Gyratory crusher main shaft sleeve

Abstract

A gyratory crusher main shaft sleeve friction fit over an uppermost end of a crusher main shaft. The sleeve includes an elongate axial wall for being positioned in contact with an outward facing surface of the main shaft. The axial wall has a thickness that decreases in a direction from a second upper end to a first lower end, wherein the internal facing surface of the sleeve extends transverse to a longitudinal axis of the sleeve so as to taper inwardly towards the axis in a direction from the first to the second end.

Claims

1. A gyratory crusher comprising: a main shaft including a shaft body having a first end for positioning at a lower region of the crusher and a second end for positioning at an upper region of the crusher relative to the first end, a thickness of the shaft body being tapered in an axial direction of the main shaft at a region of the second end so as to decrease in cross-sectional area; and a sleeve fitted over the tapered region at the second end of the main shaft, the sleeve including an elongate axial wall extending around a longitudinal axis of the sleeve, the axial wall having an internal facing surface for positioning in contact with an outward facing surface of the main shaft, and an external facing surface relative to the longitudinal axis, the axial wall extending between the internal and external facing surfaces, the axial wall having a first end for positioning at a lower region of the main shaft and a second end for positioning at an upper region of the main shaft relative to the lower region, wherein a thickness of the axial wall at a region between the first and second ends decreases in a direction from the second end to the first end, in the axial direction the internal facing surface at said region between the first and second ends extending transverse to the longitudinal axis so as to taper inwardly towards the longitudinal axis in the direction from the first to the second end.

2. The gyratory crusher as claimed in claim 1, wherein the region over which the thickness of the axial wall decreases extends substantially the full axial length of the sleeve.

3. The gyratory crusher as claimed in claim 1, further comprising a radial wall extending perpendicular or transverse to the axial wall, the radial wall being positioned at or towards the second end and extending inwardly towards the longitudinal axis.

4. The gyratory crusher as claimed in claim 3, wherein the radial wall includes a through bore positioned at the longitudinal axis of the sleeve.

5. The gyratory crusher as claimed in claim 1, wherein a cross-sectional shape profile of the external facing surface is substantially circular.

6. The gyratory crusher as claimed in claim 1, wherein a cross-sectional shape profile of the internal facing surface is substantially circular.

7. The gyratory crusher as claimed in claim 1, wherein a shape profile of the external facing surface defines a section of a cylinder in the axial direction.

8. The gyratory crusher as claimed in claim 1, wherein a shape profile of the internal facing surface defines a section of a cone in the axial direction.

9. The gyratory crusher as claimed in claim 1, further comprising at least one bore provided through the axial wall to allow the passage of a fluid to the internal facing surface.

10. The gyratory crusher as claimed in claim 1, wherein at a curved region of the first end, the internal facing surface is curved radially outward relative to the longitudinal axis in a direction towards the external facing surface such that the axial wall thickness decreases to zero at the curved region.

Description

BRIEF DESCRIPTION OF DRAWINGS

(1) A specific implementation of the present invention will now be described by way example only and with reference to the following drawings in which:

(2) FIG. 1 is a cross-sectional side view of a gyratory crusher having a main shaft supported at its upper end by a top bearing set and having a protective sleeve mounted about the upper end of the main shaft according to a specific implementation of the present invention;

(3) FIG. 2 is a magnified view of the upper region of the crusher of FIG. 1.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENT OF THE INVENTION

(4) Referring to FIG. 1, a crusher comprises a frame 100 having an upper frame 101 and a lower frame 102. A crushing head 103 is mounted upon an elongate shaft 107. A first crushing shell 105 is fixably mounted on crushing head 103 and a second crushing shell 106 is fixably mounted at top frame 101. A crushing zone 104 is formed between the opposed crushing shells 105, 106. A discharge zone 109 is positioned immediately below crushing zone 104 and is defined, in part, by lower frame 102.

(5) Upper frame 101 is further divided into a topshell 111, mounted upon lower frame 102 (alternatively termed a bottom shell), and a spider that extends from topshell 111 and represents an upper portion of the crusher. The spider comprises two diametrically opposed arms 110 that extend radially outward from a central cap positioned on a longitudinal axis 115 extending through frame 100 and the gyratory crusher generally.

(6) Arms 110 are attached to an upper region of topshell 111 via an intermediate annular flange that is centred around longitudinal axis 115. Typically, arms 110 and topshell 111 form a unitary structure and are formed integrally.

(7) A drive (not shown) is coupled to main shaft 107 via a drive shaft 108 and suitable gearing 116 so as to rotate shaft 107 eccentrically about longitudinal axis 115 and to cause crushing head 103 to perform a gyratory pendulum movement and crush material introduced into crushing gap 104. An upper end region of a shaft 113 comprises an axial taper to define an upper conical section. The cone 113 tapers inwardly in the bottom to top direction away from head 103. A very uppermost end 117 of shaft 107 is maintained in an axially rotatable position by a top bearing assembly 112. Similarly, a bottom end 118 of shaft 107 is supported by a bottom bearing assembly 119.

(8) To avoid excessive wear of the upper conical portion 113, a substantially cylindrical wear sleeve 114 is mounted over and about shaft region 113. Sleeve 114 is held in position at region 113 by an interference of friction fit and is provided in close touching contact over the axial length of sleeve 114. Accordingly, sleeve 114 is positioned intermediate between bearing assembly 112 and region 113 to absorb the radial and axial loading forces resultant from the crushing action of the gyratory pendulum movement.

(9) With reference to FIG. 2, sleeve 114 comprises an external facing surface 201 and an internal facing surface 200, the orientation of faces 201, 200 being relative to the longitudinal axis 115 extending through shaft region 113 and sleeve 114. Internal facing surface 200 is secured in direct contact against an external facing surface 202 of conical region 113. Accordingly, internal facing surface 200 tapers inwardly towards longitudinal axis 115 from a first end 207 and a second end 208, where the first end 207 is positioned below second end 208 within the crusher during normal use. A cross sectional shape profile of internal facing surface 200 and external facing surface 201 is circular substantially the length of sleeve 114 between first and second ends 207, 208. However, external facing surface 201 is aligned substantially parallel with axis 115 such that sleeve 114 when viewed externally comprises a substantially cylindrical geometry. According to this configuration, the annular axial wall 209 of sleeve 114 that is defined between apposed surfaces 200, 201 comprises a thickness that tapers and reduces in a direction from second upper end 208 to first lower end 207. As will be appreciated, to enable sleeve 114 to fit in close shrink-fit contact with conical end portion 113, the taper angle of inner surface 200 is substantially equal to the taper angle of the external facing surface 202 of shaft region 113 relative to axis 115.

(10) At first end 207, a thickness of walls 209 decrease sharply as internal facing surface 200 curves outwardly 204 forwards external facing surface 201. This curved or sharp annular edge region 204 is configured to fit in close contact against a shoulder region 205 of shaft 107 that curves radially outward at a region immediately above crushing shell 105 and head 103.

(11) Uppermost end 117 of shaft 107 is retained in position by a mounting pin 206, aligned at axis 115, that extends axially downward from a mounting boss 207. Boss 207 and pin 206 are positioned coaxially with shaft end 113 and sleeve 114.

(12) A radial wall 203 extends perpendicular to axial wall 209 and is orientated inwardly towards axis 115 at second end 208. A bore 210 is provided through radial wall 203 of a diameter sufficient to accommodate boss 207 such that wall 203 extends around boss 207 from axial wall 209. Accordingly, sleeve 114 is fully mated in position over conical shaft region 113 when radial wall 203 is seated against shaft end 117. In this configuration, axial wall 209 is positioned intermediate between top bearing 112 and shaft region 113.

(13) According to the specific implementation, the axial wall 209 comprises a thickness that decreases from second end 208 to first end 207 uniformly over the entire length of sleeve 114 with the exception of curved end region 204.