Inertia cone crusher with a journal plain bearing

Abstract

Inertia cone crusher for crushing materials includes a body with an outer cone and an inner cone arranged inside, on whose drive shaft an unbalance weight is provided with the aid of a slide bushing and connected via a transmission disk coupling to a combined moving dynamic assembly comprising a counterbalance weight and a counterbalance weight slide bushing, the assembly connected to a gear transmission and a motor, and has an improved plain journal bearing. The plain bearing is installed between the flange and the counterbalance weight, bearing the load from the crusher's moving part, and includes a base ring and an upper ring, the base ring having a spherical bottom surface and its mating recess on the flange's top surface. The bearing enables the moving dynamic assembly's rotation around the axis, using a hydrodynamic sliding mode, with radial oil slots additionally provided on top surface of the base ring.

Claims

1. An inertia cone crusher comprising: a body resting on a foundation over resilient dampers; an outer cone and an inner cone arranged inside the body on a spherical support, the outer cone and the inner cone forming a crushing chamber in between, the crushing chamber being connected to the finished product discharge area, an unbalance weight mounted upon the drive shaft of the inner cone using an unbalance weight slide bushing, the unbalance weight having a center of gravity that is adjustable relative to an axis of rotation, the unbalance weight slide bushing being connected to a transmission disk coupling that includes a driving half-coupling, a driven half-coupling, and a floating disk arranged between them, the transmission disk coupling being connected to a tooth gear and a counterbalance weight, both being installed upon a counterbalance weight slide bushing, such that the tooth gear, the counterbalance weight, and the counterbalance weight slide bushing form a moving dynamic assembly, the dynamic assembly being mounted on a fixed pivot resting on a flange, and rotatable around the fixed pivot via a journal plain bearing, wherein the flange is rigidly fixed in a bottom part of the body; wherein the journal plain bearing is arranged between the flange and the counterbalance weight, and includes a base ring resting on the flange and an upper ring supporting the counterbalance weight slide bushing and the counterbalance weight; an inner radius of the base ring being equal to an inner diameter of the upper ring and to an inner radius of the unbalance weight bushing, and being equal to or greater than the fixed pivot's outer radius; and a top surface of the flange has a mating recess for installing the base ring.

2. The crusher of claim 1, wherein the base ring has a flat top surface and a spherical bottom surface, and the mating recess has a spherical shape for coupling to the base ring.

3. The crusher of claim 1, wherein the upper ring has a flat top surface and a flat bottom surface, and an annular shoulder along a top outer edge.

4. The crusher of claim 3, further comprising an annular groove on a bottom surface of the counterbalance weight, on a side of a larger segment of its disk, that mates to the annular shoulder of the upper ring, and wherein, on a side of a smaller segment of the disk, its outer radius is equal to or smaller than an inner radius of the annular shoulder.

5. The crusher of claim 1, wherein an inner radius of the base ring is equal to the inner radius of the upper ring.

6. The crusher of claim 1, wherein an outer radius of the base ring is equal to an outer radius of the upper ring.

7. The crusher of claim 1, wherein a total thickness of the base ring and upper ring that together form the plain bearing is such that there will always be a sufficient guaranteed clearance of a predetermined minimum height h between the counterbalance weight and the flange.

8. The crusher of claim 1, further comprising radially arranged oil slots on a top surface of the base ring.

Description

BRIEF DESCRIPTION OF THE ATTACHED FIGURES

[0041] 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.

[0042] In the drawings:

[0043] FIG. 1 shows the diagram of a cone crusher as a cross-sectional view.

[0044] FIG. 2 presents a “dynamic assembly” and the crusher components coupled with it.

[0045] FIG. 3 presents a journal plain bearing as assembled.

DETAILED DESCRIPTION OF EMBODIMENTS OF THE INVENTION

[0046] Reference will now be made in detail to the preferred embodiments of the present invention, examples of which are illustrated in the accompanying drawings.

[0047] Body 1 of the cone crusher is mounted upon foundation 9 over resilient dampers 10. Outer crushing cone 2 and inner crushing cone 3, which is mounted upon head center 15, form a crushing chamber between them. Head center 15 rests on spherical support 4. Installed on shaft 5 of head center 15 are unbalance weight's slide bushing 12 and unbalance weight 6. The bushing is rigidly connected to transmission coupling 13, FIG. 1.

[0048] Transmission coupling 13 consists of driving half-coupling 25, driven half-coupling 16, and floating disk 17 arranged between them; the coupling design is shown in detail in FIG. 2.

[0049] Unbalance weight's slide bushing 12 has mounting holes along the rim edge, with the aid of which is its rigidly connected to driven half-coupling 16 via its mounting holes with mounting bolts 26.

[0050] Driving half-coupling 25 has mounting holes, via which it is rigidly connected with gear 22 via mounting holes along the edges of its central mounting hole and simultaneously with counterbalance weight 11 with mounting bolts 19.

[0051] Counterbalance weight 11 is shaped as a disk segment, at the center of which is a mounting hole equal to the outer radius of slide bushing 14. Along the edge of the central mounting hole of counterbalance weight 11 are fastening surfaces of the disk of counterbalance weight 11, with a recess provided to mate the mounting fasteners of flange 24.

[0052] Driving half-coupling 25, tooth gear 22 and counterbalance weight 11 are mounted upon counterbalance weight's slide bushing 14, forming one body of rotation with it.

[0053] Thus, driving half-coupling 25, gear 22, counterbalance weight 11, and slide bushing 14 form one moving “dynamic assembly,” all of whose components are rigidly connected to each other.

[0054] The “dynamic assembly” is installed on fixed pivot 23 and flange 24 via journal plain bearing 27, 28 as assembled, enabling the assembly's rotation around pivot 23, for which purpose, slide bushing 14 is mounted on pivot 23.

[0055] A recess is provided on the bottom surface of driving half-coupling 25, whose outer radius is equal to the outer radius of bushing 14.

[0056] The pain journal bearing consists of upper ring 28 and base ring 27, see FIG. 3. Upper ring 28 has a flat top surface and a flat bottom surface, and annular shoulder 30 along the outer top edge.

[0057] On the bottom surface of counterbalance weight 11, on the side of the disk's larger segment, is annular groove 18 mating shoulder 30.

[0058] On the side of the smaller segment of the disk of counterbalance weight 11, the disk's outer radius is designed to be equal or smaller than the inner radius of shoulder 30.

[0059] Base ring 27 has a flat top surface and a spherical bottom surface. Flange 24 has a mating spherical recess on its top surface to install base ring 27, Note B, FIG. 2.

[0060] The radius of inner holes of base ring 27 and upper ring 28 are made equal. The outer radius of pivot 23 is made smaller than the plain bearing's inner radius by the size of the clearance necessary and sufficient for free rotation of the bearing around pivot 23.

[0061] Pivot 23 rests on flange 24 rigidly fixed in the bottom part of body 1 with mounting bolts.

[0062] Pivot 23 and flange 24 may be designed either as two different parts rigidly connected to each other or as one integral part acting as a fixed bearing support for the “dynamic assembly.”

[0063] The moving “dynamic assembly” is installed so that unbalance weight 6 is always opposite in phase to counterbalance weight 11.

[0064] Thus, journal bearing 27, 28 as assembled is installed between the moving “dynamic assembly” and fixed flange 24, bearing the load of the entire “dynamic assembly,” transmission assembly, and unbalance weight vibrator.

[0065] Counterbalance weight 11 is designed and arranged so as to provide its minimum clearances with body 1 and flange 24, enabling the maximum use of the body space without increasing its dimensions.

[0066] Tooth gear 22 is engaged with drive gear shaft 21 installed in body 20 of the gear shaft connected to a motor (not shown in the figures).

[0067] The invention works as follows.

[0068] The torque from the motor is transmitted to drive gear shaft 21 and to the tooth gear 22. Along with gear 22, the entire “dynamic assembly” is set into rotation, comprising also counterbalance weight slide bushing 14, counterbalance weight 11, and driving half-coupling 27 of transmission coupling 13. Thus, the “dynamic assembly” rotates around fixed pivot 23 and flange 24 resting on journal plain bearing 28, 27 as assembled.

[0069] The spherical shape of the bottom surface of base ring 27 and the spherical shape of its mating recess on the top surface of flange 24 serve the bearing self-adjustment and self-alignment in relation to the crusher's center axis of rotation 7 in the initial assembling of this assembly of the crusher.

[0070] Shoulder 30 of upper ring 28 serves to align the journal bearing in relation to counterbalance weight 11 and to the crusher's center axis of rotation 7.

[0071] Since all the moving parts rotate around a common axis, it is important that the axes of rotation of all moving parts of the “dynamic assembly” and the axis of rotation of journal plain bearing 27, 28 coincide with the crusher's central pivot.

[0072] The total thickness of the journal bearing 28, 27 as assembled is calculated so that there will always be a sufficient guaranteed clearance of the minimum height h between moving counterbalance weight 11 and fixed flange 24, as shown in Note A, FIG. 2.

[0073] Thus, parts 11 and 24 do not contact each other, therefore there is no friction between the parts.

[0074] Between pivot 23 and bushing 14 is a clearance necessary and sufficient for free rotation of bushing 14 and related “dynamic assembly” around pivot 23.

[0075] Oil under pressure is supplied via an oil duct 8 to the crusher's inner cavities. For additional lubrication of parts of journal bearing 27, 28, and especially for oil lubrication of the interface of the top surface of base ring 27 and bottom surface of upper ring 28, with radial oil slots 29 provided on the upper surface of base ring 27. Via the slots 29, oil goes from the friction cavity between pivot 23 and bushing 14 to the outer perimeter of the plain bearing.

[0076] The present design of journal plain bearing 28, 27 is intended to reduce specific loads occurring in the rotation of the “dynamic assembly” by increasing the contact area. Loads are also reduced by the oil wedge formed between the bearing's rings with oil supplied under pressure and distributed among radial slots. A favorable operating mode of the bearing is provided due to the generated “hydrodynamic sliding” mode.

[0077] The spherical bottom surface of the base ring enables using the self-adjustment, or self-alignment, effect in the assembling of the crusher structure.

[0078] 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.