WO2025037118A1

WO2025037118A1 - A bucket crusher

Info

Publication number: WO2025037118A1
Application number: PCT/GB2024/052157
Authority: WO
Inventors: Neeraj Sharma
Original assignee: Individual
Current assignee: Individual
Priority date: 2023-08-17
Filing date: 2024-08-15
Publication date: 2025-02-20
Anticipated expiration: 2026-02-17
Also published as: GB202312566D0; GB2632684A

Abstract

A bucket crusher is provided with a hopper (12). A crusher surface is provided at or on an inner surface (16) of the hopper (12). There is a first drive element (26a) having a first eccentric drive output, the first drive element (26a) being drivable by a first motor (28a), and a second drive element (26b) having a second eccentric drive output, the second drive element (26b) being drivable by a second motor (28b). The first and second drive elements (26a, 26b) are separately driven by the first and second motors (28a, 28b). There is also a first reciprocable jaw 18a to define a first crushing zone (22a), the first reciprocable jaw 18a being drivable by the first eccentric drive output, and a second reciprocable jaw (18b) to define a second crushing zone (22a), the second reciprocable jaw 18b being drivable by the second eccentric drive output.

Description

A Bucket Crusher

The present invention relates to a bucket crusher, and more particularly to such a crusher having at least two separately eccentrically-drivable jaws. Furthermore, the invention relates to a vehicle comprising such a bucket crusher, and to a method of improving the throughput of crushed material processed by such a bucket crusher.

A bucket crusher is a tool employed to collect material and crush it into smaller aggregate through the use of crushing elements mounted within the bucket. The crushing elements included in the bucket typically comprise a reciprocable jaw and a stationary crushing surface, wherein the reciprocable jaw reciprocates within the bucket to compress and crush the material present between the jaw and the crushing surface.

The throughput of material through the bucket crusher is limited by the size of the bucket. Bucket crushers typically operate with a single crankshaft, which restricts the maximum width of the bucket and hence reduces the amount of material that can be processed in a given time.

Additionally, if the bucket crusher jams due to a piece of material which is too hard to be crushed being lodged between the reciprocable jaw and stationary crushing surface, the bucket crusher is unusable until the material is extracted. Even comparatively small pieces of material can cause a jam and prevent operation, reducing the throughput of the bucket crusher.

The present invention seeks to provide a solution which obviates or overcomes the above- mentioned deficiencies.

According to a first aspect of the invention, there is provided a bucket crusher comprising: a hopper, a crusher surface at or on an inner surface of the hopper, a first drive element having a first eccentric drive output, the first drive element being drivable or configured to be driven by a first motor; a second drive element having a second eccentric drive output, and the second drive element being drivable or configured to be driven by a second motor separately of the first motor; a first reciprocable jaw which is opposed to the crusher surface to define a first crushing zone, the first reciprocable jaw being drivable or configured to be driven by the first eccentric drive output; a second reciprocable jaw which is opposed to the crusher surface to define a second crushing zone, the second reciprocable jaw being drivable or configured to be driven by the second eccentric drive output.

Such a bucket crusher provides several advantages over the prior art. A bucket crusher operating with two spaced apart crankshafts can be wider than a crusher operating on a single crankshaft, since shorter crankshafts generally reduce the stress imparted on the bucket crusher. Additionally, such a bucket crusher substantially alleviates issues caused by a reciprocable jaw jamming or malfunctioning, since the bucket crusher can continue to operate with one of the reciprocable jaws even if the other is inoperable, potentially saving an operator from the time-consuming process of stopping the machine and unjamming or fixing the jaws. These improvements allow for a bucket crusher which can process a greater volume of material in a given time when compared to existing bucket crushers known in the art.

Optionally, each of the first motor and the second motor is a hydraulic motor. Preferably, the first motor and the second motor are connected in a parallel hydraulic drive circuit.

Hydraulic motors are well suited for use with a bucket crusher, as they can generate high torque very efficiently and are robust to harsh environmental conditions. Connecting the two motors in a parallel hydraulic drive circuit means that in the event of one of the reciprocable jaws jamming or malfunctioning, the pressure and rate of flow through the motor associated with the other reciprocable jaw will increase, generating more torque and rotational force which leads to an increase in the crushing capabilities of the non-jammed reciprocable jaw.

Optionally, the first motor and the second motor may be configured to rotate in opposite directions.

Opposite rotation of the first and second motor means that, if the motors are started at the same time, as one jaw moves away from the crusher surface, the other moves towards it, and vice versa. This means that in the ideal case wherein a phase between the two reciprocable jaws remains the same, the stress on the bucket crusher is reduced, as only one reciprocable jaw is crushing material at a time.

Advantageously, a direction of rotation of each of the first motor and the second motor may be reversible.

A direction of rotation of each of the motors being reversible is useful in the event that a reciprocable jaw jams due to a hard piece of material getting stuck between a reciprocable jaw and the crushing surface, as running the motor in reverse can lift the jaw, allowing for the hard material causing the jam to be removed.

Preferably, the hopper may include an inlet for intaking material to be crushed and an outlet for the expulsion of crushed material. Most preferably, the hopper may include a protruding scooping portion at the inlet.

An inlet and outlet defined in the hopper allows the bucket crusher to act in a similar manner to a power shovel, with the bucket crusheroperated to scoop up material to be processed and expulsed through the outlet. This is most effective when a protruding scooping portion is included in the hopper at the inlet, allowing the bucket crusher to shovel in material more effectively in operation.

Preferably, the first and second crushing zones may taper towards the outlet of the hopper.

The first and second crushing zones tapering towards the outlet allows for efficient processing of large material down to the desired size. Material may be progressively crushed to smaller and smaller sizes as it progresses through the crushing zone, which may be accomplished by gravity if the outlet is positioned to be lower than the inlet, until the crushed material is small enough to be expulsed from the crushing zone, after which it may exit the hopper through the outlet.

Optionally, a position of each of the first reciprocable jaw and the second reciprocable jaw may be adjustable or configured to be adjusted relative to the crusher surface, so as to adjust a shape of one or both of the crushing zones.

Having the position of each of the reciprocable jaws be adjustable allows the user control over the size of the outputted crushed material. Material may exit the crushing zone through the gap between the crusher surface and the jaws and thus adjusting the height of this gap alters the maximum size of the outputted crushed material.

Preferably, the bucket crusher may further comprise a first stationary jaw mounted to the inner surface of the hopper and a second stationary jaw mounted to the inner surface of the hopper, wherein the first and second stationary jaws together define the crusher surface and are opposed to the first and second reciprocable jaws respectively.

Having the crusher surface being defined by two stationary jaws mounted to the surface allows the stationary jaws to be easily removed and replaced if damaged. Having first and second stationary jaws is particularly useful in the event that the crusher surface is damaged in only one of the crushing zones as only one stationary jaw must be replaced.

Optionally, the first drive element may comprise a first eccentric crankshaft and the second drive element may comprise a second eccentric crankshaft.

Eccentric crankshafts can convert the rotational motion of the engine into the reciprocal motion of the reciprocable jaws efficiently, are simple to construct, and are robust to mechanical failures.

Optionally, the first eccentric crankshaft may be colinear with the second eccentric crankshaft.

Having the first eccentric crankshaft colinear with the second eccentric crankshaft allows for adjacent reciprocable jaws, allowing for the material to be crushed evenly. Preferably, the bucket crusher may further comprise at least one jaw bearing element upon which the first reciprocable jaw and/or the second reciprocable jaw is mountable or is configured to be mounted, and through which the first eccentric crankshaft and/or the second eccentric crankshaft are receivable or are configured to be received.

The jaw bearing elements can rotationally receive the eccentric crankshafts with reduced friction. The structure of the jaw bearing elements allows the reciprocable motion of the eccentric crankshafts to be transferred to the reciprocable jaws without transferring undesired rotational motion.

Advantageously, the bucket crusher may further comprise at least one crankshaft support, the at least one crankshaft support having at least one crankshaft support bearing element within which the first eccentric crankshaft and/or the second eccentric crankshaft is receivable or is configured to be received.

Crankshaft supports can provide structural support for the eccentric crankshafts. The crankshaft support bearing element of the crankshaft support can rotationally receive an eccentric crankshaft, reducing friction.

Most preferably, the bucket crusher may further comprise at least one support plate engageable or configured to be engaged with the hopper, wherein the at least one crankshaft support is mountable or is configured to be mounted to the support plate.

Support plates provide structural support to the mounted crankshaft support bearing elements and can help distribute the load from the eccentric crankshafts.

Preferably, the at least one jaw bearing element and/or the at least one crankshaft support bearing element is a spherical roller bearing element.

Spherical roller bearings allow rotation with very little friction, while being able to withstand heavy radial loads and allowing some misalignment.

Optionally, the bucket crusher may comprise at least one spacer on the first eccentric crankshaft and/or the second eccentric crankshaft.

Spacers may be inserted onto a crankshaft to maintain the correct position of the reciprocable jaws along the respective eccentric crankshafts.

Optionally, the first drive element may comprise a first flywheel and the second drive element may comprise a second flywheel, the first and second flywheels being connected to the first eccentric shaft and the second eccentric shaft respectively. A flywheel connected an eccentric crankshaft helps to keep the rotation of each of the eccentric crankshafts constant, providing a smoother delivery of power from the motor to the reciprocable jaws.

Optionally, the operating power of the first reciprocable jaw may be different to the operating power of the second reciprocable jaw.

The material inputted into the bucket crusher is often inhomogeneous, and may contain materials of different hardness. If the first crushing zone contains much harder material than the second crushing zone, it may be beneficial for the first reciprocable jaw to have a greater operating power than the second reciprocable jaw.

Optionally, three or more reciprocable jaws are provided, the bucket crusher including a complementary number of driving elements and motors.

The bucket crusher may include more than two reciprocable jaws, which allows for the bucket crusher to be scaled to larger sizes and potentially provides even more advantages in terms of alleviating issues caused by the reciprocable jaws jamming or malfunctioning, as a single jammed or broken jaw has a lesser impact on the productivity of the bucket crusher if a greater number of reciprocable jaws are included in the bucket crusher.

Preferably, the bucket crusher may be adapted to be mountable to an excavator or a wheel loader.

Excavators and wheel loaders are heavy construction equipment well suited to receive and operate a bucket crusher, due to their high lifting capabilities. Excavators and wheel loaders also typically operate hydraulically, which allows for a bucket crusher comprising hydraulic motors to be easily connected and operated.

According to a second aspect of the invention, there is provided a vehicle comprising a bucket crusher as claimed in any one of the preceding claims. Preferably, the vehicle may be in the form of an excavator or a wheel loader.

The bucket crusher may be included in a vehicle to provide a highly mobile means to scoop and crush material. An excavator or wheel loader are well suited to include a bucket crusher due to their high lifting capabilities and hydraulics.

According to a third aspect of the invention, there is provided a method of improving throughput of crushed material using a bucket crusher according to the first aspect of the invention, the method comprising the step of: a] providing at least two separately drivable reciprocable jaws, so that if the one of the said at least two reciprocable jaws jams, the remainder of the said at least two reciprocable jaws continue to operate. Such a method improves the throughput of a bucket crusher by substantially alleviating issues caused by jams, since the bucket crusher can continue to operate in the event of a jaw jamming, preventing the lengthy process of halting operation to unjam the bucket crusher.

Preferably, the method may further comprise the step of: b] connecting the at least two reciprocable jaws to a hydraulic circuit, such that if one of the said at least two reciprocable jaws jams, the remainder of the at least two reciprocable jaws receive an increased driving force via the parallel hydraulic drive circuit.

Connecting the jaws in a parallel hydraulic drive circuit means that in the event of one of the reciprocable jaws jamming, the remainder of the at least two reciprocable jaws receive an increased driving force via the parallel hydraulic drive circuit, increasing the crushing capabilities of the nonjammed reciprocable jaws.

The invention will now be more particularly described, by way of example only, with reference to the accompanying drawings, in which:

Figure 1 shows an isometric view of an embodiment of a bucket crusher in accordance with the first aspect of the invention;

Figure 2 shows an exploded view of the bucket crusher of Figure 1;

Figure 3 shows an isometric view of a hopper of the bucket crusher of Figure 1;

Figure 4 shows an isometric view of a reciprocable jaw of the bucket crusher of Figure 1 ;

Figure 5 shows an isometric view of an eccentric crankshaft of the bucket crusher of Figure 1 ;

Figure 6 shows an exploded view of a crankshaft support of the bucket crusher of Figure 1

Figure 7a shows a first spacer of the bucket crusher of Figure 1 ;

Figure 7b shows a second spacer of the bucket crusher of Figure 1; and

Figure 8 shows a diagrammatic representation of a parallel hydraulic circuit of the bucket crusher of Figure 1.

Referring to Figures 1 and 2, there is indicated an embodiment of a bucket crusher, referenced globally at 10. The bucket crusher 10 comprises a hopper 12, a crusher surface 14 at or on an inner surface 16 of the hopper 12, a first reciprocable jaw 18a, and a second reciprocable jaw 18b. In the illustrated embodiment, a first stationary jaw 20a and a second stationary jaw 20b are provided and are mounted to the inner surface 16 of the hopper 12 which define the crusher surface 14. The first and second reciprocable jaws 18a, 18b are opposed to the respective first and second stationary jaws 20a, 20b to define a first crushing zone 22a and a second crushing zone 22b, respectively. In the depicted embodiment, the bucket crusher 10 is adapted to be mountable to a wheel loader via an attachment bar 24, although other attachment means are possible, such as a mounting bracket which may be used to mount the bucket crusher 10 to a wheel loader or an excavator.

The bucket crusher 10 is provided with a first drive element 26a drivable by a first motor 28a and a second drive element 26b drivable by a second motor 28b. The first and second drive elements 26a, 26b have a respective first and second eccentric drive output, for driving the first and second reciprocable jaws 18a, 18b respectively. The first and second drive elements 26a, 26b are drivable separately and independently of each other.

The structure of the hopper 12 can be seen more clearly with reference to Figure 3. The hopper 12 comprises a first side wall 30a and a second side wall 30b, with the two side walls 30a, 30b preferably being planar or substantially planar. The two side walls 30a, 30b are opposed to one another, and are preferably parallel or substantially parallel. The distance between the two side walls 30a, 30b defines a width of the hopper 12.

In the depicted embodiment, each of the side walls 30a, 30b has a top edge 32a, 32b and opposing bottom edge 34a, 34b and a front edge 36a, 36b and opposing rear edge 38a, 38b. Each of the side walls 30a, 30b includes receiving means or elements to allow other components of the bucket crusher 10 to be engageable with the hopper 12. The receiving means includes one or more apertures and slots in the side walls 30a, 30b. The receiving means comprises an attachment bar receiving aperture 40a, 40b on the first and second side walls 30a, 30b respectively. The attachment bar 24 extends through the attachment bar receiving aperture 40a, 40b of each of the first and second side walls 30a, 30b. The receiving means of each of the side walls 30a, 30b comprises a crankshaft support receiving slot 42a, 42b and a motor support aperture 44a, 44b, which are described in more detail below. The receiving means included in the first side wall 30a are preferably identical and directly opposed to the receiving means included in the second side wall 30b.

The two side walls 30a, 30b are interconnected at, adjacent or near their bottom edges 34a, 34b by a base wall 46, which is preferably perpendicular to each of the side walls 30a, 30b. The crusher surface 14 of the bucket crusher 10 is located at or on the inner surface 16 of this base wall 46. The two side walls 30a, 30b is also interconnected at, adjacent or near the top edges 32a, 32b by one or more connecting members.

Each of the first side wall and the second side wall 38a, 38b include a flange portion 48a, 48b at its bottom, which extends beyond at least a portion along a length of the base wall 46 of the hopper 12. The flange portion 48a, 48b helps to prevent the outer surface of the base wall 46 from contacting the ground, which can provide some protection of the base wall 46. The two parallel flange portions 48a, 48b can aid the movement of the bucket crusher 10 if it is slid across the ground, similar to the runners of a sled. The flange portions 48a, 48b also extend perpendicularly or substantially perpendicularly from the side walls 30a, 30b to better support and distribute the weight of the bucket crusher 10.

In the depicted and preferred embodiment of the bucket crusher 10, the connecting members are provided as two support beams 50, with the two support beams 50 being positioned on either side of the crankshaft support receiving slots 42a, 42b. These support beams 50 are shown with an attachment means, provided as a plurality of bolt holes 52, to allow other elements of the bucket crusher 10 to be engaged with the hopper 12. The bolt holes 52 allow for first and second support plates 54a, 54b to be engaged with the hopper 12, the purpose of which is described in more detail below. If the first and second support plates 54a, 54b are included, the two support beams 50 and the support plates 54a, 54b together define a top of the hopper 12, as illustrated in the depicted embodiment. Otherwise, the top of the hopper 12 is defined solely by the connecting members.

The hopper 12 of the bucket crusher 10 preferably has a rectangular or substantially rectangular cross section, which allows for components to easily be mounted to or engaged with the flat or planar surfaces of the bucket crusher 10.

An inlet 56 is defined in the hopper 12 at a front end, and an outlet 58 is defined at the opposing rear end of the hopper 12, with the boundaries of each of the inlet 56 and outlet 58 being delimited by the base wall 46, the two side walls 30a, 30b, and the support beams 50. The inlet 56 allows the intake of material to be crushed, and the outlet 58 allows for crushed material to be expelled from the hopper 12. A material flow direction is defined from the inlet 56 to the outlet 58, which in the depicted embodiment is straight or linear or substantially straight or linear.

In the depicted embodiment, the base wall 46 includes a front base wall portion 60 at or adjacent to the front end of the of the hopper 12, a rear base wall portion 62 at or adjacent to the rear end of the hopper 12, and an intermediate base wall portion 64 therebetween. Whilst the rear and intermediate base wall portions 62, 64 are provided between the first and second side walls 30a, 30b, the front base wall portion 60 has a first part 66 which extends past the bottom edge 34a, 34b of the two side walls 30a, 30b to provide additional structural support, and has a second scooping part 68 which protrudes past a front edge 36a, 36b of each of the side walls 30a, 30b effectively forming a protruding scooping portion. This second scooping part 68 allows for material to be more easily collected into the bucket crusher 10, allowing for the bucket crusher 10 to be operated without the need of an external loading shovel or digger to deposit material into the bucket crusher 10. Furthermore, the second scooping part 68 provides a sloped scooping surface, extending upwardly from the front to rear direction to further assist with directing material into the hopper 12. In the depicted embodiment, the two flange portions 48a, 48b extend from the rear edges of the first and second side walls 30a, 30b and abut the front base wall portion 60 to provides additional structural support.

In the depicted embodiment, the crusher surface 14 of the bucket crusher 10 is preferably located at or on the inner surface of the rear base wall portion 62. The wall portions 60, 62, 64 are separate components, with the front base wall portion 60 preferably being removably attached to the bottom edges of the side walls 30a, 30b. This allows for the front base wall portion 60 to be to be individually removed and replaced, which is advantageous because the front base wall portion 60 is subject to much more wear than the rest of the base wall 46, and as such may need replacing more frequently.

The front, intermediate and rear base wall portions 60, 62, 64 are angled relatively to one another such that they are not co-planar with adjacent wall potions. The base wall portions 60, 62, 64 of the base wall 46 are planar or substantially planar. The base wall portions 60, 62, 64 are positioned such that, in use, the material is directed in the material flow direction, i.e. from the inlet 56 to the outlet 58. In particular, the intermediate base wall portion 64 is angled upwardly from the front to rear direction. The rear base wall portion 62 is offset from and below the intermediate base wall portion 64, disposing a gap 63 therebetween, so that the first and second stationary jaws 20a, 20b mounted on the rear base wall portion 62 which define the crusher surface 14 are positioned appropriately adjacent the intermediate base wall portion 64 to receive the material for crushing.

The base wall portions 60, 62, 64 being positioned in this way means that material can easily move in the material flow direction to the crusher surface 14, but material moving opposed to the material flow direction will catch against the edge of the intermediate base wall portion 64 or the front base wall portion 60. This means that material is biased towards moving in the material flow direction, helping to prevent material from exiting the bucket crusher 10 before being processed.

The front and intermediate base wall portions 60, 64 are inclined at different angles relative to the rear base wall portion 62. The intermediate base wall portion 64 is inclined at a steeper angle than that of the front base wall portion 60. This gives the base wall 46 an overall curve, which allows the bucket crusher 10 to scoop material more easily. The intermediate base wall portion 64 and the rear base wall portion 62 may be attached in a similar manner to the front base wall portion 60, but preferably they may instead extend between the inner surfaces of each of the side walls 30a, 30b. This prevents these wall portions 62, 64 from contacting the ground, which allows the bucket crusher 10 to be slid more easily along the ground, which is especially useful if the bucket crusher 10 is to be operated by a wheel loader.

The hopper 12 is made of material of appropriate hardness to perform scooping of material and to provide a receptacle for the material to be crushed therein, such as for example steel.

The crusher surface 14 of the bucket crusher 10 is defined by the first and second stationary jaws 20a, 20b, which are mounted at or on the rear base wall portion 62 of the base wall 46. The first and second stationary jaws 20a, 20b includes first and second jaw plates 70a, 70b respectively, each of the first and second jaw plates 70a, 70b having a plurality of jaw teeth 72 formed as rows of alternating ridges and troughs thereon, which define the crusher surface 14.

In the depicted embodiment, the jaw teeth 72 are provided in rows along the width of the hopper 12, such that each ridge or trough extends along in parallel or substantially parallel to the front to rear direction of the hopper 12. This allows the crusher surface 14 to extend and continue from the first jaw plate 70a to the second jaw plate 70b seamlessly with ease. However, it will be appreciated that the jaw teeth 72 may be angled differently, such that each ridge or trough extends perpendicularly or substantially perpendicularly, or at an obtuse or acute angle, to the front to rear direction of the hopper 12. In a further alternative, other types of jaw teeth 72 may be provided, such as a plurality of spikes spaced at regular or irregular intervals, of the same or different sizes and shapes.

The first and second jaw plates 70a, 70b have identical dimensions and jaw teeth 72 arrangement so that they can be interchanged conveniently to provide the same functionality. However, different jaw plates 70a, 70b may be provided that are different in size, shape and/or jaw teeth 72 arrangement in order provide different functionalities between the first and second crushing zones.

The crusher surface 14, which in the depicted embodiment is defined by the first and second jaw plates 70a, 70b, is preferably made of a hard material such as, for example, steel or manganese.

Each of the jaw plates 70a, 70b of the stationary jaws 20a, 20b are separately mounted to the rear base wall portion 62 of the bucket crusher 10 in a removable manner, to allow one or both of the stationary jaws 20a, 20b to be replaced in the event of wear or damage. Suitable mounting means include brackets, bolts or screws, and/or dovetail slots and corresponding protrusions. Evidently, more permanent attachment means are possible, such as for example a welded connection. Alternatively, the first and second stationary jaws 20a, 20b may be internally formed as one jaw having a single jaw plate defining the crusher surface 14, the single jaw plate being mounted to the inner surface 16 of the hopper 12 in a removable manner.

The crusher surface 14 spans or substantially spans the width of the hopper 12 to maximise crushing capacity. The jaw plate 70a, 70b of the first and second stationary jaws 20a, 20b are aligned such that the crusher surface 14 extends across seamlessly or substantially seamlessly.

The first reciprocable jaw 18a is shown in Figure 4 and comprises a first pitman 74a and a third jaw plate 70c mounted to the pitman. In the depicted embodiment, the second reciprocable jaw 18b is identical or substantially identical to the first reciprocable jaw 18a and also comprises a second pitman 74b and a fourth jaw plate 70d mounted to the second pitman 74b. In the embodiment depicted, the first and second reciprocable jaws 18a, 18b have identical dimensions, but any of the reciprocable jaws 18a, 18b, pitmans 74a, 74b, and jaw plates 70a, 70b, 70c, 70d may have different shapes or sizes while still falling within the scope of the present invention. The first reciprocable jaw 18a is described in detail below and is applicable to the second reciprocable jaw 18b also in relation to its corresponding components.

In the embodiment shown, the first pitman 74a comprises a pitman mounting portion 76 for mounting the pitman 74a to the hopper 12 through the first drive element 26a and a jaw plate support portion 78 extending from the pitman mounting portion 76 for the third jaw plate 70c to be attached and supported thereto. The pitman mounting portion 76 is a cylindrical sleeve or tube member defining a hole 80 therethrough, through which the first drive element 26a is releasably receivable. The jaw plate support portion 78 includes two spaced apart support members 82 extending perpendicularly or substantially perpendicularly from an axial extent of the cylindrical sleeve member and three spaced apart mounting members 84 which extend perpendicularly or substantially perpendicularly from the support members 82. A jaw plate facing surface of the mounting members 84 being flat or substantially flat to allow easy connection of the third jaw plate 70c to the first pitman 74a. Preferably, the first pitman 74a is provided with a plurality of bolt holes (not shown) to allow a nut and bolt connection between the third jaw plate 70c and the first pitman 74a.

The first pitman 74a is structured in this way to allow for a solid connection between the first pitman 74a and the third jaw plate 70c, while reducing the weight of the first pitman 74a. Alternatively, the jaw plate support portion of the first pitman may have a solid substantially planar component, for ease of construction. It will be further appreciated that the precise number of support members and mounting members may vary from the depicted embodiment, whereby an increase in size and weight of the pitman mounting portion and/or the third jaw plate may call for an increase in the number or size of the support members and mounting members, and vice versa. Each of the first and second pitmans 74a, 74b is advantageously detachable from the respective first and second drive elements 26a, 26b. This allows for replacing the pitmans 74a, 74b in case of damage, or substituting a pitman 74a, 74b for one with different dimensions or of a different type.

Each of the third and fourth jaw plates 70c, 70d comprise jaw teeth formed as alternating rows of ridges and troughs, in a manner similar to those of first and second jaw plates of the first and second stationary jaws 20a, 20b. Preferably, the ridges of the third and fourth jaws plates 70c, 70d correspond to the troughs of the first and second jaw plates 70a, 70b respectively and vice versa, to increase the crushing force exerted on material in the bucket crusher 10. The third and fourth jaw plates 70c, 70d have the same or substantially the same dimensions as that of the first and second jaw plates 70a, 70b. The third and fourth jaw plates 70c, 70d of the first and second reciprocable jaws 18a, 18b which are opposed to the first and second jaw plates 70a, 70b of the first and second stationary jaws 20a, 20b define the first and second crushing zones 22a, 22b respectively.

Each of the third and fourth jaw plates 70c, 70d being removably attached from the respective first and second pitmans 74a, 74b allows for the jaw plates 70c, 70d to be easily replaced in case of damage. Evidently, more permanent attachment means are possible, such as for example a welded connection.

The third and fourth jaw plates 70c, 70d preferably have identical or substantially identical dimensions to the respective first and second jaw plates 70a, 70b, and most preferably all of the jaw plates 70a, 70b, 70c, 70d have identical dimensions. The third and fourth jaw plates 70c, 70d are subject to more wear than the first and second jaw plates 70a, 70b, and thus a method to extend the lifetime of the bucket crusher 10 involves periodically swapping the first and second jaw plates 70a, 70b with the third and fourth jaw plates 70c, 70d to extend the lifetime of the bucket crusher 10. Evidently, the jaw can be independently swapped. Should, for example, the first reciprocable jaw 18a suffer more wear than the second reciprocable jaw 18b, the third jaw plate 70c may be swapped with the first jaw plate 70a, or indeed the second jaw plate 70b, while the fourth jaw plate 70d may be left in place.

In the depicted embodiment, each of the first to fourth jaw plates 70a, 70b, 70c, 70d is planar or substantially planar and the dimensions of the ridges and troughs of the jaw teeth 72 are the same or substantially the same across the plates. In an alternative, any of the first to fourth jaw plates 70a, 70b, 70c, 70d may be convex, either by varying the thickness of the jaw plate 70a, 70b, 70c, 70d and/or the distance between the ridge and trough of the jaw teeth 72. Convex jaw plates provide greater crushing pressure towards the centres of the first and second crushing zones 22a, 22b, allowing for the bucket crusher 10 to crush harder materials more effectively when compared to flat jaw plates. An alternative preferred embodiment of the bucket crusher 10 has each of the jaw plates 70a, 70b, 70c, 70d be convex, but any combination of flat jaw plates, concave jaw plates, and convex jaw plates is possible without deviating from the scope of the present invention.

Preferably, each of the third and fourth jaw plates 70c, 70d are made from a material that is substantially harder than the material to be crushed. Examples of suitable materials include, but are not limited to, steel or manganese.

Each of the first reciprocable jaw 18a and the second reciprocable jaw 18b is positioned between the first and second side walls 30a, 30b. Preferably, the first reciprocable jaw 18a and the second reciprocable jaw 18b are positioned adjacent or close to the first side wall 30a and the second side wall 30b respectively, to minimise the distance between the first reciprocable jaw 18a and the first side wall 30a and the distance between the second reciprocable jaw 18b and the second side wall 30b. In this case, the first and second side walls 30a, 30b delineate the lateral extent of the combined first and second crushing zones 22a, 22b. The first reciprocable jaw 18a and the second reciprocable jaw 18b are preferably adjacent to each other, thus the combined first and second crushing zones 22a, 22b spans or substantially spans the width of the bucket crusher 10.

Alternative structures of the reciprocable jaws are also possible. For example, each of the reciprocable jaws may be provided as a single solid component with ridges and teeth to aid with crushing, rather than the jaw plate being included as a separate component attached to the pitman.

The first and second reciprocable jaws 18a, 18b are supported and driven by the respective first and second drive elements 26a, 26b. The structure of each of the first and second drive elements 26a, 26b will now be described in more detail, with particular reference to Figures 2 and 5. In the depicted embodiment, the first and second drive elements 26a, 26b are identical or substantially identical. Thus discussion regarding the first drive element 26a is applicable to the second drive element, and vice versa.

The second drive element 26b is spaced apart from the first drive element 26a along the width of the hopper 12. In the depicted embodiment, the first drive element 26a comprises a first eccentric crankshaft 84a, a first pulley 86a connected to the first eccentric crankshaft 84a, and a first belt drive 88a interconnecting the first pulley 86a and a first motor shaft 90a of the first motor 28a. Similarly, the second drive element 26b comprises a second eccentric crankshaft 84b, a second pulley 86b connected to the second eccentric crankshaft 84b, and a second belt drive 88b interconnecting the second pulley 86b and a second motor shaft (not shown) of the first motor 28b. In the depicted embodiment, the first and second pulleys 86a, 86b, first and second belt drives 88a, 88b, the first and second motor shafts 90a and the first and second motors 28a, 28b are provided outside the hopper 12 to maximise the crusher surface 14 and the first and second crushing zones 22a, 22b inside the hopper 12, ensuring the entire width or substantially entire width of the hopper 12 is utilised for crushing.

Each of the motors 28a, 28b is connected to the respective side walls 30a, 30b at the motor support aperture 44a, 44b via attachment means (not shown) such as a bolt or welding, or optionally instead connected to components on the other side of the apertures. The motor support apertures 44a, 44b may be used to connect the motors 28a, 28b via a hydraulic drive circuit, for example via hydraulic hoses passing through the apertures to connect to the motors 28a, 28b, allowing connection to an existing hydraulic system with a pump, such as a hydraulic system of an excavator or wheel loader.

The first pulley and the second pulley 86a, 86b have a larger diameter than the first motor shaft 90a and a second motor shaft, respectively. Each of the pulleys 86a, 86b thus acts as a flywheel, which helps to keep the rotation of each of the eccentric crankshafts 84a, 84b constant. In embodiments of the bucket crusher 10 where the drive element 26a, 26b does not comprise a pulley 86a, 86b, each of the first and second eccentric crankshafts 84a, 84b may still have an attached flywheel for this purpose.

The respective pulleys 86a, 86b and belt drives 88a, 88b provide an efficient way of transmitting rotation from the motors 28a, 28b to the eccentric crankshafts 84a, 84b. Having a belt drive 88a, 88b and pulley 86a, 86b included in each of the drive elements 26a, 26b has the advantage of preventing a direct connection between the eccentric crankshafts 84a, 84b and the motors 28a, 28b. This can protect shocks being transferred from the eccentric crankshafts 84a, 84b to the motors 28a, 28b, preventing damage to the motors 28a, 28b.

Figure 5 shows the first eccentric crankshaft 84a of the bucket crusher 10 in detail. In the depicted embodiment, the first and second eccentric crankshafts 84a, 84b have identical dimensions, but the shape and sizes of the eccentric crankshafts 84a, 84b may be different, for example if it was desired to have each of the reciprocable jaws 18a, 18b operate with a substantially different reciprocal motion. The eccentric crankshafts 84a, 84b are preferably colinear or substantially colinear, such that the two reciprocable jaws 18a, 18b are adjacent, to evenly crush the material. Of course, the two crankshafts 84a, 84b may instead be offset, rotating about separate axes.

The first eccentric crankshaft 84a comprises two end portions 92, 93 and a central portion 94 which interconnects the two end portions 92, 93. As illustrated in Figure 5, the end portions 92, 93 have a first rotation axis 96 and the central portion 94 has a second rotation axis 98 that is offset from the first rotation axis 96. The central portion 94 is therefore eccentric with respect to the end portions 92 by an eccentric distance, the eccentric distance being the distance between the first and second rotation axis . This allows for the first eccentric crankshaft 84a to provide an eccentric drive output. Preferably, the eccentric distance is greater than 5mm, more preferably between 5mm and 30mm, even more preferably 10mm to 20mm. Most preferably, the eccentric distance is 14mm. The reciprocating movement of the central portion 94 up and down about the first rotation axis of the first eccentric crankshaft 84a is transferred to the first reciprocable jaw 18a, crushing material between the first reciprocable jaw 18a and first stationary jaw 20a.

The central portion 94 and end portions 92 of the first eccentric crankshaft 84a may themselves be segmented. In in depicted embodiment of the bucket crusher 10, the central portion 94 of the eccentric crankshafts 84a, 84b comprises three sections. These sections include a primary central section 102 having a largest diameter and two secondary central sections 104 having equal or substantially equal diameters, with diameters which are less than the primary central section 102 and greater than the end sections 92, 93. The secondary central sections 104 interconnect the end portions 92, 93 and the primary central section 102. Each of the secondary central sections 104 preferably has equal length or axial extent, which is shorter than a length or an axial extent of the primary central section 102.

The above description in relation to the first eccentric crankshaft 84a is applicable also to the second eccentric crankshaft 84b.

The first and second eccentric crankshafts 84a, 84b are receivable through the pitman mounting portion 76 of the first and second reciprocable jaws 18a, 18b . Preferably, the reciprocable jaws 18a, 18b are not directly mounted onto the eccentric crankshafts 84a, 84b. Instead, the eccentric crankshafts 84a, 84b are connected to the respective reciprocable jaws 18a, 18b via first and second spaced apart jaw bearing elements 106a, 107a, 106b, 107b respectively, which can be seen in Figure 2. The first and second jaw bearing elements 106a, 107a, 106b, 107b are the same or substantially the same.

Each of the jaw bearing elements 106a, 107a, 106b, 107b is a spherical roller bearing, having an inner ring (not shown) with an inner diameter equal to an outer diameter of the secondary central section 104 of the eccentric crankshafts 84a, 84b and having an outer ring with an outer diameter equal to an inner diameter of the pitman mounting portion 76. Between the inner ring and the outer ring are two rolls of rollers (not shown), which are interconnected by a cage (not shown). Spherical roller bearings are preferred over other types of bearings due to spherical roller bearings being able to take very high radial loads and additionally allowing some misalignment between the first rotation axis 96 of the eccentric crankshafts 84a, 84b and an axis of the reciprocable jaws 18a, 18b. This allows the bucket crusher 10 to operate even if the eccentric crankshafts 84a, 84b are knocked slightly out of alignment, or warp due to the stress imparted on the eccentric crankshafts 84a, 84b. The eccentric crankshafts 84a, 84b are rotationally received within the inner rings of the respective jaw bearing elements 106a, 107a, 106b, 107b with the rollers allowing the eccentric crankshafts 84a, 84b to rotate with very little friction. Friction may further be reduced by lubricating the jaw bearing elements 106a, 107a, 106b, 107b for example with lubricating oil or grease.

The jaw bearing elements 106a, 107a, 106b, 107b are received within the respective cylindrical sleeve member of the pitman mounting portions 76 of the reciprocable jaws 18a, 18b. The outer ring of each of the jaw bearing elements 106a, 107a, 106b, 107b is rigidly connected to an inner surface of cylindrical sleeve member, which may be accomplished via a tight friction fit or by more permanent means, for example a welded connection. With respect to the reciprocable jaws 18a, 18b, the outer ring of each of the jaw bearing elements 106a, 107a, 106b, 107b are therefore stationary, whereas the inner ring rotates.

In this manner, the jaw bearing elements 106a, 107a, 106b, 107b constrain the motion of the reciprocable jaws 18a, 18b, allowing the eccentric crankshafts 84a, 84b to transfer the desired reciprocating motion to the reciprocable jaws 18a, 18b without transferring the full rotation of the eccentric crankshafts 84a, 84b.

In a preferred embodiment of the invention, the first and second jaw bearing elements 106a, 107a, 106b, 107b are dimensioned to receive the secondary central sections 104 of the respective eccentric crankshafts 84a, 84b. Evidently, the inner diameter of the inner rings of the jaw bearing elements 106a, 106b may correspond to any diameter of the secondary central sections 104 of the central portion 94 of the eccentric crankshafts 84a, 84b. It will be appreciated that although two identical jaw bearing elements are provided per eccentric crankshaft it is possible to provide only one or more than two. Furthermore, the plurality of jaw bearing elements need not be identical, and may have different inner diameters, corresponding to different diameters of sections of the central portion of the eccentric crankshafts.

Figure 6 shows an exploded view of a crankshaft support 108, to be included in the bucket crusher 10 for the purpose of supporting the first or second eccentric crankshaft 84a, 84b. The crankshaft support 108 has a crankshaft support bearing element 110 through which the first or second eccentric crankshaft 84a, 84b is rotatably received. The crankshaft support 108 provides structural support for the first or second eccentric crankshaft 84a, 84b and reduces the friction of the rotating eccentric crankshaft 84a, 84b, increasing the efficiency of the bucket crusher 10. In the depicted embodiment, the crankshaft support bearing element 110 is a spherical roller bearing, and has the capability of allowing rotation with very little friction while being able to withstand high radial loads and allowing some misalignment. The crankshaft support bearing elements 110 are spherical roller bearings with components the same or substantially the same as the jaw bearing elements 106a, 106b. The crankshaft support bearing elements 110 have an inner ring 114 with an inner diameter equal to an outer diameter of the end portions 92 of the eccentric crankshafts 84a, 84b and have an outer ring 118. Between the inner ring 114 and the outer ring 118 of the crankshaft support bearing element 110 are two rolls of rollers 116 (one roll is visible in Figure 6), which are interconnected by a cage (not shown). Spherical roller bearings are preferred over other types of bearing for the reasons mentioned above.

The crankshaft support 108 further includes a crankshaft support housing member 120 to accommodate and support the crankshaft support bearing element 110 thereto. The crankshaft support housing member 120 has an aperture 122 through its two sides, a diameter of the aperture 122 being sized to correspond to the outer diameter of the outer ring 118 of the crankshaft support bearing element 110. The crankshaft support bearing element 110 is rigidly connected to the crankshaft support housing member 120 via a tight fiction fit or by more permanent means, for example a welded connection. The crankshaft support housing member 120 has an outer perimeter 124 shaped complimentarily with the crankshaft support receiving slot 42a, 42b of the hopper 12, so that the crankshaft support housing member 120 is accommodated and connected thereto. As a top of the crankshaft support receiving slot 42a, 42b is not bound by the first or second side wall of the hopper 12, the crankshaft support 108 can slide out of the first or second side wall in a bottom to top direction, if access to the crankshaft support 108 is required, for example for maintenance or replacement. Furthermore, in use, a top edge of the crankshaft support housing member 120 is flush with the top edge of the first or second side wall of the hopper 12.

The crankshaft support receiving slot 42a, 42bs of the hopper 12 provide support to the crankshaft supports 108 and thus the crankshafts 84a, 84b, and help distribute the loads through the bucket crusher 10.

In the depicted embodiment, each of the first and second eccentric crankshafts 84a, 86b are provided with two such crankshaft supports 108, each being rotationally received within and supported by the two crankshaft supports 108 positioned on the end portions 92, 93, i.e. at either side of the central portion 94, of the respective eccentric crankshafts 84a, 84b. As described above, one of the two crankshaft supports 108 lies or substantially lies in the plane of the first or second side wall of the hopper 12 and the other crankshaft support 108 is parallel to the side walls 30a, 30b, with the two crankshaft supports 108 being colinear, such that the first or second eccentric crankshaft 84a, 84b received through said crankshaft supports 108 is perpendicular to said side walls 30a, 30b of the hopper 12. Furthermore, the end portion 93 of the first or second eccentric crankshaft 84a, 84b closest to the respective first or second side wall 30a, 30b is longer in its axial extent compared to the other end portion 92 of said eccentric crankshaft 84a, 84b so as to extend through one of the crankshaft supports 108 and engage with the respective pulley 86a, 86b. The crankshaft support 108 positioned on the opposing end portion 92 of the first or second eccentric crankshaft 84a, 84b is not connected to the first or second side wall 30a, 30b, but is adjacent to the corresponding crankshaft support 108 of the second or first eccentric crankshaft 84a, 84b. There is a small gap therebetween to allow the first and second eccentric crankshaft 84a, 84b to rotate freely and independently of each other.

In an alternative embodiment, the first and second eccentric crankshafts may each be supported at one end by only an aperture included in the respective first and second side walls and supported at the other end by the crankshaft support. It is also possible for no crankshaft supports to be included, with each of the eccentric crankshafts being received through an aperture of the first side wall at one end and received through a corresponding aperture of the second side wall at the other end.

As illustrated in Figures 7a and 7b, each of the first and second eccentric crankshafts 84a, 84b has two sets of spacers 126, 128 thereon, each set comprising a first spacer 126 and a second spacer 128 thereon, each set being provided on either side of the primary central section 102 of the central portion 94 of the respective eccentric crankshaft 84a, 84b. The spacers 126, 128 prevent undesired movement of the jaw bearing elements 106a, 106b along the longitudinal axis of the eccentric crankshafts 84a, 84b, keeping the reciprocable jaws 18a, 18b in the correct position. The first spacer 126 and the second spacer 128 are a ring-shaped sleeve having a respective first aperture 130 and second aperture 132 to receive the eccentric crankshaft 84a, 84b therethrough. An inner diameter and outer diameter of the first spacer 126 are different to that of the second spacer 128, as they are designed to correspond to and locate at different positions along the respective eccentric crankshaft 84a, 84b and are connected tightly thereto. In depicted embodiment, the first spacers 126 are located on the two secondary central sections 104 of the central portion 94 of the eccentric crankshaft 84a, 84b respectively and the second spacers 128 are located on the two end portions 92, 93 of the eccentric crankshaft 84a, 84b respectively.

In the depicted embodiment, each set of the first and second spacers 126, 128 is inserted between the respective 106a, 106b and the crankshaft support 108, with the 106a, 106b being prevented from moving along the eccentric crankshaft 84a, 84b in one direction by the primary central section 102 of the central portion 94, and prevented in the other direction by spacers 126, 128 inserted on the eccentric crankshaft 84a, 84b. Effectively, the spacers 126, 128 brace the jaw bearing elements 106a, 106b against the crankshaft supports 108, preventing undesired movement along the eccentric crankshaft 84a, 84b.

It is evident how spacers 126, 128 may adjust the position of the jaw bearing elements 106a, 106b and thus the reciprocable jaws 18a, 18b along the crankshaft, for example by inserting a spacer between the jaw bearing elements 106a, 106b and the primary central section 102. For this purpose, spacers of different sizes may be provided, with larger width spacers providing a greater adjustment to the position of the first or second reciprocable jaw along the respective crankshaft than smaller width spacers. Evidently, multiple smaller width spacers could be used in the same manner as a larger spacer.

The inner diameter of the spacer 126, 128 corresponds to a diameter of the respective eccentric crankshaft 84a, 84b, and the outer diameter may vary to provide an increased diameter on the crankshaft where the spacer 126, 128 is inserted.

Each crankshaft support 108 includes attachment means to allow the crankshaft supports 108 to be attached to other components of the bucket crusher 10. Preferably, the attachment means comprises a plurality of bolt holes.

The crankshaft supports 108 may be directly connected to the hopper 12, for instance via a bolted connection or a welded connection.

Preferably, each of the crankshaft supports 108 may be mounted to its respective support plate 54a, 54b, with the support plate 54a, 54b being engaged with the hopper 12. The top edge of each crankshaft support 108, which is planar or substantially planar, allows each crankshaft support 108 to be easily connected to the support plate 54a, 54b, for example by welding or via a bolted connection. The first and second support plate 54a, 54b are provided for the respective first and second reciprocable jaws 18a, 18b and respective first and second drive elements 26a, 26b, with each of the support plates 54a, 54b having two crankshaft supports 108 mounted thereupon.

Each support plate 54a, 54b includes engagement means or portions, to allow the support plates 54a, 54b to be engageable with the hopper 12 of the bucket crusher 10. Preferably, the support plates 54a, 54b are releasably engaged, for example by being bolted to the hopper 12 via a nut and bolt, with bolt holes included in the support plates 54a, 54b and the hopper 12. This allows the support plates 54a, 54b to be easily removed and installed, allowing for support plates 54a, 54b to be replaced in case of damage, or allowing for the support plates 54a, 54b to be removed to allow access to other components of the bucket crusher 10 for repair or replacement. Other engagement means, such as for example a welded connection between the support plates and hopper are possible.

While it is preferred that the bucket crusher includes two support plates to provide support for each of the two eccentric crankshafts and reciprocable jaws it is possible to instead have only one support plate, positioned across or substantially across the full width of the bucket crusher, to which all of the crankshaft supports are mounted. Alternatively, smaller but greater number of support plates could be provided, with one support plate being provided for each crankshaft support. Although the attachment bar is provided for attaching the bucket crusher to a vehicle, alternative or further attachment means may be mounted to the support plates to allow for the bucket crusher to be attached to heavy machinery such as a wheel loader or excavator. In particular, an attachment bracket may be mounted to the support plates to allow connection with the arm of an excavator.

The present invention thus provides a bucket crusher 10 having hopper 12 with a crusher surface 14 and combined crushing zone 22a, 22b therein that is wider than that of a crusher operating on a single crankshaft only. In a preferred embodiment, an inner width of the hopper 12 is preferably between 1000mm to 3000mm, more preferably 1500mm to 2500mm, even more preferably 1600mm to 2000mm, and most preferably 1800mm. Each of the jaw plates 70a, 70b, 70c, 70d is half or substantially half of the inner width. A distance between the top and bottom edges of the first or second side wall is preferably between 500mm and 1500 mm, more preferably 700mm and 1350mm, and most preferably 1080mm.

It is envisioned that the bucket crusher may be provided with three or more reciprocable jaws with a complementary number of motors and drive elements. While the features of the bucket crusher have been described for a bucket crusher having two reciprocable jaws it should be evidence to the skilled person that any of the above features could be included in a bucket crusher with three or more jaws.

A representative diagram of a hydraulic drive circuit 134 of the bucket crusher 10 is shown in Figure 9. The arrowed lines show the direction of transport of the hydraulic fluid. The first and second motor 28a, 28b are connected in a parallel hydraulic drive circuit 134. The hydraulic drive circuit 134 may be connected to existing hydraulic systems, such as a hydraulic system of an excavator or of a wheel loader. A pump (not shown) serves to pump the hydraulic fluid through the circuit 134.

A control valve 136 can be used to shut the hydraulic fluid off from the hydraulic drive circuit 134, or to adjust the pressure and flow rate through the hydraulic drive circuit 134 by varying the size of the flow passage.

The hydraulic fluid flows to each of the first motor 28a and the first motor 28b to drive the motors 28a, 28b, allowing for operation the first and second eccentric crankshafts 84a, 84b of the bucket crusher 10 respectively. Should one of the reciprocable jaws 18a, 18b jam due to a piece of material which is too hard to be crushed being lodged between the said reciprocable jaw and the crusher surface 14 or malfunctions, fluid will be unable to flow through the motor 28a, 28b corresponding to said stuck jaw 18a, 18b. In this case, the pressure and flow rate through the other motor 28a, 28b will increase, increasing the power and crushing capabilities of the other reciprocable jaw 18a, 18b. In a bucket crusher 10 which operates with a single reciprocable jaw 18a, 18b only, the jaw 18a, 18b jamming or malfunctioning can cause a pressure build-up which can damage the motor or other components connected to the hydraulic drive circuit 134, most notably the pump. This issue is alleviated by the present invention because the fluid has an additional means to flow, preventing pressure build-up if one of the reciprocable jaws 18a, 18b jams.

The hydraulic drive circuit 134 may comprise hydraulic circuit components to mediate the flow through the hydraulic drive circuit 134. For example, a hydraulic manifold may be included in the hydraulic drive circuit 134, which could regulate fluid flow to each of the motors 28a, 28b. This allows the user control over the operation of each of the reciprocable jaws 18a, 18b by providing the option of an uneven split of hydraulic fluid to each motors 28a, 28b. For example, the hydraulic manifold may be used to send a greater proportion of the inputted hydraulic fluid to the first motor 28a than the first motor 28b, which would lead to an increase in the operating power of the first reciprocable jaw 18a and a decrease in the operating power of the second reciprocable jaw 18b. In many cases, the material to be crushed is not homogenous, and has uneven hardness. If the material in the first crushing zone 22a is harder than the material in the second crushing zone 22a, the user may for example alter the hydraulic flow accordingly to provide the first reciprocable jaw 18a more power.

The hydraulic drive circuit 134 may be configured to allow the two motors 28a, 28b to be to rotate in opposite directions, which means the reciprocable jaws 18a, 18b are able to operate in opposite directions, i.e. while one of the reciprocable jaws 18a, 18b moves towards the crusher surface, the other moves away from the crusher surface. In the ideal case wherein a phase between the two reciprocable jaws 18a, 18b remains the same, the stress on the bucket crusher 10 is reduced, as only one of the reciprocable jaws 18a, 18b is crushing material at a time.

Furthermore, a direction of rotation of each of the first motor 28a and the first motor 28b may be reversible, such that the direction of operation of the reciprocable jaws 18a, 18b are also reversible. This is particularly useful for helping to remove jammed material between the reciprocable jaws 18a, 18b and the crusher surface 14.

While the hydraulic drive circuit has been described with respect to two motors, any number of hydraulic motors could be connected in a parallel hydraulic drive circuit. In that case, one or more of the hydraulic motors jamming or otherwise malfunctioning would lead to increased flow and pressure through each of the remaining, non-jammed motors.

Although the bucket crusher may operate in place if connected to a suitable hydraulic system, the bucket crusher is primarily intended for use with heavy machinery, preferably an excavator or a wheel loader. To this end, the bucket crusher may include separate attachment means for a wheel loader and excavator arm respectively, as the different methods of operation of an excavator and wheel loader mean that different mounting locations are preferred.

A bucket crusher 10 included in a vehicle such as an excavator or wheel loader provides an extremely mobile means to crush material, allowing the bucket crusher 10 to be moved to the site at which material is to be processed. This eliminates the need for separate diggers or power shovels, which are needed to transport material if stationary crushers are used, reducing the amount of equipment and personnel needed on site.

For the preferred operation of the bucket crusher 10 to crush material, the bucket crusher 10 is first mounted to the arm of an excavator or to a wheel loader, via included attachment means such as, for example, the attachment bar 24 located at the rear of the bucket crusher 10, or an attachment bracket mounted to the support plates 54a, 54b of the bucket crusher 10. The bucket crusher 10 is provided with a first and second motor 28a, 28b, which are separately connected to the first and second reciprocable jaws 18a, 18b, so that the jaws 18a, 18b can be driven separately by the motors 28a, 28b.

The first and second motors 28a, 28b are connected in parallel to a hydraulic drive circuit 134. This parallel arrangement of motors 28a, 28b means that if either one of the first or second reciprocable jaws 18a, 18b jams, fluid no longer flows through the motor driving the reciprocable jaw 18a, 18b which has jammed, increasing the fluid flow rate and pressure through the remaining hydraulic motor. This means that the remaining reciprocable jaw 18a, 18b receives an increased driving force, increasing the crushing capabilities of that reciprocable jaw 18a, 18b.

The hydraulic drive circuit 134 is then connected to the existing hydraulic systems of the excavator or the wheel loader. Fluid flow through the circuit 134 is provided by the pump included in an excavator or wheel loader, which is typically driven by a diesel engine included in the vehicle. The bucket crusher 10 may be operated to scoop in material using an excavator, similarly to how an excavator bucket is operated. The method of operation of the bucket crusher 10 is slightly different when attached to a wheel loader, being operated usually by placing the bucket crusher 10 against the ground and then moving it forwards and away from the vehicle to scoop up and lift material.

Material to be crushed enters the bucket crusher 10 via the scooping motion through the inlet 56 of the hopper 12. The user may then use the wheel loader or excavator to position the bucket crusher 10 so that the outlet 58 of the hopper 12 is lower than the inlet 56 of the hopper 12, such that gravity assists in moving material from the inlet 56 to the outlet 58. The motors 28a, 28b can then be activated via the hydraulic drive circuit 134, to drive the reciprocable jaws 18a, 18b in a reciprocating motion, crushing material between the crusher surface 14 and the reciprocable jaws 18a, 18b. Preferably, the first and second crushing zones 22a, 22b taper from the inlet 56 towards the outlet 58 of the hopper 12, allowing for progressive crushing of material to smaller and smaller sizes as it progresses through the crushing zones 22a, 22b. The crushed material is then discharged from the bucket crusher 10 through the outlet 58 of the hopper 12.

In some cases, the user may be able to individually operate the first and second motors 28a, 28b via the hydraulic drive circuit 134, which may be useful if the material in one crushing zone is harder than the other, or if there is more material in one crushing zone than the other, which may occur if, for example, the bucket crusher 10 is tilted to one side.

In the event of one of the reciprocable jaws 18a, 18b jamming, the other reciprocable jaw 18a, 18b can still be operated by the user. The user could account for the reciprocable jaw 18a, 18b being jammed, for example by tilting the bucket crusher 10 sideways such that helps to move the material to be crushed into the crushing zone with the unjammed reciprocable jaw 18a, 18b. This allows the bucket crusher 10 to be effectively operated even if a reciprocable jaw 18a, 18b jams, especially because the remaining jaw 18a, 18b is provided with an increased driving force.

Preferably, the user is able to reverse the direction of rotation of each of the motors 28a, 28b. If one or both of the reciprocable jaws 18a, 18b jam, for example due to a hard piece of material stuck between a reciprocable jaw 18a, 18b and the crusher surface 14, the user could reverse the direction of the motors 28a, 28b, lifting the jammed jaw 18a, 18b away from the crusher surface 14 and allowing the piece of material to be removed. The user could position the bucket crusher 10 so that the inlet 56 is lower than the outlet 58 before reversing the direction of the motors 28a, 28b, so that when the reciprocable jaw 18a, 18b moves away from the crusher surface 14, the piece of material that was jammed between the crusher surface 14 and the reciprocable jaw 18a, 18b can fall out of the bucket crusher 10 due to gravity.

The material to be crushed may include any debris from construction processes including but not limited to debris comprised of concrete, bricks, glass, stone, or any combination thereof, and also may include raw material to be processed such as, but not limited to, ore, coal, soil, rough stone, or any combination thereof. It is appreciated that this is a non-exhaustive list of crushable materials.

The bucket crusher 10 is particularly well suited for the crushing of high volume, low hardness materials due to the much larger width of the hopper 12 allowing a greater throughput of these materials when compared to typical bucket crushers 10. This includes materials such as, to provide a non-exhaustive list of examples, glass, coal, and concrete up to M30 grade.

It is worth noting that “eccentric drive output” can be taken generally to include any mechanical component capable of converting the rotational motion produced by each of the motors into a reciprocating motion or substantially reciprocable motion, to allow the reciprocable jaws to operate. Therefore, while the bucket crusher has been described as operating with an eccentric crankshaft it is possible for the reciprocating motion of the reciprocable jaws to be provided by alternative means, such as for example a Scotch yoke mechanism or a Swashplate mechanism.

Preferably, the position of each of the first reciprocable jaw and the second reciprocable jaw is adjustable relative to the crusher surface, so as to adjust the volume of the material to be crushed and the size of the outputted crushed material. This may be achieved by adjusting the position to which the first and/or the second reciprocable jaw is indirectly attached to the first and/or second side walls of the hopper. Furthermore, such adjustment can be apply only to one of the reciprocable jaws such that the reciprocable jaws are not coplanar with each other, even when not in use.

Although preferably the bucket crusher is provided with a first stationary jaw and second stationary jaw mounted to the inner surface of the base wall of the hopper, the first and second stationary jaws defining the crusher surface, it will be appreciated that the crusher surface may be defined by or on the inner surface of the base wall of the hopper itself. For example, the first and second stationary jaws may be integrally formed with the base wall, or teeth may be attached to or integrally formed on the inner surface, to define the crusher surface. Furthermore, the crusher surface may not be complimentarily shaped with the first and second reciprocable jaws or vice versa. The crusher surface may be a planar or substantially planer surface for material to abut against and be crushed, or may be uneven with repeated or random undulations.

Whilst spacers are preferably provided to prevent undesirable movement of the jaw bearing elements on the eccentric crankshaft other means maybe provided to locate the jaw bearing elements thereon such that the spacers may be dispensed with. For example, a non-cylindrical locator may be provided. Alternatively, spacers may be dispensed with altogether if the attachment of the jaw bearing element to the crankshaft and/or to the reciprocable jaw adequately secure.

Although the base wall of the hopper is preferably provided with three separate base wall portions it will be appreciated that a greater or fewer number of such portions may be provided. Various alterations may also be made to simplify manufacture of the base wall. For example, two or more of the base wall portions, may be integrally formed without any gaps therebetween. Furthermore, the length of the base wall portions may be the same or different. The base wall portions may be coplanar or substantially coplanar with their respective adjacent wall portions. The crusher surface may be defined by more than the rear base wall portion and may further include the intermediate base wall portion, for example.

The words ‘comprises/comprising’ and the words ‘having/including’ when used herein with reference to the present invention are used to specify the presence of stated features, integers, steps, or components, but do not preclude the presence or addition of one or more other features, integers, steps, components, or groups thereof.

It is appreciated that certain features of the invention, which are, for clarity, described in the context of separate embodiments, may also be provided in combination in a single embodiment. Conversely, various features of the invention which are, for brevity, described in the context of a single embodiment, may also be provided separately or in any suitable sub-combination.

The embodiments described above are provided by way of examples only, and various other modifications will be apparent to persons skilled in the field without departing from the scope of the invention as defined herein.

Claims

1. A bucket crusher (10) comprising: a hopper (12); a crusher surface at or on an inner surface (16) of the hopper (12); a first drive element (26a) having a first eccentric drive output, the first drive element (26a) being drivable by a first motor (28a); a second drive element (26b) having a second eccentric drive output, and the second drive element (26b) being drivable by a second motor (28b) separately of the first motor (28a); a first reciprocable jaw (18a) which is opposed to the crusher surface to define a first crushing zone (22a), the first reciprocable jaw (18a) being drivable by the first eccentric drive output; a second reciprocable jaw (18b) which is opposed to the crusher surface to define a second crushing zone (22b), the second reciprocable jaw (18b) being drivable by the second eccentric drive output.

2. A bucket crusher (10) as claimed in claim 1 , wherein each of the first motor (28a) and the second motor (28b) is a hydraulic motor.

3. A bucket crusher (10) as claimed in claim 2, wherein the first motor (28a) and the second motor (28b) are connected in a parallel hydraulic drive circuit (134).

4. A bucket crusher (10) as claimed in any one of the preceding claims, wherein the first motor (28a) and the second motor (28b) are configured to rotate in opposite directions.

5. A bucket crusher (10) as claimed in any one of the preceding claims, wherein a direction of rotation of each of the first motor (28a) and the second motor (28b) is reversible.

6. A bucket crusher (10) as claimed in any one of the preceding claims, wherein the hopper (12) includes an inlet (56) for intaking material to be crushed and an outlet (58) for the expulsion of crushed material.

7. A bucket crusher (10) as claimed in claim 6, wherein the hopper (12) includes a protruding scooping portion positioned at the inlet (56).

8. A bucket crusher (10) as claimed in claim 6 or claim 7, wherein the first and second crushing zones (22a, 22b) taper towards the outlet (58) of the hopper (12).

9. A bucket crusher (10) as claimed in any one of the preceding claims, wherein a position of each of the first reciprocable jaw (18a) and the second reciprocable jaw (18b) is adjustable relative to the crusher surface (14), so as to adjust a shape of one or both of the crushing zones (22a, 22b).

10. A bucket crusher (10) as claimed in any one of the preceding claims, further comprising a first stationary jaw (20a) mounted to the inner surface (16) of the hopper (12) and a second stationary jaw (20b) mounted to the inner surface (16) of the hopper (12), wherein the first and second stationary jaws (20a, 20b) together define the crusher surface (14) and are opposed to the first and second reciprocable jaws (18a, 18b) respectively.

11. A bucket crusher (10) as claimed in any one of the preceding claims, wherein the first drive element (26a) comprises a first eccentric crankshaft (84a) and the second drive element (26b) comprises a second eccentric crankshaft (84b).

12. A bucket crusher (10) as claimed in claim 11 , wherein the first eccentric crankshaft (84a) is colinear with the second eccentric crankshaft (84b).

13. A bucket crusher (10) as claimed in claim 11 or claim 12, further comprising at least one jaw bearing element upon which the first reciprocable jaw (18a) and/or the second reciprocable jaw (18b) is mountable, and through which the first eccentric crankshaft (84a) and/or the second eccentric crankshaft (84b) are receivable.

14. A bucket crusher (10) as claimed in any one of claims 11 to 13, further comprising at least one crankshaft support (108), the at least one crankshaft support (108) having at least one crankshaft support bearing element (110) within which the first eccentric crankshaft (84a) and/or the second eccentric crankshaft (84b) is receivable.

15. A bucket crusher (10) as claimed in claim 14, further comprising at least one support plate (54a, 54b) engageable with the hopper (12), wherein the at least one crankshaft support (108) is mounted to the support plate (54a, 54b).

16. A bucket crusher (10) as claimed in any one of claims 13 to 15, wherein the at least one jaw bearing element and/or the at least one crankshaft support bearing element (110) is a spherical roller bearing element.

17. A bucket crusher (10) as claimed in any one of claims 11 to 16, further comprising at least one spacer (126, 128) on the first eccentric crankshaft (84a) and/or the second eccentric crankshaft (84b).

18. A bucket crusher (10) as claimed in any one of claims 11 to 17, wherein the first drive element (26a) comprises a first flywheel and the second drive element (26b) comprises a second flywheel, the first and second flywheels being connected to the first eccentric shaft (84a) and the second eccentric shaft (84b) respectively.

19. A bucket crusher (10) as claimed in any one of the preceding claims, wherein the operating power of the first reciprocable jaw (18a) is different to the operating power of the second reciprocable jaw (18b).

20. A bucket crusher (10) as claimed in any one of the preceding claims, wherein three or more reciprocable jaws are provided, the bucket crusher including a complementary number of driving elements and motors.

21. A bucket crusher (10) as claimed in any one of the preceding claims, adapted to be mountable to an excavator or wheel loader.

22. A vehicle comprising a bucket crusher as claimed in any one of the preceding claims.

23. A vehicle as claimed in claim 22, in the form of an excavator or a wheel loader.

24. A method of improving throughput of crushed material using a bucket crusher (10) as claimed in any one of claims 1 to 21 , the method comprising the step of: a] providing at least two separately drivable reciprocable jaws (18a, 18b), so that if the one of the said at least two reciprocable jaws (18a, 18b) jams, the remainder of the said at least two reciprocable jaws (18a, 18b) continue to operate.

25. A method of improving throughput of crushed material using a bucket crusher (10) as claimed in claim 24, further comprising the step of: b] connecting the at least two reciprocable jaws (18a, 18b) to a hydraulic circuit, such that if one of the said at least two reciprocable jaws (18a, 18b) jams, the remainder of the at least two reciprocable jaws (18a, 18b) receive an increased driving force via the hydraulic circuit.