AN ADJUSTMENT ASSEMBLY FOR A JAW CRUSHER

Field of the Invention

The present invention relates to components of a jaw crusher, which is an apparatus used for breaking feed materials that are passed thereinto. In one form the invention relates to an adjustment assembly for a jaw crusher for adjusting the position of one of the jaws, and will primarily be described with reference to this context .

Background Art

Jaw crushers for breakage of materials are known in the art. Such apparatus includes two opposing supporting plates, or jaw stocks, which are generally angularly disposed relative to each other, and which can be moved relative to one another by the motion of at least one of the jaw stocks. In normal circumstances the jaw stocks are arranged so as to define a tapering channel region therebetween. Also, the opposing faces of each jaw stock are generally fitted with a removable wear plate made of a hard, wear resistant material which is clamped thereto, to prevent abrasive damage to the jaw stocks during use of the crusher.

In use, coarse feed materials such as rock, gravel, mineral ores and the like are passed under the influence of gravity into the channel formed between the wear plate/jaw stock pair and the motion of the or each jaw stock causes the feed materials to become crushed therebetween. The materials are thus attritioned to the point where they are smaller in size than the narrowest distance between the wear plate/jaw stock pair, and consequently these materials then fall out of the base of the tapering channel region.

The term 'closed side setting' is used to describe the distance of closest approach between the fixed jaw and the at least one moveable (or swing or reciprocating) jaw, at or near the bottom of the wear plates. By adjusting the closed side setting the size of the attritioned particles can be varied. Normally the closed side setting is adjusted by moving the position of the swing jaw relative to the fixed jaw. This is achieved by various types of mechanisms which usually involve a toggle plate, which is located between a closed side setting adjustment mechanism and the rear of the swing jaw. The toggle plate is moveable whilst still being held in tension between these components as the swing jaw moves during operation of the crusher. Jaw crushers are generally built with the toggle plate as the weakest part so that it can break without causing too much damage.

The adjustment mechanism is used to push the toggle plate against the back of the swing jaw to tighten the closed side setting. The known prior art closed side setting adjustment mechanisms can fail if they are not of sufficient strength to counter the resistance of the material being crushed, which is transmitted via the swing jaw and toggle plate during crushing. The effect of this can be that the closed side setting aperture may vary depending on the adjustment mechanism being used, which can in turn cause the maximum size of the crushed product to vary.

The known adjustment mechanisms can also be quite complicated to use and to access for manual adjustment, requiring great operator dexterity. In the case of a movable jaw stock, this back face access can be obstructed by the drive mechanism which moves during operation to cause the reciprocation of this jaw. It is also frequently the case that the jaw stock is positioned

immediately adjacent to major obstructions in the region of its back face, for example other pieces of equipment, walls, and so on. An example where restrictions in space can cause such obstruction to the back of the jaw stock include where a j aw crusher is positioned as part of a crawler crusher unit .

Frequent adjustment of the closed side setting involve stopping the jaw crusher and manually adjusting the various parts of the adjustment mechanism. This can be a complicated, awkward and difficult procedure for the reasons already mentioned, leading to significant down time of the crusher, which can be costly from an operational standpoint.

Summary of the Invention

In a first aspect, the present invention provides an adjustment assembly for a jaw crusher having a frame and a pair of jaws, the assembly arranged for location in the frame and comprising first and second members, the members having respective engagement surfaces that are in opposing relation and the members arranged to slide laterally relative to each other across the engagement surfaces, said relative lateral sliding movement arranged to provide adjustment to a spacing between the jaws in a longitudinal direction which is transverse to the lateral sliding movement of the members, and a first actuator associated with the first member and operative to impart sliding of that member relative to the second member, the first actuator having one end fixed from lateral movement relative to the frame .

In one embodiment the second member is fixed from lateral movement relative to the frame.

However in an alternate embodiment a second actuator is associated with the second member and operative to impart sliding of the second member relative to the first member, the second actuator having a first end fixed from lateral movement relative to the frame. In this embodiment the first actuator has a second end attached to the first member, and the second actuator has a second end attached to the second member.

In both embodiments the or each actuator may be arranged in use to be moved in opposite directions.

By associating separate actuators with separate members, the force which an actuator can apply to the sliding movement of that member can be maximised, so that the maximum force can thus be applied in a direction to tighten the jaw crusher closed side setting. Such positioning of the actuator can also avoid slippage which may occur in prior art situations where, for example, an actuator may span two members in an adjustment assembly.

Additionally, this arrangement also removes the potential problem of components associated with an actuator from becoming crossed with adjacent parts of the assembly, such as across members. Some components associated with an actuator may include hydraulic fittings, electrical lines and so on.

The actuators may be arranged in use to be moved in opposite directions to causes the members to be arranged with a fully extended length in the longitudinal direction, to tighten the closed side setting.

In one embodiment, the or each actuator can be arranged moveable in a plane which is generally parallel to the engagement surfaces to maximise the force applied.

In an alternative embodiment, the or each actuator can be arranged moveable in a plane which is generally orthogonal to the longitudinal direction.

In one embodiment, the actuators can be elongate and are arranged in use to be laterally spaced apart from one another and are aligned along parallel axes .

In one embodiment the or each actuator can be a hydraulic ram .

The frame and/or housing can also protect the members and actuators to some extent from damage by rocks or other materials being crushed in the jaw crusher. If the housing is arranged to provide side access to reach the member and actuator pairs, this can simplify the maintenance replacement of worn or broken components by reducing the complexity and awkwardness of the task and the need to disassemble the entire adjustment assembly. This may also lead to improvements in occupational safety, such as reducing the risks involved in lifting or moving heavy items of equipment .

The or each member may have a wedge-like configuration and is provided with one or more surfaces that constitute the engagement surface .

In one embodiment the or each member comprises a single flange of a generally triangular configuration. The actuator associated with a corresponding member is juxtaposed in a side-by-side relationship with the single flange constituting the corresponding member.

In an alternate embodiment the or each member may comprise a pair of parallel spaced apart flanges, each of the flanges being of generally triangular configuration. In such an embodiment the or each actuator associated with a

corresponding member is disposed between the pair of flanges forming that corresponding member. The or each member may further comprise a plate attached to the pair of flanges constituting that member wherein one side of the plate comprises the engagement surface.

In a second aspect, the present invention provides a jaw crusher including a pair of jaws, a toggle plate and the adjustment assembly as defined in the first aspect, the toggle plate located between the adjustment assembly and one of the j aws .

Brief Description of the Drawings

Notwithstanding any other forms which may fall within the scope of the present invention, preferred forms of the invention will now be described, by way of example only, with reference to the accompanying drawings in which:

Figure 1 shows a perspective view of an embodiment of an adjustment assembly for a jaw crusher, in accordance with the present invention, and a toggle plate connected thereto;

Figure 2 shows a perspective, exploded view of the embodiment of the adjustment assembly for a jaw crusher of Figure 1;

Figure 3 shows a perspective view of part of the embodiment of Figure 1. In particular this Figure shows a member in the form of a wedge having a respective actuator associated therewith in the form of a hydraulic ram;

Figure 4 shows a sectional, plan view of the embodiment of the adjustment assembly of Figure 1. In particular this Figure shows details of the members in the form of wedges and respective, associated actuators in the form of hydraulic rams, the latter moveable towards an extended position (in the direction of the Arrows T) so as to

maximise the longitudinal expansion of the adjustment assembly (in the direction of Arrow L) ;

Figure 5 shows a perspective view of an embodiment of an adjustment assembly for a jaw crusher, in accordance with the present invention. In particular this Figure shows the adjustment assembly and a toggle plate located at a moveable (or swing) jaw stock;

Figure 5A shows a view of a detail of the portion the embodiment of Figure 5 that is shown in the circle A of dotted outline;

Figure 6 shows a front, side perspective view of the adjustment assembly for a jaw crusher of Figure 5; Figure 7 shows a rear, side perspective view of the adjustment assembly for a jaw crusher of Figure 5 ; Figure 8 shows a sectional, plan view of the embodiment of the adjustment assembly of Figure 5. In particular this Figure shows details of the members in the form of wedges and respective, associated actuators in the form of hydraulic rams, the latter shown in the retracted position so as to minimise the longitudinal expansion of the adjustment assembly;

Figure 9 shows a sectional, plan view of the embodiment of the adjustment assembly of Figure 5. In particular this Figure shows details of the members in the form of wedges and respective, associated actuators in the form of hydraulic rams, the latter shown in the fully extended position (in the direction of the Arrows T) so as to maximise the longitudinal expansion of the adjustment assembly (in the direction of Arrow L) ; Figure 10 is a perspective view of the wedge coupled to a slide rail and a toggle block incorporated in the embodiment of the actuator depicted in Figures 5 - 9; Figure 11 is a perspective view of the wedge coupled to a slide rail for bearing against a strong back incorporated in the embodiment depicted in Figures 5 - 9;

Figure 12 is a perspective view of a member in the form of parallel plates coupled to a slide rail for a further embodiment of the adjustment assembly;

Figure 13 is a perspective view of a pair of members each in the form of a single plate with one of the members coupled via a slide rail to a toggle block, and the other member coupled to a slide rail for bearing against a strong back in a further embodiment of the adjustment assembly; Figure 14 is a perspective view of a member in the form of a wedge coupled directly to a toggle block for a further embodiment of the adjustment assembly,-

Figure 15 is a plan view of a pair of members in the form of wedges with corresponding actuators when in a fully retracted position for a further embodiment of the adjustment assembly; and,

Figure 16 is a plan view of the members and actuators shown in Figure 15 but with the actuators in a fully extended position.

Modes for Carrying out the Invention

Referring to Figures 1, 2, 3 and 4, one embodiment of an adjustment assembly 10 for adjusting the closed side setting of a jaw crusher is shown. The assembly 10 comprises first and second members 12, 14, each in the form of a wedge. The members 12, 14 comprise respective rectangular flat base plates or panels 16, 18 having respective spaced apart flanges 20, 22 depending orthogonally therefrom. Each of the flanges 20, 22 is of a generally triangular shape. More particularly each flange is in the shape of a right angle scalene triangle with a truncated apex. An actuator in the form of a hydraulic ram 24, 26 is shown substantially enclosed within each member 12, 14. By locating a hydraulic ram 24, 26 within a member 12, 14, or at least in a side by side juxtaposition with the flanges 20, 22 a full stroke

movement (between a fully extended position and fully retracted position) is possible along the length of the member 12 , 14.

The flat base plate 16 of the member 12 has an outer surface face 28 that is arranged to be in frictional engagement with, and in opposing relation to, an outer surface face 30 of the flat base plate 18 of the other member 14, in other words a "back to back" configuration. In this way the two surface faces 28, 30 of the members

12, 14 can slide laterally across one another during use, as will shortly be described. In other embodiments, this same sliding with frictional engagement can be achieved with other surface face shapes, for example, rounded or arch-shaped complementary faces.

Within the members 12, 14, and located on the side of the base plate 16, 18 which is the side opposite to the outer surface face 28, 30, is a generally rectangular flange 32, 34 which protrudes into the member 12, 14. The hydraulic ram 24, 26 is mounted at one end to this protruding flange 32, 34 by a pin 36, 38 which passes through a flange pair 40, 42, which form a saddle at one end of the ram piston 44, 46, and through a hole arranged in the protruding flange 32, 34. The distal end of the hydraulic ram comprises a sleeve 48, 50 into which the ram piston 44, 46 is received. That distal end is also mounted to an end plate 64, 66 via a pin 56, 58 which passes through a flange pair 60, 62, which form a saddle at the end of the ram sleeve 48, 50. The pins 56, 58 also pass through respective generally triangular flanges 52, 54 formed at the end plates 64, 66. The generally triangular flange 52, 54 is supported at the end plate 64, 66 by webs 70.

The hydraulic rams 24, 26 therefore bridge, and are pivotally fastened to, respective slidable members 12, 14 and respective end plates 64, 66, the latter of which are

fastened in use to a frame which surrounds the adjustment assembly 10. The frame itself can support, or be an integral part of, a housing 72 which is arranged around the adjustment assembly 10 to exclude dust and attritioned particles from jamming the hydraulic rams 24, 26 or sliding movement of the members 12, 14. In order to locate (or replace) a hydraulic ram 24, 26 and member 12, 14 during maintenance intervals, the end plate 64, 66 is simply unbolted from the frame of the adjustment assembly 10 (for example by undoing threaded hexagonal bolts 74 positioned at a side wall of the assembly) and the entire rams 24, 26 with corresponding members 12, 14 can then be slidingly removed from the assembly 10.

When in position, the expansion of the hydraulic rams 24, 26 within each member 12, 14 can cause the member 12, 14 to slide laterally across one another in opposite directions (in the direction of Arrow T, Figure 4) . In some embodiments, the outermost end faces 76, 78, of the flanges 20, 22, of the members 12, 14 can be seated on slide rails 80, 82 to facilitate a sliding movement. The rail 80 may bear against or be formed integrally with a back wall 84 (also known as a "strong back") of the frame. Similarly the rail 82 may bear against or be formed integrally with a wear plate 86. Due to the tapering shape of the members 12, 14, the relative sliding movement of each member toward the respective other (in the direction of Arrow T) will cause an expansion of the overall transverse dimension (i.e. the combined width) of the two members, which is mesaured transverse to the lateral sliding movement. Thus, as one of the members 12 bears against the back wall 84, the other member 14 is moved in the longitudinal direction (in the direction of the Arrow L) so as to bear against, and be operatively coupled to, a wear plate 86, a toggle block 88, a toggle plate seat 90 and ultimately the toggle plate 92 itself which, in turn, bears against a back wall of a jaw stock.

Lateral expansion or contraction of the hydraulic rams 24, 26 therefore controls the position of the jaw stock and thus the closed side setting.

The force to tighten the closed side setting is maximised in arrangements where the assembly 10 comprises an actuator that is associated with each respective member 12, 14. A further force maximum is achieved in the longitudinal direction in those arrangements where the actuators (in this case hydraulic rams 24, 26) are moveable in opposite directions, and spaced apart but aligned along parallel axes as shown in Figures 1 to 4 (and also, as will shortly be described, in Figures 5 to 11) .

As shown in Figures 1 to 4 , each hydraulic ram 24, 26 is moveable in a plane which is generally parallel to the flat outer surface faces 28, 30 of the members 12, 14, which also maximises the force applied to the toggle plate 92 in the longitudinal direction (Arrow L) . In the embodiment which will shortly be described in relation to Figures 5 to 11, each hydraulic ram 24B, 26B is moveable in a plane which is generally orthogonal to said longitudinal direction, while the hydraulic rams 24B, 26B remain aligned along parallel axes.

In further embodiments, there need only be an actuator associated with one of the members and operative to impart sliding of that member relative to the other member. By frictional interaction, the member that is without an actuator can simply slide in response to the sliding of the member that is fitted with an actuator.

In another embodiment, the actuator need not be a hydraulic piston but can be a ratchet wheel that interacts with a pawl to move the associated member in a sliding manner by manual movement between various fixed positions,

for example by being moved along a perforated slide rail. In that sense, the 'sliding' of the member can also mean a non-continuous, incremental sliding motion, unlike the continuous sliding offered by a piston or hydraulic ram. Other types of actuators are also within the scope of the invention, such as geared electric motors or even threaded rods .

Referring now to Figures 5 to 11, in order to avoid repetition and for ease of reference, components and features of equivalent parts of the invention of similar functionality to those identified in Figures 1 to 4 have, for different embodiments, now been designated with an additional "B", such as the hydraulic rams 24B, 26B.

In Figure 5 a portion of a jaw crusher 100 is shown having a fixed jaw stock 120 and a movable jaw stock 140. Each jaw stock 120, 140 is fitted with a respective wear component in the form of a wear plate 160, 180 made of a wear resistant material such as tungsten carbide or a hardened metal alloy or a hardened steel product, which mounted thereto in a clamped configuration. As shown in the drawings, the wear plates are arranged with a series of elongate, downwardly extending surface ribs 200 defining a working face 220 thereof.

The two jaw stocks 120, 140 and their respective wear plates 160, 180 are angularly disposed relative to each other so as to define a tapering channel region 280 located therebetween. The interior tapering region 280 is also defined by two side walls (or cheek plates 300) which retain material being crushed between the two jaws. Only one such cheek plate 300 is shown in Figure 5. Typically feed materials for breakage are gravity- fed into the interior tapering region 280 of the jaw crusher 100.

Typical feed materials can include rock, gravel, mineral ores, metalliferous slags, glass and the like. Having

regard to the moveable or swing jaw 140, the closed side setting is determined by the toggle plate 92B and adjustment assembly 1OB.

The assembly shown in Figures 5 to 11 is in all respects similar to that already shown in Figures 1 to 4, with two principal differences. Rather than being mounted to an end plate, as shown in particular in Figures 6 and 7 the distal end of the ram sleeve 48B, 5OB into which the ram piston 44B, 46B is received is mounted directly to the frame of the adjustment assembly by hexagonal screws (or bolts) 74B which are fitted to the strongback 84B, or by hexagonal screws (or bolts) 75B which are fitted to the toggle block 88B. Without an end plate the rams 24B, 26B can be inspected and maintained from the outside of the assembly 1OB via the open sides of the strongback 84B without needing to unscrew an end plate and thereby withdraw the entire ram. Open side access can simplify the maintenance replacement of worn or broken components by reducing the complexity and awkwardness of the task.

The hydraulic rams can also move across their full stroke when the sides are open in this way. Also, the various hydraulic connections 130 on the rams can be linked to associated hoses and pipe work (not shown) which can pass directly via those open sides.

The other main difference when compared with the assembly shown in Figures 1 to 4 is best seen in Figures 8 and 9. Each hydraulic ram 24B, 26B is moveable in a plane which is generally orthogonal to the longitudinal direction (Arrow L) , whilst the pistons remain aligned along parallel axes . In this arrangement the inventor has found that the rams do not rotate as the members are adjusted, which can be advantageous in preventing possible damage to associated hydraulic systems such as hoses and pipework, or electrical lines . The association of an actuator with an individual channel member can also maximise the force

which can be applied to the sliding movement of that member to tighten the jaw crusher closed side setting, and avoid slippage.

In both of the embodiments shown in Figures 1 - 4 and

Figures 5 - 11 the actuators (i.e. hydraulic rams 24, 26) have one end, namely that comprising the sleeve 48, 50, fixed from lateral movement relative to the frame . In Figures 1 - 4 this is by way of attachment of the sleeves 48, 50 via saddles 60, 62; pins 56, 58; lugs 52, 54; and, plates 64, 66 to the housing 72 that is fixed to the frame. In Figures 5 - 11 this is by virtue of the lugs 52B, 54B being mounted directly to the frame and toggle block respectively.

Figure 12 depicts a member 12C for an alternate embodiment of the actuator assembly. In particular, this figure depicts a member 12C comprising two parallel spaced apart generally rectangular flanges 2OC between which corresponding hydraulic ram 24C is disposed. In its simplest terms, the member 12C may be considered as a form of the member 12B shown in Figure 11 but with the rectangular flat base plate 16B removed. A brace B may be provided to couple the flanges 2OC together.

In all other respects, the member 12C is the same as the member 12B. The plates 20C have respective planar surfaces 21C that are inclined relative to the rail 8OC and together form an outer surface face 28C that is arranged to be in frictional engagement with, and in opposing relationship to, a second member coupled with a toggle plate. The second member may be in a form: identical to the second member 14 depicted in Figures 1 - 4; or, identical to the second member 14B depicted in Figures 5 - 11; or, identical to that of the first member 12C shown in Figure 12; or, identical to the second member

14D described later in this specification and depicted in Figure 14.

Figure 13 depicts members 12D and 14D of yet a further embodiment of the adjustment assembly. In this embodiment, each of the members 12D and 14D comprise a respective single flange 2OD, 22D of a generally triangular shape and having respective planar outer surfaces 21D, 23D which are inclined relative to their corresponding rails 8OD, 82D on which they are seated.

The members 12D and 14D are seated on their corresponding rails 80D and 82D respectively at locations so that their respective surfaces 21D, 23D face each other and can slide against each other. The ram 24D is connected to the rail 8OD at one end by a flange 52D and attached at an opposite end to the plate 12D via a generally rectangular flange 32D that protrudes from and is fixed to the flange 12D. A hydraulic ram (not shown) is coupled between the flange 14D and the rail 82 in the same manner as described above in relation to the ram 24D.

Figure 14 depicts a member 14E for yet a further embodiment of the actuator assembly. In this embodiment, the member 14E is fixed directly to the toggle block 88E and is thus stationary relative to the toggle block 88E. In this embodiment, there is no need for a rail because the member 14E does not laterally slide. The member 14E may be in the form of a channel or wedge as depicted by: item 14 in Figures 1 - 4; or, item 14B in Figures 5 - 11 and thus be provided with a rectangular flat base plate or panel similar to that depicted as item 18 in Figure 2. Alternately, the member 14E may be in the form of two parallel spaced apart generally rectangular flanges 2OC as depicted in Figure 12. In such an embodiment, as the member 14E does not move laterally relative to the toggle block 88, there is no associated ram disposed within or adjacent the member 14E in which case, if desired, the

member 14E may be formed as a cast solid block of material .

In the embodiment shown in Figure 14 , and the force required to drive the toggle block 88E in the longitudinal direction (arrow L) is provided by a ram associated with an opposing member (not shown) which may be in the form of any one of the members 12, 12B, 12C and 12D hereinbefore described.

Figures 15 and 16 depict members 12F and 14F in yet a further embodiment of the adjustment assembly. In Figure 15, the members 12F and 14F are shown with their corresponding hydraulic rams 24F and 26F in a fully retracted position providing a minimal overall transverse dimension of the members 12F and 14F. This is coincident with the minimal longitudinal extension position of an associated toggle plate (not shown) .

In Figure 16, the hydraulic rams 24F and 26F are shown in their fully extended positions resulting in the maximum overall transverse dimension of the members 12F and 14F and coinciding with the maximum longitudinal extension of the toggle plate.

The main difference between the members 12F and 14F and the members 12B and 14B shown in Figures 8 and 9 is that the members 12F and 14F, when considered together extend beyond the lateral dimensions of the toggle block 88F, and frame. More particularly, in Figure 15 when the rams 24F and 26F are in the fully retracted positions, it is the wide ends of the respective members 12F and 14F that extend beyond the toggle block 88E. In Figure 16, with the rams 24F and 26F in the fully extended positions, it is the narrow end of the members 12F and 14F that extend beyond the toggle block 88E. However while the members 12F and 14F may extend beyond the frame the associated

rams 24F, 26F are maintained substantially within the frame. Another difference between the members 12F and 14F in comparison with the members 12B and 14B is the provision of slots 101 cut into the flanges 20F and 22F. The slots 101 are dimensioned and located in the respective flanges 2OF and 22F so that when the rams 24F and 26F are in the fully retracted position (shown in Figure 15) bolts or pins used to connect the hydraulic rams 24F and 26F to their respective flanges 52F and 54F can be accessed for installation or removal.

The performance and maintenance requirements of jaw crushers, as well as operating costs are affected by how long it can take for parts to be changed (ie. machine downtime) . For the embodiments described, the inventor has shown that reduced maintenance interval times can be combined with safer and easier inspection and changing of the components of the closed side setting adjustment assembly. The inventor has also been able to achieve better control of the closed side setting because the full piston area of the hydraulic ram resists any tendency for the piston rod to creep and allow the members to retract during use. In examples where there are two hydraulic rams in two back-to-back members, there is a greater degree of closed side setting adjustment available than in the known arrangements. Overall, such improvements can lead to lower materials processing costs and a more consistently-sized product.

The materials of construction of the adjustment assembly can be any suitable materials which wear appropriately, and that can be shaped, formed and fitted in the manner so described, such as the appropriate metal, metal alloys, hard plastics or even ceramics, and so on.

It is to be understood that, if any prior art information is referred to herein, such reference does not constitute an

admission that the information forms a part of the common general knowledge in the art, in Australia or any other country.

Whilst the invention has been described with reference to preferred embodiments it should be appreciated that the invention can be embodied in many other forms .