ZA200908510B

ZA200908510B - Gyratory cone crusher

Info

Publication number: ZA200908510B
Application number: ZA2009/08510A
Authority: ZA
Inventors: Andrei Nikolaevich Safronov; Leonid Petrovich Zarogatsky
Original assignee: Sarathan Invest Cc
Priority date: 2008-09-01
Filing date: 2009-12-01
Publication date: 2010-11-24

Description

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BACKGROUND TO THE INVENTION

THIS invention relates to a gyratory cone crusher.

Known gyratory cone crushers typically have a conical crushing head which is caused to gyrate within an outer cone, otherwise referred to as a liner or concave, which is mounted in an upper part of a main frame of the crusher.

Particulate material which is to be reduced in size is deposited from above into the varying gap between the crushing head and liner such that the particles of the material are crushed between the opposing conical surfaces of the outer cone and crushing head. in the known gyratory crushers, the crushing head is mounted on a shaft journalled within the bore of an eccentric mass which is supported for rotation in a sleeve mounted in a lower part of the crusher main frame. The eccentric is caused to rotate by a suitable drive. This may for instance

Co include a ring gear connected to the eccentric and a pinion which meshes with the ring gear and which is driven by an external motor.

Examples of known gyratory crushers having the features discussed above are described in US 3,302,896; US 3,456,889 and US 4,339,087. These crushers all have the facility to vary the crushing gap defined between the : crushing head and the outer cone, by varying the elevation of the outer : : cone and crushing head relative to one another, in order to vary the reduction ratio, i.e. the ratio of the size of uncrushed material to crushed material. :

However in all the known crushers there is a generally rigid kinematic relationship between the outer cone and the crushing head, attributable to Co the manher in which the eccentric is mounted in the sleeve, and this limits the reduction ratio which can be achieved. An additional limitation on crushing efficiency is the fact that in each case the crushing force is not adjustable.

A further problem with the known crushers mentioned above is the fact that it is generally impossible for the crusher to be started up without breakage of mechanical components if the crushing chamber is full of material.

SUMMARY OF THE INVENTION

A gyratory cone crusher according to the present invention comprises a main frame, a gyratory crushing head with a conical outer surface in the main frame, an outer cone which has a conical inner surface and which is supported in the main frame with its inner surface opposing the outer surface of the crushing head, a shaft for rotating the crushing head in a gyratory manner, a sleeve which is rotatable relative to the main frame, an : eccentric in which the shaft is located, which is located in the sleeve and which can move eccentrically in the sleeve, drive means for rotating the sleeve and articulated transmission means for transmitting rotation of the sleeve to the eccentric thereby to cause gyratory motion of the shaft and crusher head.

In the preferred embodiment, the crushing head has a spherically curved : lower surface which seats on a spherically curved upper surface of a seat supported by the main frame.

Preferably also, the sleeve is cup-shaped and includes a base with a spherically curved upper surface on which a spherically curved lower surface of the eccentric can float radially. The sleeve may be rotatable about a central axis of the main frame.

The articulated transmission means is typically a cardan shaft connected in articulated manner to the sleeve and to the eccentric.

The eccentric may carry replaceable weights, conveniently in an eccentric cavity, to enable the crushing force applied by the crusher to be varied.

In one version of the invention the drive means comprises a ring gear on the sleeve, a pinion which engages the ring gear and a motor for driving the pinion. In another version of the invention the drive means comprises a shaft connected coaxially to the sleeve and a belt drive for driving the shaft.

It is preferred that the main frame be supported relative to fixed structure by elastic mountings.

BRIEF DESCRIPTION OF THE DRAWINGS

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

In the drawings:

Figure 1 shows a cross-sectional view of a gyratory cone crusher according to this invention;

Figure 2 shows a cross-section at the line 2-2 in Figure 1;

Figure 3 shows a cross-sectional view of a gyratory cone crusher according to a second embodiment of the invention; and

Figure 4 shows a cut-away view of the gyratory cone crusher seen in

Figure 3.

DESCRIPTION OF THE ILLUSTRATED EMBODIMENTS

The gyratory cone crusher 10 seen in Figure 1 has a main frame or body 12 which has a central axis 14 and which supports an outer cone 16, towards its upper end, at a threaded connection 18. This allows the position of the outer cone to be adjusted vertically. The outer cone has a conical inner surface 20 formed by a lining 22.

The main frame includes a spherical seat 24 on which the underside of a crushing head 26 locates. The crushing head 26 has a conical outer surface formed by a lining or mantle 28.

The crushing head 26 is mounted fast on a shaft 30 the lower end of which is supported in an eccentric 32 via a bearing 34. The eccentric 32 is located in a cup-shaped sleeve 36, with a spherical lower surface 38 of the eccentric in contact with a spherical upper surface 40 of the base 42 of the sleeve. The complemental curvature of the surfaces 38 and 40 allows the eccentric to move freely, in a radial direction, with respect to the sleeve, i.e. the eccentric can float relative to the sleeve in a radial sense.

The sleeve 36 carries a ring gear 44 which is engaged by a pinion 46 carried by a shaft 48 supported in bearings 50 and connected via a flexible coupling 52 to a drive motor 54. When the motor is operational the shaft 48 rotates and transmits rotational drive to the sleeve 36 at a rotational speed determined by the gear ratio established by the meshing pinion 46 and ring gear 44.

The sleeve 36, which is supported for rotation in the main frame by radial bearings 56 and an axial thrust bearing 58, in turn transmits rotation to the eccentric 32 through a shaft 60. This in the nature of a cardan shaft which is capable of transmitting rotation but the respective ends of which are freely articulated to the sleeve and eccentric.

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The selected geometry is such that the minimum horizontal clearance 62 between the eccentric 32 and the sleeve 36 (Figure 2) is 1.5 times the maximum clearance 64 between the opposing surfaces of the liner 22 of the outer cone 16 and the liner 28 of the crushing head 26.

Figure 2 also shows that the eccentric 32 includes an internal cavity accommodating replaceable weights 66.

As shown in Figure 1, the main frame 12 is supported relative to fixed structure 68 on elastic mountings 70.

It will be understood that with the motor 54 running, the sleeve 36 rotates about the central axis 14. The eccentric 32 rotates eccentrically in the sleeve, resulting in gyration of the shaft 30 and crushing head 26 about a centre of gyration 72.

In use, material which is to be crushed is deposited into the crushing chamber 74 of the crusher 10 from, for instance, an overhead bunker as indicated by the arrow 75. Typically the deposition of material is such that the material generates a pressure of at least 0.7t/m? in the chamber. Once the chamber is fully charged, the motor 54 is switched on to start the operation of the crusher.

As indicated previously, the crushing head 26 describes gyratory motion on the spherical seat 24. Material which enters the gap between the opposing conical surfaces of liners 22 and 28 of the crushing head and outer cone is crushed and leaves the crusher through a chute 76, as indicated by the arrow 78. The size reduction which is achieved is determined inter alia by the centrifugal force generated by the gyration of the eccentric 32 and crushing head 26, and this is in turn partially dependent on the magnitude of the weights 66 carried by the eccentric. Thus by varying the magnitude of the weights 66 it is possible to vary the crushing force and accordingly the size reduction which is achieved.

It can be shown that the crushing force that can be applied by the crushing head 26 can be determined by the equation:

F =F. + Fo=w? (ml, +mel,)

Where: :

F is the crushing force;

F. and F, are respective values for the centrifugal force attributable to the crushing head 26 and eccentric 32; w is the angular speed of rotation of the eccentric 32; m.is the weight of the crushing head 26; m, is the weight of the unbalanced part of the eccentric 32, i.e. of the weights 66; .

I.is the amplitude of movement of the centre of gravity of the crushing head 26; and le is the distance from the centre of gravity of the eccentric 32 to the axis of the crushing head.

From this equation it can be seen that if the rotational speed w is increased by a factor of 2, the crushing force F is increased by a factor of 4. It can also be seen that the crushing force can be varied by modifying the various weights and amplitude.

Apart from providing the facility to vary the crushing force, the embodiment described above has the advantage that the free floating movement of the eccentric 32 in the sleeve 36 allows the crusher to be start up under load because the eccentric can move radially to the extent necessary to accommodate particles which are present in the crushing chamber 74.

Also, if a particularly hard particle which is not crushable should arrive in the chamber the eccentric can again move radially as necessary to allow passage thereof. In both cases, the free radial flotation of the eccentric permits the crusher to operate without damage to the mechanical components of the crusher.

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The opposing conical surfaces of the liners 22 and 28 of the outer cone and crushing head cannot impact against one another because the design is

Such that contact between the eccentric 32 and the inner surface of the sleeve 36 determines the minimum crushing gap.

It is perceived that a gyratory cone crusher as described above will have the ability to achieve a variable size reduction ratio of between 5 and 30, depending on the adjustments which are made.

Figures 3 and 4 illustrate a second embodiment of the invention which differs from the first embodiment only that it has a different drive arrangement. In this case, the previously described arrangement including the ring gear, pinion and shaft are replaced by a belt drive including a shaft 80 connected to the sleeve 36 and carrying a pulley 82 around which the belt is entrained.

Claims

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1. A gyratory cone crusher comprising a main frame, a gyratory crushing head with a conical outer surface in the main frame, an outer cone which has a conical inner surface and which is supported in the main frame with its : inner surface opposing the outer surface of the crushing head, a shaft for rotating the crushing head in a gyratory manner, a sleeve which is rotatable relative to the main frame, an eccentric in which the shaft is located, which is located in the sleeve and which can move eccentrically in the sleeve, drive means for rotating the sleeve and articulated transmission means for transmitting rotation of the sleeve to the eccentric thereby to cause gyratory motion of the shaft and crusher head.

9 . A gyratory cone crusher according to claim 1 wherein the crushing head has a spherically curved lower surface which seats on a spherically curved upper surface of a seat supported by the main frame.

3. A gyratory cone crusher according to claim 1 or claim 2 wherein an external lining on the crushing head forms the conical outer surface thereof. 4, A gyratory cone crusher according to claim 3 wherein an internal lining on the outer cone forms the conical inner surface thereof.

5. A gyratory cone crusher according to any one of the preceding claims wherein the sleeve is cup-shaped and includes a base with a spherically curved upper surface on which a spherically curved lower surface of the eccentric can float radially.

A gyratory cone crusher according to any one of the preceding claims wherein the sleeve is rotatable about a central axis of the main frame.

7. A gyratory cone crusher according to claim 6 wherein the articulated transmission means comprises a cardan shaft connected in articulated manner to the sleeve and to the eccentric.

8. A gyratory cone crusher according to any one of the preceding claims wherein the eccentric carries replaceable weights.

9. A gyratory cone crusher according to claim 8 wherein the eccentric includes a cavity in which the replaceable weights are accommodated.

10. A gyratory cone crusher according to any one of the preceding claims wherein the drive means comprises a ring gear on the sleeve, a pinion which engages the ring gear and a motor for driving the pinion.

11. A gyratory cone crusher according to any one of claims 1 to 9 wherein the drive means comprises a shaft connected coaxially to the sleeve and a belt drive for driving the shaft.

12. A gyratory cone crusher according to any one of the preceding claims wherein the main frame is supported relative to fixed structure by elastic mountings.

A gyratory cone crusher substantially as herein described with reference to Figures 1 and 2 or Figures 3 and 4 of the accompanying drawings.

Dated this 1% day of December 2009 SA SEF PZ (Grr %% Applicant's Patent Attorneys