Abstract
A drive mechanism for an inertia cone crusher having a drive transmission to rotate an unbalanced mass body within the crusher and to cause a crusher head to rotate about a gyration axis at a tilt angle formed by an axis of the crusher head relative to the gyration axis. A torque reaction coupling is positioned in the drive transmission between the mass body and a drive input component and is elastically displaceable and/or deformable. In particular, the torque reaction coupling is configured to: i) transmit a torque from the drive input to the mass body and ii) to dynamically displace and/or deform elastically in response to a change in the torque resultant from a change in the tilt angle of the crusher head so as to dissipate the change in the torque to the drive transmission.
Claims
1. A drive mechanism comprising: a drive input component forming part of a drive transmission, wherein the drive input component is arranged to rotate an unbalanced mass body located within an inertia crusher and to cause a crusher head to rotate about a gyration axis; and a torque reaction coupling positioned at the drive transmission between the unbalanced mass body and the drive input component and being elastically displaceable and/or deformable, the torque reaction coupling being configured to: i) transmit a torque from at least part of the drive input component to at least part of the mass body via a drive transmission component which is coupled to the mass body, and ii) to dynamically displace and/or deform elastically in response to a change in the torque resultant from a change in rotational motion of the crusher head about the gyration axis and/or a rotational speed of the crusher head so as to dissipate the change in the torque at the inertia crusher, the torque reaction coupling being a spring selected from a helical spring or a coil spring.
2. The drive mechanism as claimed in claim 1, wherein the crusher head supports an inner crushing shell, the mass body being provided at or connected to the crusher head.
3. The drive mechanism as claimed in claim 2, wherein the mass body is connected to the crusher head via a main shaft or the mass body is integrated at or mounted within the crusher head.
4. The drive mechanism as claimed in claim 1, further comprising at least one further drive transmission component coupled to the mass body and the drive input component to form part of the drive transmission.
5. The drive mechanism as claimed in claim 4, wherein the torque reaction coupling is elastically deformable relative to the drive input component and/or the further drive transmission component.
6. The drive mechanism as claimed in claim 1, wherein the torque reaction coupling includes a torsion bar.
7. The drive mechanism as claimed in claim 1, wherein the spring has a stiffness in the range 100 Nm/degrees to 1500 Nm/degrees and a damping coefficient (Nm.Math.s/degree) of less than 5% of the stiffness.
8. The drive mechanism as claimed in claim 1, wherein the torque reaction coupling includes a first part anchored to the mass body or a component coupled to the mass body and a second part anchored to the drive input component or a coupling forming part of the drive transmission and coupled to the drive input component such that the torque reaction coupling is elastically displaceable and/or deformable in an anchored position between the drive input component and the mass body.
9. The drive mechanism as claimed in claim 1, wherein the torque reaction coupling is configured and mounted in the drive transmission to store the change in the torque and to displace and/or deform relative to the drive input component to inhibit transmission of the change in the torque to at least part of the drive transmission.
10. The drive mechanism as claimed in claim 1, wherein the torque reaction coupling is configured to displace and/or deform in response to the change in the torque due to deviations from a substantially circular motion of the crusher head around the gyration axis.
11. An inertia crusher comprising: a frame arranged to support an outer crushing shell; a crusher head moveably mounted relative to the frame to support an inner crushing shell to define a crushing zone between the outer and inner crushing shells; and a drive mechanism according to claim 1.
12. A method of operating an inertia crusher comprising: inputting a torque to a drive input component at the crusher forming part of a drive transmission; transmitting drive from the drive input component to an unbalanced mass body via a torque reaction coupling to cause a crusher head to rotate about a gyration axis formed by an axis of the crusher head relative to the gyration axis; partitioning the drive transmission between the drive input component and the mass body via an elastically displaceable and/or deformable torque reaction coupling configured to allow the torque to be transmitted from the drive input component to the mass body, the torque reaction coupling being a spring selected from a helical spring or a coil spring; and inhibiting the transmission of a change in the torque resultant from a change in the rotational motion of the crusher head about the gyration axis and/or a rotational speed of the crusher head to at least part of the drive transmission via displacement and/or deformation of the torque reaction coupling.
Description
BRIEF DESCRIPTION OF DRAWINGS
(1) A specific implementation of the present invention will now be described, by way of example only, and with reference to the accompanying drawings in which:
(2) FIG. 1 is a cross-sectional view through an inertia cone crusher according to one specific implementation of the present invention;
(3) FIG. 2 is a schematic side view of selected moving components within the inertia crusher of FIG. 1 including in particular the crushing head, the unbalanced weight and drive transmission;
(4) FIG. 3 is a cross-sectional view of an inertia cone crusher according to a further specific implementation of the present invention;
(5) FIG. 4 is a cross-sectional view of an inertia cone crusher according to a further specific implementation of the present invention;
(6) FIG. 5 is a schematic illustration of a torsion rod forming a part of a drive transmission of the inertia cone crusher of FIG. 4;
(7) FIG. 6 is a cross-sectional view of an inertia cone crusher according to a further specific implementation of the present invention;
(8) FIG. 7 is a perspective cross-sectional view through a drive pulley component of an inertia cone crusher according to a specific implementation of the present invention;
(9) FIG. 8 is a schematic perspective view of a torque reaction coupling mounted about an unbalanced weight of an inertia cone crusher according to a further specific implementation;
(10) FIG. 9 is a schematic illustration of selected components of an inertia cone crusher including a crusher head, unbalanced weight and drive transmission components according to a further specific implementation of the present invention;
(11) FIG. 10 is a further specific implementation of a torque reaction coupling forming part of a drive transmission within an inertia cone crusher;
(12) FIG. 11 is a magnified perspective view of a disc spring part of the torque reaction coupling of FIG. 10;
(13) FIG. 12 is a partial cross-sectional view through an inertia cone crusher with the torque reaction coupling of FIGS. 10 and 11 mounted in position as part of the unbalanced weight according to a specific implementation of a present invention;
(14) FIG. 13 is a schematic perspective view of a further embodiment of the torque reaction coupling forming part of a drive transmission within an inertia cone crusher;
(15) FIG. 14 is a schematic illustration of the torque reaction coupling of FIG. 13 mounted in position within the drive transmission between a crushing head and a drive input component;
(16) FIG. 15 is a schematic illustration of a further implementation of the torque reaction coupling positioned in the drive transmission between an unbalanced weight and a drive component;
(17) FIG. 16 is a further magnified perspective view of the torque reaction coupling of FIG. 15;
(18) FIG. 17A is an exploded view of a further specific implementation of a torque reaction coupling;
(19) FIG. 17B is an assembled view of the specific implementation of a torque reaction coupling of FIG. 17A; and
(20) FIG. 18 is a further specific implementation of a torque reaction coupling mounted in position between selected drive transmission components within an inertia cone crusher.
DETAILED DESCRIPTION OF PREFERRED EMBODIMENT OF THE INVENTION
(21) FIG. 1 illustrates an inertia cone crusher 1 in accordance with one embodiment of the present invention. The inertia crusher 1 comprises a crusher frame 2 in which the various parts of the crusher 1 are mounted. Frame 2 comprises an upper frame portion 4, and a lower frame portion 6. Upper frame portion 4 has the shape of a bowl and is provided with an outer thread 8, which cooperates with an inner thread 10 of lower frame portion 6. Upper frame portion 4 supports, on the inside thereof, a concave 12 which is a wear part and is typically formed from a manganese steel.
(22) Lower frame portion 6 supports an inner crushing shell arrangement represented generally by reference 14. Inner shell arrangement 14 comprises a crushing head 16, having a generally coned shape profile and which supports a mantle 18 that is similarly a wear part and typically formed from a manganese steel. Crushing head 16 is supported on a part-spherical bearing 20, which is supported in turn on an inner cylindrical portion 22 of lower frame portion 6. The concave and mantle 12, 18 form between them a crushing chamber 48, to which material that is to be crushed is supplied from a hopper 46. The discharge opening of the crushing chamber 48, and thereby the crushing capacity, can be adjusted by means of turning the upper frame portion 4, by means of the threads 8,10, such that the vertical distance between the concave and mantle 12, 18 is adjusted. Crusher 1 is suspended on cushions 45 to dampen vibrations occurring during the crushing action.
(23) The crushing head 16 is mounted at or towards an upper end of a main shaft 24. An opposite lower end of shaft 24 is encircled by a bushing 26, which has the form of a cylindrical sleeve. Bushing 26 is provided with an inner cylindrical bearing 28 making it possible for the bushing 26 to rotate relative to the crushing head shaft 24 about an axis S extending through head 16 and shaft 24.
(24) An unbalance weight 30 is mounted eccentrically at (one side of) bushing 26. At its lower end, bushing 26 is connected to the upper end of a drive transmission mechanism indicated generally by reference 55. Drive transmission 55 comprises a torque reaction coupling 32 in the form of a helical spring having a first upper end 33 and a second lower end 34. The first end 33 is connected to a lowermost end of bushing 26 whilst second end 34 is mounted in coupled arrangement with a drive shaft 36 rotatably mounted at frame 6 via a bearing housing 35. A torsion bar 37 is drivably coupled to a lower end of drive shaft 36 via its first upper end 39. A corresponding second lower end 38 of torsion bar 37 is mounted at a drive pulley 42. An upper balanced weight 23 is mounted to an axial upper region of drive coupling 36 and a lower balanced weight 25 is similarly mounted at an axial lower region to drive coupling 36. According to the specific implementation, torque reaction coupling 32, drive shaft 36, bearing housing 35, torsion bar 37 and pulley 42 are aligned coaxially with one another, main shaft 24 and crushing head 16 so as to be centred on axis S. Drive pulley 42 mounts a plurality of drive V-belts 41 extending around a corresponding motor pulley 43. Pulley 43 is driven by a suitable electric motor 44 controlled via a control unit 47 that is configured to control the operation of the crusher 1 and is connected to the motor 44, for controlling the RPM of the motor 44 (and hence its power). A frequency converter, for driving the motor 44, may be connected between the electric power supply line and the motor 44.
(25) According to the specific implementation, drive mechanism 55 comprises four CV joints at the regions of the respective mounting ends 33 and 34 of the torque reaction coupling 32 and the respective ends 39, 38 of the torsion bar 37. Accordingly, the rotational drive of the pulley 42 by motor 44 is translated to bushing 26 and ultimately unbalanced weight 30 via drive transmission components 32, 36, 37 coupled to pulley 42 which may be regarded as a drive input component of crusher 1. Pulley 42 is centred on a generally vertically extended central axis C of crusher 1 that is aligned coaxially with shaft and head axis S when the crusher 1 is stationary.
(26) When the crusher 1 is operative, the drive transmission components 32, 36, 37 and 42 are rotated by motor 44 to induce rotation of bushing 26. Accordingly, bushing 26 swings radially outward in the direction of the unbalance weight 30, displacing the unbalance weight 30 away from crusher vertical reference axis C in response to the centrifugal force to which the unbalance weight 30 is exposed. Such displacement of the unbalance weight 30, and bushing 26 (to which the unbalance weight 30 is attached), is achieved due to the flexibility of the CV joints at the various regions of drive transmission 55. Additionally, the desired radial displacement of weight 30 is accommodated as the sleeve-shaped bushing 26 is configured to slide axially on the main shaft 24 via cylindrical bearing 28. The combined rotation and swinging of the unbalance weight 30 results in an inclination of the main shaft 24, and causes head and shaft axis S to gyrate about the vertical reference axis C as illustrated in FIG. 2 such that material within crushing chamber 48 is crushed between the concave and mantle 12, 18. Accordingly, under normal operating conditions, a gyration axis G, about which crushing head 16 and shaft 24 will gyrate, coincides with the vertical reference axis C.
(27) FIG. 2 illustrates the gyrating motion of the central axis S of the shaft 24 and head 16 about the gyration axis G during normal operation of the crusher 1. For reasons of clarity, only the rotating parts are illustrated schematically. As the drive shaft 36 rotates the torque reaction coupling 32 and the unbalance bushing 26, the unbalance weight 30 swings radially outward thereby tilting the central axis S of the crushing head 16 and the shaft 24 relative to the vertical reference axis C by an inclination angle i. As the tilted central axis S is rotated by the drive shaft 36, it will follow a gyrating motion about the gyration axis G, the central axis S thereby acting as a generatrix generating two cones meeting at an apex 13. A tilt angle α, formed at the apex 13 by the central axis S of head 16 and the gyration axis G, will vary depending on the mass of the unbalance weight 30, the RPM at which the unbalance weight 30 is rotated, the type and amount of material that is to be crushed, the DO setting and the shape profile of the concave and mantle 18, 12. For example, the faster the drive shaft 36 rotates, the more the unbalance weight 30 will tilt the central axis S of the head 16 and the shaft 24. Under the normal operating conditions illustrated in FIG. 2, the instantaneous inclination angle i of the head 16 relative to the vertical axis C coincides with the apex tilt angle α of the gyrating motion. In particular, when the drive transmission components 33, 36, 37 and 42 are rotated the unbalanced weight 30 is rotated such that the crushing head 16 gyrates against the material to be crushed within the crushing chamber 48. As the crushing head 16 rolls against the material at a distance from the periphery of the concave 12, central axis S of crushing head 16, about which axis the crushing head 16 rotates, will follow a circular path about the gyration axis G. Under normal operating conditions the gyration axis G coincides with the vertical reference axis C. During a complete revolution, the central axis S of the crushing head 16 passes from 0-360°, at a uniform speed, and at a static distance from the vertical reference axis C.
(28) However, the desired circular gyroscopic precession of head 16 about axis C is regularly disrupted due to many factors including for example the type, volume and non-uniform delivery speed of material within the crushing chamber 48. Additionally, asymmetric shape variation of the concave and mantle 12, 18 acts to deflect axis S (and hence the head 16 and unbalanced weight 30) from the intended inclined tilt angle i. Sudden changes from the intended rotational path of the main shaft relative to axis G and/or sudden changes in the angular velocity (referred to herein as speed) of the unbalanced weight 30 manifest as substantial exaggerated dynamic torsional changes that are transmitted into the drive transmission components 32, 36, 37 and 42. Such dynamic torque can result in accelerated wear, fatigue and failure of the drive transmission 55 and indeed other components of the crusher 1.
(29) Torque reaction coupling 32, according to the specific embodiment, functions like an elastic spring that is configured to deform elastically in response to receipt of the dynamic torque resultant from the undesired and uncontrolled movement and speed of unbalanced weight 30. In particular, spring 32 is adapted to be self-adjusting via radial and axial expansion and contraction as torque is transmitted from a bearing race (mounted at an axial lower end 31 of bushing 26) to spring upper end 33 and then spring lower end 34. Accordingly, the reaction torque resultant from the exaggerated motion of unbalanced weight 30 is dissipated by coupling 32 and is inhibited and indeed prevented from transmission to the remaining drive transmission components 36, 37 and 42. Torque reaction component 32 is configured to receive, store and at least partially return torque to the bushing 26 and unbalanced weight 30. Accordingly, unbalanced weight 30 via coupling 32 is suspended in a ‘floating’ arrangement relative to the remaining drive transmission components 36, 37 and 42. That is, coupling 32 enables a predetermined amount of change in the tilt angle i of weight 30 in addition to changes in the angular velocity of weight 30 relative to the corresponding rotational drive of components 36, 37 and 42
(30) FIG. 3 illustrates a further embodiment in which the drive transmission 55 comprises an axially upper torsion bar 50 connected at its upper end 51 to bushing 26 and at its lower end 52 to drive shaft 36. The torque reaction coupling 32 in the form of a spring is effectively mounted to replace the lower torsion bar of FIG. 1 and is mounted axially in position between a lower end of drive shaft 36 and drive pulley 42. Accordingly, a drive torque from motor 44 is transmitted to the crusher via drive pulley 42, torque reaction coupling 32, drive shaft 36, upper torsion bar 50, bushing 26 and ultimately to unbalanced weight 30. As detailed with reference to FIG. 1, the torque reaction coupling 32 (positioned at a low region of the drive transmission) is configured to move by elastic deformation to dissipate the reaction torque generated by unbalanced mass 30.
(31) FIG. 4 illustrates a further embodiment according to a variation of the embodiment of FIG. 1. A torsion rod indicated generally by reference 53 represents the torque reaction coupling 32. Torsion rod 53 is positioned axially between bushing 26 and the drive shaft 36. In particular, a first axial upper end of torsion rod 53 is mounted via a rigid mounting 15 to bushing 26. An axial lower end of rod 53 is similarly mounted via a rigid mount 49 to drive shaft 36. Torsion rod 53 comprises a plurality of concentrically mounted tubes each configured to twist about an axis of the rod 53 in response to the reaction torque generated by unbalanced mass 30. Rod 53 comprises a first radially outer tube 54, a centrally positioned radially innermost rod or tube 59 and an intermediate tube 58 positioned between the innermost and outer components 59, 54. The respective components 54, 59 and 58 are coupled together at their respective axial ends via a first axially upper assembly mount 56 and a second axially lower assembly mount 57.
(32) Accordingly, each of the torsion components 54, 59, 58 are connected to one another at their respective ends in series so as to transmit drive torque from drive shaft 36 to bushing 26 and reaction torque from unbalanced weight 30 to drive shaft 36. When transmitting the drive, the force transmission pathway from drive shaft 36 extends into the radially innermost rod or tube 59, into the intermediate tube 58, then into the radially outer tube 54 and then into the bushing 26 via mount 15. FIG. 5 illustrates schematically the configuration of torsion rod 53 configured to twist between the axial end mounts 56, 57 such that the axial structure of the torsion rod 53 adopts a helical twisted profile indicated generally by reference 60.
(33) FIG. 6 illustrates a variation on the embodiment of FIGS. 4 and 5 that comprises a corresponding modular torsion rod indicated generally by reference 53 accommodated within an elongate bore 62 extending axially within main shaft 24. Bore 62 extends between a bearing race 86 (mounted at shaft end 31) that receives the axial upper end of the upper torsion rod 50 to an axial region of shaft 24 about which head 16 is mounted.
(34) Like the embodiment of FIGS. 4 and 5, torsion rod 53 comprises an outer tube 63 and a corresponding coaxial inner tube 64 with both tubes 63, 64 connected via their respective upper and lower ends via mounts 61 and 65. A mounting 66 connects outer tube 63 to the unbalanced weight 30 whilst lower mounting 65 connects the inner tube 64 to the bearing race 86. Accordingly, both the drive and opposed reaction torque are transmitted through torsion rod 53 along the axial length of each tube 63, 64 with each tube configured to twist elastically as illustrated in FIG. 5. Accordingly, torsion rod 53 comprises a sufficient stiffness to transmit the drive torque whilst comprising a torsional flexibility to receive the reaction torque and to deform within bore 62.
(35) A further embodiment of the torque reaction coupling is described with reference to FIG. 7 in which the drive pulley 42 of FIG. 1 is modified to include a resiliently deformable component 32. In particular, pulley 42 comprises a radially outermost grooved race 69 around which extend V-belts 41. A radially inner race 67 defines a socket 68 to receive the lower end 38 of lower torsion bar 37. An inner bearing assembly, comprising bearings 70 and bearing raceways 71, is mounted radially outside inner race 67 and secured in position via an upper mounting disc 73 and a lower mounting disc 74. An adaptor shaft indicated generally by reference 81 comprises a radially outward extending axially upper cup portion 84 non-moveably attached to a lower region 83 of inner race 67. Adaptor shaft 81 also comprises a radially outward extending flange 85 provided at a lowermost end of shaft 81. An outer bearing assembly, comprising bearings 88 and bearing raceways 87, is positioned radially between the grooved radially outer race 69 and a bearing housing 72 that is positioned radially between the two bearings assemblies 87, 88 and 70, 71. Accordingly, the outer grooved race 69 is capable of independent rotation relative to the inner race 67 via the respective bearing assemblies 70, 71 and 87, 88.
(36) The flexible torsion coupling 32 is positioned in the drive transmission pathway between the grooved pulley race 69 and the inner race 67 via adaptor shaft 81. According to the specific implementation, coupling 32 comprises a modular assembly formed from deformable elastomeric rings and a set of intermediate metal disc springs. In particular, a first annular upper elastomer ring 78 mounts at its lowermost annular face a first half of a disc spring 79. A corresponding second lower annular elastomer ring 77 similarly mounts at its upper annular face a second half of the disc spring 80 to form an axially stacked assembly in which the metal disc spring 79, 80 separates respective upper and lower elastomeric rings 78, 77. A first upper annular metal flange 76 is mounted at an upper annular face of the upper elastomer ring 78 and a corresponding second lower metal flange 89 is attached to a corresponding axially lower face of the lower elastomer ring 77. Upper flange 76 is attached at its radially outer perimeter to a first upper adaptor flange 75 formed from an elastomer material. Flange 75 is secured at its radially outer perimeter to a lower annular face of the grooved belt race 69. Accordingly, adaptor flange 75 and coupling flange 76 provide one half of a mechanical coupling between the grooved V belt race 69 and the flexible coupling 32. Similarly, a second lower adaptor flange 82, also formed from an elastomer material, is mounted to the lower coupling flange 89 at a radially outer region and is mounted to adaptor shaft flange 85 at a radially inner region. Accordingly, adaptor flange 82 provides a second half of the mechanical connection between flexible coupling 32 and inner face 67 (via adaptor shaft 81). Each of the elastomeric components 75, 78, 77, 82 are configured to elastically deform in response to torsional loading in a first rotational direction due to the drive torque and in the opposed rotational direction by the reaction torque. Lower adaptor flange 82 is specifically configured physical and mechanical to be stiffer in torsion relative to components 77, 78, 75 but to be deformable axially so as to provide axial freedom and to allow components 78, 77 to flex in response to the torque loading.
(37) Flexible coupling 32 is demountably interchangeable at pulley 42 via a set of releasable connections. In particular, upper coupling flange 76 is releasably mounted to adaptor flange 75 via attachments 97 (such as bolts) and lower coupling flange 89 is releasably attached to adaptor flange 82 via corresponding attachments (not shown). Additionally, lower adaptor flange 82 is releasably attached to the adaptor shaft flange 85 via releasable attachment bolts 98. According to further embodiments, adaptor shaft end portion 84 is demountable attached to race lower end region 83 to allow the interchange of different configurations of shaft 81.
(38) In the mounted position at pulley 42, the elastomeric components 78, 77, 75, 82 in addition to the metal disc spring 79, 80 are configured to deform radially and axially via twisting and axial and radial compression and expansion in response to the driving and reaction torques. Coupling 32, as with the embodiments of FIGS. 1 to 6, is accordingly configured to dissipate the undesired reaction torque created by the change in the tilt angle α and the non-circular orbiting motion of the unbalanced weight 30. In particular, coupling 32 is configured specifically to absorb these torques and inhibit onward transmission to the drive components, in this example, the readily outer grooved V-belt race 69.
(39) A further implementation of a flexible elastic torsion transmission coupling is described with reference to FIG. 8 in the form of a coil or clock spring indicated generally by reference 90. According to the specific implementation, spring 90 comprises a rectangular cross-sectional shape profile and is formed from an elongate metal strip coiled into a circular spiral having a first end 91 and a second end 92 with each end 91, 92 overlapping one another in the circumferential direction. As will be appreciated, the coil spring 90 may comprise one single circular turn or may comprise a plurality of spiral turns each extending through 360°. Spring 90 is positioned radially outside unbalanced weight 30 at the region of an axial upper end 51 of an upper torsion bar 50. In particular, spring first end 91 is secured via a rigid connection 94 to a region of unbalanced weight 30 and spring second end 92 is secured via a rigid connection 93 to torsion bar 50. Accordingly, spring 90 is positioned in the drive transmission pathway between unbalanced weight 30 and upper torsion bar 50. As such, spring 90 is configured to dynamically coil and uncoil in response to both the driving torque from a drive pulley and a reaction torque created by the motion of unbalanced weight 30.
(40) Referring to FIG. 9, a further embodiment of the flexible torsional response coupling 32 is described in the form of a helical spring 32 mounted axially between upper and lower torsion bars 50, 37. In particular, a first axially upper end 137 of spring 32 is rigidly mounted to a first CV bushing 95 that mounts and rotationally supports an axially lower end 52 of upper torsion bar 50. A corresponding second lower axial end 114 of spring 32 is rigidly attached to a second CV bushing 96 that mounts and rotationally supports an axial upper end 39 of lower torsion bar 37. The respective upper end 51 of upper torsion bar 50 is attached to shaft bushing 26 at described with reference to FIG. 3 and the axial lower end 38 of lower torsion bar 37 is mounted to pulley 42 as described with reference to FIG. 1. Accordingly, spring 32 provides the torsional elastic deformation characteristic to inhibit transmission of the reaction torque from the motion of unbalanced weight 30 into the lower drive components 37 and 42. As with all of the embodiments described herein, the unbalanced weight 30 via deformable coupling 32 may be considered to be held in a ‘floating’ relationship relative to at least some of the drive transmission components to provide a degree of independent rotational movement between unbalanced weight 30 and selected components of the drive transmission 55.
(41) A further specific implementation is described with reference to FIGS. 10 to 12. According to the further embodiment, torque reaction coupling 32 is implemented as a torsional disc spring mounted between the unbalanced weight 30 and the bearing race 86 (illustrated in FIG. 6) that mounts and rotationally supports the axial upper end 51 of upper torsion bar 50. A torsion disc spring 32 is formed integrally with the unbalanced weight 30 and is configured to sit within a stack of generally annular unbalanced weight segments. In particular, one segment 106 of the unbalanced weight 30, corresponding to an axially lowermost segment of the stack (that is positioned in contact with a movement sensing plate 107) is adapted to at least partially accommodate the torsional disc spring 32. Segments 106 is annular and comprises bore 108 for mounting about bushing 26. Referring to FIG. 12, the spring indicated generally by reference 105 is positioned between the upper and lower faces 112, 113 of weight segment 106. A circumferentially extending groove 101 is recessed into upper face 112 of weight segment 106 and at least partially mounts an arcuate slider axle 100. A plurality of annular disc spring segments are slidably mounted on axle 100 between its first and second ends. Each segment comprises a pair of annular discs or rings 109, 110 connected at their radially outermost perimeters and aligned transverse to one another so as to be capable of hinging about their combined annular perimeter junction 139. A radially inner end 147 of each ring 109, 110 is attached to a respective slider ring 111 slidably mounted over axle 100. Accordingly, each segment comprising rings 109, 110 is capable of compressing and expanding in the axial direction of axle 100. A first stopper 102 and second stopper 103 are mounted about axle 100 at the respective ends 148, 148 of disc spring 105. Each stopper 102, 103 is connected to the unbalanced weight 30. A torsional input coupling 104 is mounted at spring second end 149 such that spring 105 is configured to compress and expand axially along axle 100 in response to the reaction torque as described herein. Additional bearing surfaces 138 at the axially lower region of bushing 26 further assist with the transmission of axial loads at the region of the torsion spring 105.
(42) According to a further embodiment of FIGS. 13 and 14, torque reaction coupling 32 is implemented as an assembly of axial compression springs positioned between the unbalanced weight 30 and an upper torsional bar 50. The spring assembly comprises a set of slider compression spring arrangements distributed radially outside the upper torsion bar 50. Each slider arrangement comprises an axle 119 that slidably mounts a spring guide 118 configured for linear movement along axle 119. A helical spring 116 extends axially around axle 119 and is positioned to extend between guide 118 (mounted at one end of axle 119) and a spring holder 117 (mounted at an opposite end of axle 119). Accordingly, each helical spring 116 is sandwiched between guide 118 and holder 117. Each holder 117 is secured to torsion bar 50 via link arm 115 and the flexible coupling is secured to the unbalanced weight 30 via the guides 118. Accordingly, the drive and reaction torques may be transmitted through the spring assembly such that non-circular motion of weight 30 about the gyration axis G forces each guide 118 to slide along axle 119 with the motion being controlled by the linear compression and extension of each respective spring 116. Accordingly, exaggerated dynamic torsion is transmitted into the spring arrangement where they are dissipated and inhibited from onward transmission into the upper torsion bar 50.
(43) FIGS. 15 and 16 illustrate a further implementation of the dynamically reactive coupling 32 in a form of an air spring indicated generally by reference 121. According to the specific implementation, air spring 121 is integrated within the unbalanced weight 30 in a similar manner to that described for the embodiment of FIGS. 10 to 12. In the specific implementation, air spring 121 comprises an internal chamber defined by a housing having a first end 127 and a second end 128. The internal chamber similarly comprises a first end 124 and a second end 125 that are partitioned by a slider plate 126 extending across the internal chamber. Accordingly, the internal chamber is divided into a first chamber 122 and second chamber 123 either side of slider plate 126 in between the respective ends 124, 125. A rigid connection mounting 120 extends from slider plate 126 and is attached to an upper torsion bar 50. Housing second end 128 is attached to a region of the unbalanced weight 30. Accordingly, in response to torsion transmitted to the air spring 121 from the undesired deflected motion of unbalanced weight 30, the slider plate 126 is configured to slide between chamber ends 124, 125. A fluid within one or both chamber halves 122, 123 is forced to compress (or expand) in response to the sliding of plate 126 so as to provide the elastic deformation and torsional reaction. Accordingly, air spring 121 via the choice of fluid, pressure and/or volume of the fluid within chamber halves 122, 123 may be single or dual acting in response to the reaction torques transmitted respectively into the coupling 121 from the non-circular orbiting motion of unbalanced weight 30.
(44) Referring to FIGS. 17A and B, the torque reaction coupling 32 may in one implementation be represented as a camming joint at the region of an upper torsion rod 50. In particular, rod 50 is divided into at least two axial segments including a lower segment 131 and an upper segment 130. Lower segment 131 comprises an upward facing camming surface 132 and upper segment 130 comprises a corresponding downward facing camming surface 136 opposed to the camming surface 132 of the lower segment 131. A spring 133 is positioned to extend between and axially couple the respective camming surfaces 132, 136 and is attached at its first and second ends 134, 135 to the respective axial segments 131, 130 of torsion bar 50. Accordingly, the camming and spring assembly provides a flexible joint to dissipate the exaggerated torsion resulting from the motion of unbalanced weight 30 as the camming surfaces 132, 136 are forced towards one another. In particular, spring 133 compresses or expands due to differences in torsion between the upper and lower segments 130, 131 of the torsional bar 50 so as to bias together the two segments 130, 131. According to the specific implementation camming surfaces 136, 132 each comprise a ‘wave’ type profile extending in the circumferential direction at one end of a short cylindrical wall segment that, in part, defines each of the respective upper and lower segments 130, 131.
(45) The torsional responsive coupling 32 is described according to a further embodiment with reference to FIG. 18. Coupling 32 is positioned towards an axially lower region of the drive transmission 55 between a lower torsion bar 37 and a drive pulley 42. Being similar to the embodiment of FIG. 7, coupling 32 comprises a modular assembly construction having first and second elastomeric rings 140, 143 secured between respective upper and lower mounting plates 141, 142. A metal disc spring 146 partitions the upper and lower elastomeric rings 140, 143 and is configured to allow a degree of independent rotational motion of rings 140, 143 resulting from torque induced by the motion of unbalanced weight 30. Lower plate 142 is mounted at its radially inner region 144 to a radially outward extending flange 145 projecting from bearing housing 72 as described with reference to FIG. 7. Similarly, a radially inner region 144 of upper plate 141 is coupled to a radially outward extending flange 150 projecting from an upper region of inner race 67 that supports lower torsion rod 37 as described with reference to FIG. 7. Accordingly, drive and reaction torque is transmitted between bearing housing 72 and inner race 67 via flexible coupling 32. Accordingly, the undesirable reaction torque is dissipated dynamically by the rotational twisting of elastomer rings 140, 143 and the movement of the intermediate disc spring 146.
(46) As will be appreciated, the specific embodiments of FIGS. 1 to 18 are example implementations of an elastically deformable torsion response coupling positioned between a part of the drive transmission 55 and the unbalanced weight 30. In particular, according to further embodiments, torsion transmission coupling 32 may provide a direct couple between pulley 42 and bushing 26 according to the embodiment of FIG. 1 that would obviate the need for drive shaft 36 and lower torsion bar 37. Similarly and by way of example only, the coil spring embodiment of FIG. 8 may be implemented at a position directly between unbalanced weight 30 (or bushing 26) and upper torsion bar 50.
(47) In preferred embodiments, coupling 32 is positioned in the drive transmission pathway closer to the unbalanced weight 30 (or bushing 26) relative to pulley 42. Such a configuration is advantageous to dissipate the reaction torque closer to source and to isolate all or most of the drive transmission components 55 from large excessive torsions. However, positioning the coupling 32 towards the lower region of crusher 1 at or close to drive pulley 42 is advantageous for installation, servicing and maintenance of wear parts. In particular, the embodiment of FIG. 7 is advantageous to allow convenient interchange of different configurations of flexible coupling 32 at the axially lower region of pulley 42 to suit crushing material and desired operating parameters that may affect the magnitude and frequency of the reaction torque.
