each case, the holes 184b could be blind rather than through holes and, in such case, blind holes 184b preferably would have an axial extent from surface 176b which is at least to the lower threaded extent of holes 182b.

In some circumstances, it can be desirable to maximise the force with which the lower peripheral end of part 170 of liner 124 bears against the upper end of part 172, at abutment 121 therebetween. An example where this is likely to be required is with a crusher required to crush very hard material of a maximum lump size able to enter the crushing chamber (such as represented by lump X shown in Figure 2). Such crushing will have a tendency to displace the upper end of liner 124 in a radial direction, and this tendency must be resisted by bands 176,178 of securement means 174 in unison with the contact between parts 170,172 at their abutment 121.

Figure 16 illustrates an arrangement enabling maximisation of the force with which part 170 bears against part 172 of liner 124. For this, bands 176, 178 are inserted into gap 171 and fasteners E are inserted as described in relation to Figure 12. However fasteners E are inserted only to achieve finger tightness so as not to exert any, or any significant, clamping force on bands 176 and 178 or, via bands 176 and 178, on housing 122 and liner part 170, respectively. Prior to positioning cap 126 and inserting bolts F, as described in relation to Figure 13, plate 92 is positioned on the top of liner part 170 with each of its holes 93 positioned over a respective pair of holes 182a and 184a of bands 178,176. A respective bolt H then is inserted through each or a sufficient number of holes 93, the corresponding pair of holes 182a and 184a, and the hole or notch 186a of ledge 186 and into threaded engagement with a respective hole 188a of shoulder 188 of housing 122. The bolts H then are tightened to draw plate 92 down, and urge part 170 of liner 124 into required tight and unyielding contact with liner part 172.

When bolts H have been fully tightened, a suitable tool (not shown) is inserted in turn through each hole 95 of plate 92. Each hole 95 is above a respective bolt E, and the tool is such as to enable bolts E to be fully tightened as described in relation to Figure 12. That is, bolts E are tightened to lock bands 176 and 178 together, and to lock band 176 with housing 122 and band 178 with liner part 170, with this being achieved while the forces generated by bolts H are maintained. Once bolts E have been fully tightened, bolts H and

plate 92 are removed, following which cap 126 is fitted and bolts F are inserted and fully tightened as described with reference to Figure 13.

As will be appreciated, the part 170 of crusher head liner 124 is heavy.

Also, part 170 has no convenient attachments by which it can be connected to mechanical lifting means for positioning part 170 over, or removing it from, head bearing housing 122. Where liner 124 is of integral construction, rather than in two parts 170 and 172, each of these factors are even more relevant. However, in relation to a liner 124 having parts 170 and 172, as illustrated in Figure 17, securement means 174 can be used to assist removing part 170 from housing 122 (while, if liner 124 is integral, in lifting it from housing 122).

In the arrangement of Figure 17, securement means 174 has been released from its securement position. With bands 176,178 in their assembled relationship, but rotated relative to each other to locate each hole 182a or 182c of band 178 in line with a respective threaded hole 184d of band 176, means 174 is lifted up to, or repositioned within, an upper extent of liner part 170 which is above housing 122. A respective fastener or bolt J then is passed through each clearance hole 182a or 182c of band 178, into threaded engagement with a hole 184d, and tightened. With tightening of bolts J, bands 176,178 are caused to move axially relative to each other by axial forces generated by bolts J, causing band 176 to contract radially and band 178 to expand radial. The force generated by bolts J is increased until radial expansion of band 178 brings it into tight, unyielding contact with liner part 170, providing a powerful frictional force therebetween. Suitable mechanical lifting equipment, attachable to or under the securement means 174 then is able to provide a convenient means for lifting a worn part 170 from housing 122 and, conversely, for positioning a new liner part 170 into position on liner 122.

As will be appreciated, axially forces are applied to rings 77 and 79 of securement means 74 of Figures 1 to 9, and to the bands 176 and 178 of means 174 of Figures 10 to 17. However, the frusto-conical surfaces of rings 77 and 79 bear against the frusto-conical surfaces of bands 76 and 78 of means 74, while it is the frusto-conical surfaces 176b and 178b by which bands 176 and 178 are in contact. As a consequence, the axial forces generate force

components both parallel to and normal to the contacting frusto-conical surfaces. It is the normal components which result in the radial contraction and expansion, respectively of bands 76 and 78 and of bands 176 and 178 and give rise to the tight, unyielding engagement achieved with the respective housing 22,122 and liner part 70,170.

The components of securement means 74 and 174 typically are made of a suitable high strength metal, such as a suitable steel. The radial contraction of their respective bands 76,176 and the radial expansion of their respective bands 78,178 is achieved, under the applied forces indicated, within the elastic limit of the metal such that, on release of the forces, the bands are able to resiliently recover to their original, unstressed form.

The ledge 86 in the arrangement of Figures 1 to 9, and ledge 186 of the arrangement of Figures 10 to 17, may be continuous and have holes formed therein where indicated. However, the ledge 86 (186) more preferably is discontinuous over at least a radially inner margin thereof, to provide notches or gaps between successive sections. Each arrangement enables bolts to pass therethrough for threaded engagement in the shoulder 88 (188) defined by the housing 22 (122). However the liner 24 (124) most conveniently is formed of a hard, wear-resistant material, usually by casting, and the notched arrangement is easier to produce by casting. Similarly, the shoulder 88 (188) may be continuous or discontinuous, as required. When discontinuous, the shoulder 88 (188) has a respective one, of circumferentially spaced sections, in line with each hole or notch of the ledge 86 (186) through which a fastener is to extend.

The present invention enables a reduction in the time required to replace a worn liner with a new liner and, as a consequence, it enables a reduction in the cost of making the replacement. This reduction in time reduces the period for which the crusher needs to be out of service, with a consequent improvement in crusher productivity and, hence, a reduction in crushing costs.

As shown by the illustrated embodiment, the invention facilitates crusher head liners being made in at least two sections. Thus, only a worn section rather than an entire liner need be replaced. However, the fixing and locating means of the invention also has utility in a crusher having a single piece or

integral liner, as can be appreciated by considering liner 24 (124) as being of this form rather than as having separate parts 70 (170) and 72 (172). With an integral liner 24 (124), means 74 (174) continues to provide benefit essentially the same as detailed above, except that the bolts A act directly in applying rib 72a (172a) against housing 22 (122) rather than as a consequence of applying part 70 (170) against part 72 (172).

Finally, it is to be understood that various alterations, modifications and/or additions may be introduced into the constructions and arrangements of parts previously described without departing from the spirit or ambit of the invention.