Inertial cone crusher with an upgraded drive

Abstract

A cone crusher includes body installed on foundation with resilient dampers and having an outer cone and an inner cone. Unbalance weight is on the drive shaft of inner cone using a slide bushing, with center of gravity adjustable relative to rotation axis, slide damper of unbalance weight connected to transmission coupler, through which torque is transmitted. Transmission coupler is a disc coupler comprising a drive half-coupler, a driven half-coupler, and a floating disc between them. The driven half-coupler is rigidly connected to slide bushing, and the drive half-coupler, to gear rigidly connected to counterbalance weight. The drive half-coupler, gear and counterbalance weight are mounted on the slide bushing, and driving half-coupler, gear, counterbalance weight, and the slide bushing form one movable dynamic assembly, installed using a mounting disc, on fixed rotation axis, which rests upon flange rigidly fixed in the bottom part of body of the crusher.

Claims

1. An inertial cone crusher comprising: a body with an outer cone resting upon a foundation via resilient dampers, and an inner cone arranged inside the outer cone on a spherical support, on whose drive shaft an unbalance weight is arranged using a first slide bushing, wherein a center of gravity of the unbalance weight is adjustable relative to a rotation axis, wherein the unbalance weight includes the first slide bushing connected to a transmission coupler, wherein torque from an engine is transmitted through the transmission coupler, and wherein the transmission coupler is a disc coupler including a driving half-coupler, a driven half-coupler, and a floating disc arranged between them, wherein the driven half-coupler is rigidly connected to the first slide bushing, and the driving half-coupler is rigidly connected to a gear, and wherein the gear is rigidly connected to a counterbalance weight, with the driving half-coupler, the gear, and the counterbalance weight installed on a second slide bushing so that the driving half-coupler, the gear, the counterbalance weight, and the second slide bushing form a single dynamic assembly, wherein the dynamic assembly is mounted, via a mounting disc, on the rotation axis resting on a flange, while the flange is rigidly fixed in a bottom part of the body.

2. The inertial cone crusher of claim 1, wherein the transmission coupler comprises: a driving half-coupler shaped as a disc and connected to the gear via the mounting disc, wherein the driving half-coupler has a concave working end surface and concave geometry of a first dowel pin arranged radially on the driving half-coupler; a driven half-coupler shaped as a disc and connected to the first slide bushing, the driven half-coupler having a convex working end surface and convex geometry of a second dowel pin arranged radially on the driven half-coupler; and a floating disc arranged between the half-couplers and having a convex end surface facing the driving half-coupler and convex geometry of a first groove provided radially on the convex end surface, a concave end surface facing the driven half-coupler, and concave geometry of a second groove provided radially on the concave end surface and perpendicular to the first groove.

3. The inertial cone crusher of claim 1, wherein the driving half-coupler and the driven half-coupler and the floating disc have round oil holes arranged at the centers of the respective discs, the oil hole of the floating disc having a larger diameter than the oil holes in the driving and driven half-couplers.

4. The inertial cone crusher of claim 3, wherein the first and second dowel pins are provided with a thinning above the oil holes.

5. The inertial cone crusher of claim 3, wherein the first and second dowel pins have gaps in the middle above the oil holes.

6. The inertial cone crusher of claim 1, wherein the floating disc has oil duct grooves arranged on both disc surfaces and provided as radial fillets and a circular fillet.

7. The inertial cone crusher of claim 1, wherein a diameter of the driving half-coupler is larger than a diameter of the driven half-coupler and larger than a diameter of the floating disc.

8. The inertial cone crusher of claim 1, wherein the driving half-coupler has mounting holes along its disc perimeter coinciding with the mounting holes along an inner rim of a gear wheel, and coinciding with the mounting holes around an inner mounting hole of the counterbalance weight.

9. The inertial cone crusher of claim 8, wherein the driven half-coupler has mounting holes along the disc perimeter coinciding with the mounting holes along an edge of the first slide bushing.

10. The inertial cone crusher of claim 1, wherein concavity and convexity radii of mating end surfaces of the coupler discs are equal, centers of all the radii are arranged at one point coinciding with a center of a curvature radius of the inner surface of the spherical support of the inner cone.

11. The inertial cone crusher of claim 1, wherein the counterbalance weight is shaped as a disc segment, with a mounting hole at its center equal to an external diameter of the slide bushing, with mounting holes provided at its edges, an upper surface of the disc having two rectangular reducing shoulders and a lower surface of the disc having a conical shoulder to match the flange's mounting fasteners.

12. The inertial cone crusher of claim 11, wherein the counterbalance weight has two locator end flats.

13. The inertial cone crusher of claim 1, wherein the mounting disc is a thin disc with an oil hole at its center.

14. The inertial cone crusher of claim 1, wherein the rotation axis is a cylinder with an oil hole at its center and a round recess in an upper end of a diameter equal to a diameter of the mounting disc.

15. The inertial cone crusher of claim 1, wherein the flange is a disc with a center hole of a diameter equal to an external diameter of the rotation axis, and has mounting holes at disc edges.

16. The inertial cone crusher of claim 1, wherein the rotation axis and the flange are provided as a single integral piece.

17. The inertial cone crusher of claim 1, wherein the rotation of the dynamic assembly and transmission coupler may be directed any direction.

18. An inertial cone crusher comprising: an outer cone coupled to a foundation via resilient dampers; an inner cone inside the outer cone on a spherical support, the inner cone including a drive shaft; and an unbalance weight mounted on the drive shaft using a first slide bushing, wherein a center of gravity of the unbalance weight is adjustable relative to a rotation axis, wherein the first slide bushing is connected to a disc coupler, wherein the disc coupler includes a driving half-coupler, a driven half-coupler, and a floating disc between them, wherein the driven half-coupler is rigidly connected to the first slide bushing, and the driving half-coupler is rigidly connected to a gear, wherein the gear is rigidly connected to a counterbalance weight, with the driving half-coupler, the gear, and the counterbalance weight installed on a second slide bushing forming a single dynamic assembly, and wherein the dynamic assembly is mounted, via a mounting disc, on the rotation axis resting on a flange, while the flange is rigidly fixed in a bottom part of the inertial crusher.

19. An inertial cone crusher comprising: an outer cone coupled to a foundation via resilient dampers; an inner cone inside the outer cone on a spherical support, the inner cone including a drive shaft; and an unbalance weight mounted on the drive shaft using a first slide bushing, wherein a center of gravity of the unbalance weight is adjustable relative to a rotation axis; a disc coupler connected to the first slide bushing, wherein the disc coupler includes a driving half-coupler, a driven half-coupler, and a floating disc between them, wherein the driven half-coupler is rigidly connected to the first slide bushing; a gear rigidly connected to the driving half-coupler and to a counterbalance weight; and the driving half-coupler, the gear, and the counterbalance weight forming a single dynamic assembly, wherein the dynamic assembly is mounted, via a mounting disc, on the rotation axis that rests on a flange.

Description

BRIEF DESCRIPTION OF THE ATTACHED FIGURES

(1) The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the principles of the invention.

(2) In the drawings:

(3) FIG. 1 shows the cross-sectional diagram of the inertial cone crusher.

(4) FIGS. 2 and 3 show the dynamic assembly and the crusher components mating to it.

(5) FIGS. 4 and 5 show an embodiment of the transmission coupler and counterbalance weight.

(6) FIG. 6 shows the dynamic assembly as assembled, in one-fourth cutaway isometric view.

(7) FIG. 7 shows the dynamic assembly in its operating position.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

(8) Reference will now be made in detail to the preferred embodiments of the present invention, examples of which are illustrated in the accompanying drawings.

(9) The invention may be structurally embodied as follows, see FIG. 1:

(10) Body 1 is installed upon foundation 9 via resilient dampers 10. Outer crushing cone 2 and inner crushing cone 3 mounted upon supporting cone 15 form a crushing chamber between them. The supporting cone 15 rests on spherical support 4. An unbalance weight slide bushing 12 and unbalance weight 6 are installed on shaft 5 of the supporting cone 15. The bushing is rigidly connected to transmission coupler 13.

(11) The transmission coupler 13 comprises driving half-coupler 27 and driven half-coupler 32 and floating disc 30, whose design is presented in detail in FIGS. 2 and 3. Driving the half-coupler 27 is a disc with a concave working end surface 39, on which concave dowel pin 38 is provided; oil hole 28 is at the center of the disc, and mounting holes 40 are arranged along the disc periphery. The reverse end surface of the disc has a recess whose diameter is equal to the diameter of mounting disc 25.

(12) The driven half-coupler 32 is a disc with convex working end surface 46, where a convex pin 35 is arranged, an oil hole 34 is at the center of the disc, and mounting holes 33 are arranged along the disc periphery. The reverse end surface of the disc has a bulge whose diameter is equal to the inner diameter of the unbalance weight slide bushing 12. The floating disc 30 has convex end surface 45 facing the driving half-coupler 27, and the convex geometry of groove 29 arranged thereon; the concave end surface 30 facing the driven half-coupler 32, and a concave geometry of groove 31 provided thereon, and oil hole 36 at the center of the disc. Grooves 29 and 31 are arranged perpendicular to each other. The floating disc 30 has oil duct grooves on both disc surfaces and provided as four radial fillets and one circular fillet.

(13) The half-couplers 27 and 32 and the floating disc 30 mate each other with their concave-convex end surfaces so that the half-couplers' dowel pins should tightly enter the respective grooves of the floating disc: the pin 38 enters the groove 29, and the pin 35 enters the groove 31. The oil holes are arranged above each other, the oil hole of floating disc 36 is of a greater diameter than the oil holes 28 and 34 in the half-couplers. The half-couplers' pins may be made separate, with a break above the oil holes (FIGS. 2 and 3) or one-piece with a thinning at the center, in way of the oil holes (FIGS. 4 and 5). On the one hand, one-piece pins provide a greater pin-groove engagement area, thus providing a higher reliability at a higher torque, but on the other hand, they partially overlap the oil holes.

(14) The unbalance weight slide bushing 12 has mounting holes 47 at the rim edge, with the aid of which it is rigidly connected to the driven half-coupler 32 via its mounting holes 33 with fastening bolts 49.

(15) The driving half-coupler 27 has mounting holes 40, with the aid of which it is rigidly connected to the gear 22 via the mounting holes 26 at the edges of its central mounting hole, and to the counterbalance weight 11 via mounting holes 42 with the fastening bolts 41. Simultaneously, the parts 27, 22 and 11 are tightly fitted on the bushing 14 making one body of rotation with it.

(16) Thus, the driving half-coupler 27, gear 22, the counterbalance weight 11 and the bushing 14 form a movable dynamic assembly, all the components of which are rigidly connected to each other.

(17) The dynamic assembly is mounted on a fixed rotation axis 23 via the mounting disc 25 rotatable about it, for which purpose the bushing 14 is put on the rotation axis 23, a round recess equal to the diameter of the mounting disc 25 is provided on the top end of the rotation axis 23, and a recess equal to the outer diameter of the bushing 14 is provided on the driving half-coupler 27.

(18) Thus, the mounting disc 25 is arranged between the upper end of the rotation axis 23 and the driving half-coupler 27, serving as a plain journal bearing for the entire dynamic assembly. The rotation axis 23 rests upon the flange 24, which is rigidly fixed in the bottom part of the body 1 with the aid of mounting holes 44 and fastening bolts. The rotation axis 23 and the flange 24 may be provided as two different parts rigidly connected to each other, or as a one-piece part serving as a fixed bearing support for the dynamic assembly.

(19) An advantage of the one-piece solution of the support is a considerable improvement of the part's strength characteristics, since the axis and the flange receive a heavy dynamic load. A drawback of the solution is a higher cost of manufacturing of a complex integral part and of its installation. The movable dynamic assembly is mounted so that the unbalance weight 6 should always be in phase opposition to the counterbalance weight 11.

(20) The counterbalance weight 11 is made as a disc segment, with the mounting hole 16 equal to the outer diameter of the slide bushing 14 at its center. Arranged at the central mounting hole 16 of the counterbalance weight 11 are the mounting holes 42 intended for building a dynamic assembly. Provided on the top surface of the disc are two rectangular reducing shoulders to suit the inner surface pattern of the body 1. Provided on the bottom surface of the disc is a conical reducing shoulder to suit the surface pattern and locator fasteners of the flange 24 (FIGS. 4 and 5).

(21) The counterbalance weight 11 may additionally have two locator end flats 17 (FIGS. 2 and 3) arranged on both sides of the disc and intended to facilitate installation of the counterbalance weight in the body when the required design diameter of the counterbalance weight disc is larger than the mounting apertures of the body of this standard size of the unit.

(22) The complex shape of the counterbalance weight 11 is dictated by the compromise between the design of the inner profile of the body 1, or in other words, by the free space allocated for its accommodation, and characteristics of the counterbalance weight proper required to solve the problem of dynamic balance of the crusher. The counterbalance weight 11 is designed and arranged so that its gaps to the body 1 and the flange 24 should be minimal, which enables utilizing the body's space to the maximum without increasing the dimensions. The gear 22 engages the drive pinion shaft 21 mounted in the body 20 of the pinion shaft and connected to the engine (not shown in the figures).

(23) The invention works as follows.

(24) Torque is transmitted from the engine to the drive pinion shaft 21 and to the gear 22. Together with the gear 22 the entire dynamic assembly is set in rotation, comprising also the slide bushing 14, the counterbalance weight 11 and the drive half-coupler 27 of the transmission coupler 13. Thus, the dynamic assembly rotates about fixed the rotation axis 23. The drive half-coupler 27 transmits torque to the floating disc 37 and the driven half-coupler 32 due to the pin-groove engagements. The driven half-coupler 32 transmits torque to the slide bushing of the unbalance weight 12 and to the counterbalance weight 6. The latter develops a centrifugal force, and via the shaft 5 makes the inner cone 3 roll on the outer cone 2 over a layer of material to be crushed. If the rotation axis 24 and the shaft 5 are arranged strictly on one centerline, the floating disc 37 carries out simple rotational motion repeating it after the drive half-coupler 27 and transmitting rotation to the driven half-coupler 32.

(25) In the crusher's operating mode, the axis 24 and the shaft 5 have an angular difference of rotation axes shown in FIG. 7; in this case, the floating disc 37 receives torque from the driving half-coupler 27 and carries out complex movement of rotation-sliding-swinging because the disc 37 proper rotates about its axis, the pins 38 and 35 slide in their respective grooves 29 and 31, and mating pairs of disc end surfaces 39, 45 and 30, 46 swing due to their concave-convex geometry. The operating angle of deflection of the axes is in the range of 0 to 5. The mating concave-convex end surfaces of the coupler discs tightly abut each other, since the curvature radiuses of the mating surfaces 39 and 45 are equal and the curvature radiuses of the mating surfaces 30 and 46 are equal, therefore the slide and swivel movement of the coupler discs creates no gap.

(26) All the curvature radiuses of the mating surfaces are plotted from the same point as the curvature radius center of the inner surface of the spherical support 4 of the inner cone 3. Thus, the radius of the concave end surface 39 of the driving half-coupler 27 is greater than the radius of the convex end surface 46 of the driven half-coupler 32, which in turn is greater than the radius of the concave inner surface of the spherical support 4 of the inner cone 3. One-piece pins 18 and 48 of the half-couplers with a thinning at the center, in way of the oil holes (FIGS. 4 and 5), on the one hand, provide a greater pin-groove engagement area, thus providing a higher reliability at a higher torque, but on the other hand they partially overlap the oil holes. Therefore as an alternative, the half-couplers' dowels may be separate, with a break above the oil holes (FIGS. 2 and 3).

(27) The design of components of the dynamic assembly, and counterbalance weight 11 in particular, is calculated so that the center of gravity of its unbalanced mass should be positioned strictly at the center of the vertical generator line of the slide bushing 14. In this case, during the dynamic assembly's rotation, the load on the slide bushing 14 is distributed uniformly, thus, there is no load imbalance; thus, the wear of surfaces of the slide bushing 14 and the rotation axis 23 is uniform, and therefore the parts serve longer. All friction surfaces of the coupler need lubrication. Via oil tube 8, oil is fed under pressure to an oil duct 7 of the rotation axis 23, and then to mounting disc 25 via its oil hole 43. Next, oil goes to the transmission coupler 13 via oil holes 28, 36 and 34 of the coupler discs; and via the friction surfaces of the mounting disc 25 to the surfaces between the slide bushing 14 and the rotation axis 23. The diameter of the oil hole 36 of the floating disc 37 is of a size exceeding the oil holes 28 and 34, and such that at any operating angle of deflection of the floating disc 37 and the driven half-coupler 32 from the vertical axis, the oil holes are not overlapped and oil access to all mating surfaces of the coupler is retained.

(28) If the transmission coupler is designed with one-piece dowel pins with a thinning (FIGS. 4 and 5), the ratios of dimensions of the oil holes and thinnings of the dowel pins are such that at any operating angle of deflection the holes do not overlap and oil access to all mating surfaces of the coupler is retained.

(29) The oil ducts of the floating disc additionally help to distribute oil among the coupler's mating surfaces, which is especially efficient at high-speed engine operation.

(30) The rotation of the dynamic assembly may be directed any way. The rotation of the transmission coupler may be directed any way. The transmission coupler and dynamic assembly claimed in this invention have several considerable advantages compared to the use of a bearing and compensation ball coupler traditional for crushers, and conventional counterbalance designs.

(31) First, the design of the claimed dynamic assembly is much simpler.

(32) The central transmission link of the transmission coupler is a simple floating disc with curved end surfaces and two grooves, while a bearing and compensation ball coupler has a dumb-bell support spindle of a complex design as the transmission link, with six recess-ball pairs arranged simultaneously on both sides. The half-couplers used in the claimed coupler are simple discs with curved end surfaces and radially arranged dowel pins, while the bearing and compensation ball coupler has half-couplers shaped as complex hollow cylinders with a bottom and with semi-cylindrical grooves provided on their inner surface and precisely oriented at the recess-ball pairs.

(33) Second, the design of the claimed dynamic assembly is much more reliable.

(34) The pin-groove structural mating can withstand greater loads for longer periods than the groove-ball-recess linking. Thus, the transmission coupler can work longer transmitting a higher torque without risk of emergency breakdown, and therefore a more powerful drive engine can be used with the same performances of the crushing unit.

(35) Grouping several key parts of the machine into one dynamic assembly also enhances reliability and strength. Thus, the same crusher unit provided with the claimed dynamic assembly can operate in a wider range of outputs and loads, which makes it a more universal machine.

(36) Thirdly, the claimed dynamic assembly allows to reduce the crusher's height.

(37) The vertical dimension of the claimed coupler is smaller than the vertical dimension of the bearing and compensation ball coupler by about one half, therefore the structural section of the crusher body allocated for the transmission subassembly is proportionally smaller. The design of a counterbalance weight strictly fitted in its allocated body space, and absence of a counterbalance weight arranged outside the body also influence the height of the unit. The dynamic assembly design is compact and enables combining solutions to several problems at once in one assembly.

(38) The implementation of this invention will make the entire crusher unit lower by about 20 percent of the initial height.

(39) Fourth, the proposed dynamic assembly will allow to cut down the crusher's price.

(40) The production cost of the transmission coupler, due to its design simplicity, is considerably lower than the cost of a traditional coupler; the cost saving from simplified installation and a lower body should also be considered. As a result, the total cost of the crusher unit may be reduced by about 5-10 percent.

(41) Fifth, the proposed dynamic assembly allows a reduction of the crusher's service costs.

(42) All the parts of the transmission coupler and the dynamic assembly can easily be separated and replaced irrespective of each other, without disassembling other parts of the machine, which is guaranteed by a simple technique of coupler discs attachment to the load-bearing parts of the unit. The coupler status and wear degree can be visually monitored through an inspection hole in a side of the body. Thus, the claimed coupler requires facilitated maintenance, which is much less costly and more convenient in field conditions. The area below the crusher body level is made free of the counterbalance weight assembly and of other driving elements, so that there is no need to expand the unloading chute area, and no need to provide bottom access for maintenance: for the claimed design, maintenance is from above only, which is more practical. The overall saving on the unit maintenance costs may reach up to 10 percent depending on the version selected.

(43) Sixth, the proposed designs of the transmission coupler and dynamic assembly are universal and may be used in an inertial cone crusher of any standard size, from small laboratory units to large quarry machines.

(44) Having thus described a preferred embodiment, it should be apparent to those skilled in the art that certain advantages of the described method and apparatus have been achieved. It should also be appreciated that various modifications, adaptations, and alternative embodiments thereof may be made within the scope and spirit of the present invention. The invention is further defined by the following claims.