SI8811327A - ROTATION Crusher - Google Patents

Abstract

A device for crushing brittle and easily crushed materials utilizing a rotating means. The crushing device comprises a housing (13) with a chamber (15) for receiving the material to be crushed. The chamber (15) has a central discharge opening (27) disposed at its base. The opening (27) defining a throat (38) comprises a peripheral wall (39). A rotating crushing head (17) is typically disposed centrally within the opening (27) at a distance from the throat wall (38) to define an annular roller gap (41) between the throat wall and the outer surface (37) of the head. The crushing head is centrally supported about a pivot point (B) to allow for rotational and oscillatory movement of the crushing head about the pivot point. Means comprising a spindle (43) are provided for effecting the oscillatory movement of the crushing head. The arrangement is such that the material poured into the housing is crushed by the movement of the crushing head relative to said wall, whereby the opposite sides of the crushing head cooperate with the wall of the throat to maintain the spacing of said gap during the entire oscillation of the crushing head.

Description

VOICE VERTICAL SHAFT CONUS Crusher

TECHNICAL FIELD

The present invention relates to a conical crusher of a rotary type with a vertical axis (MKP B 02 C 2 / 0.4 and B 02 C 2/06).

In this specification, the term rotary axis is defined as the axis relative to which the crusher head of the crusher is symmetrical and the term rotational angle as the angle between the center axis of the cone and the rotary axis.

TECHNICAL PROBLEM

With existing types of rotary crushers, there is a relatively large amount of variation in the material ejected from them due to their construction. . Therefore, when a certain dimension of material is required, it is usually necessary to recycle up to 40% of the ejected material to reduce it to a satisfactory size. Such inefficiency leads to a longer crusher operation and consequently a friction tendency for the crusher to wear and breakage due to failures.

In addition, internal cone crusher components below the crusher assembly must be of a complex and accurate design, which makes replacing these components very costly not only because of the cost of the components, but also due to the downtime requiring specialized for maintenance and repairs.

Therefore, a technical problem that is solved by the present invention in towers is to improve crushing efficiency and to reduce repair and maintenance costs by improved design of the rotary crusher.

BACKGROUND OF THE INVENTION

Existing types of primary secondary and tertiary crushers for the milling of brittle and easily brittle solid materials contain rotary crushers.

A typical rotary crusher consists of an inner conical cone, which rotates about the central vertical axis of the outer cone chamber, thereby defining the annular space between the cone cone, which narrows. The inner cone makes a circular motion around the vertical axis, but in the general case does not turn the eye

of its own axis of symmetry. ......;

The movement is transmitted to the inner cone by a camshaft assembly, which receives the drive

And on the underside of the cone from the external motor and the gear train. - The gear drive is driven by a large eccentric assembly, which also includes a camshaft assembly, which causes the shaft on which the cone is mounted to rotate about the vertical axis, with the intersection point of the vertical axis and the pivot axes above the inner coupe. According to the thorns, the rotation is almost completely horizontal, which determines the dimension of the annular space between the inner cone and the outer chamber.e in such a way that it is relatively small on one side of the inner cone and relatively large on the opposite side during rotation. This large change in the dimensions of the annulus gives a relatively large variation in the grain size of the material, which is emptied from the crusher.

In French patent file no. 1411834 presents a typical rotary crusher as described above.

It should also be noted that these conventional types of crushers having points of intersection between the center axis and the pivot axis grind a face positioned above the inner cone or head, that is, the internal projection at the base of the head is greater than the internal projection at the top of the head. It is also important that the head must be strengthened at the end where a larger eruption occurs, ie the lower part of the head, since at this point the pressure of the crushed material is greater on the head. Conversely, the part of the head where minimal ejection is present, ie the top of the head, requires minimal reinforcement or should not be strengthened at all because it receives less content. Consequently, friction, the durability of the head and drive shaft is increased by balancing by counteracting the heavier contents of the reinforced crusher parts or the lighter contents to those parts of the crusher that are not reinforced. The disadvantage of these types of crusher is that the grinding effect is obtained by giving the head a larger bulge at the top instead of at the bottom so that larger pieces of crushed material are present in the larger gap, so large deviations in the grain size of the material discharged from the crusher appear.

Without dwelling on this, crushers such as those disclosed in U.S. Patent No. 2326750 and Soviet 425642 were not practical due to the fact that the shape of the drive shaft head did not provide sufficient strength for the bottom of the head so as to ensure that the top of the head where present was greatest the amount of material is sufficiently strengthened. True, the primary types of rotary crushers have identified the need to provide reinforcement for the top of the head compared to the bottom of the head, even when the bulge at the top of the head is drastically reduced to reduce filling. moreover, in order to maintain this concept of starting a crusher, the means by which additional reinforcement can be provided can only be well made when. the axis has a point of intersection with the center axis at a point sufficiently overhead to allow the use of a spherical bearing,

- 3 centered at that intersection point, which is made possible as is enshrined in French Patent File 1411834,!

Consequently, a crusher having a point of intersection between the pivot and center ^x axis located below the crusher head is mechanically impractical due to the inability to fix the head at points subjected to maximum charge ·, which causes significant bumps at the curing points, that is, drones resulting in maintenance problems .

The described construction of known rotary crushers forms the aforementioned technical problem which should be solved by this invention.

DESCRIPTION OF THE SOLUTION OF A TECHNICAL PROBLEM WITH DESCRIPTION OF THE DRAWINGS In accordance with one aspect of the present invention, a device is provided. for crushing brittle 'or Although brittle materials, consisting of:

- one cone for receiving said material, with a central discharge opening at its base, wherein said discharge opening defines a single-walled throat in circumference;

- one crushing head positioned typically centrally within said emptying opening, with the outer surface crushing at a distance from said wall and said surface of said head; wherein said crushing head has a single rotary shaft;

- a drive assembly for driving said crushing head within said cone;

- wherein said crushing head is mounted on the opposite axial endings of the bearing assemblies, which hold said crushing head in a laterally displaced position relative to the central axis of said coupe, about a fixed point of the joint at the intersection of said pivot and center axes, thereby allowing the rotational and oscillatory motion of said head about said point; wherein said fixed point is located close to, or coinciding with, the bottom of said crushing head, such that the oscillation of the upper part of said crushing surface generally comes in a direction transverse to said central axis, and the oscillations of the lower portion are generally parallel to said central axis.

It is recommended that said bearing assemblies also include a pivot shaft, centrally located within said chamber, for rotation about the central axis,

- 4 wherein said shaft has one axial end within said chamber / to engage said head in such a way that it maintains said head at a fixed angular position displaced laterally relative to the center axis of said axis, allowing relative rotation of the head and said axis' ine. It is advisable to maintain said angular position by means of a single, positioned 'wedge on the wrist, or a sleeve inserted between said head and a shaft, said sleeve having a mid-axis,' which fits in with the pivoting axis of the head and enables relative rotation between said shaft and head. '

It is advisable that the bearing assembly comprises a cardan joint to support the crushing head relative to the heap, allowing the head to rotate freely and pivotably around the joints, with the joint having a pair of sliding components, one of which is positioned centrally within the outlet port at the base of the cone and the other component is at the right conical end of the head.

The invention will be better understood in the light of the following description of two typical embodiments thereof. The description is given with reference to the attached drawings, of which:

FIG. 1 is a schematic side view of the crusher, indicating the principle of achieving rotary motion;

FIG. 2 is a top view of the object of FIG. 1 in the crushing head area;

FIG. 3 is a cross-sectional view of the first embodiment of the crusher;

Fig, 4 is a cross-sectional view of a second embodiment of the crusher; and FIG. 5 exploded appearance of shaft, wedge joint, head and first bearing articulated bearing. . It should be noted that the sketches (especially Fig. 1) show a crushing head with an excessively large rotation angle for clearer illustration. In practice, the angle of rotation may be sharper (smaller) than shown, as opposed to the friction angle, this description does not exclude that the angle of rotation may also be obtuse (larger).

Both designs are aimed at making the crusher into rotary crushers, for both soft and brittle materials.

As shown in FIG. 1, in principle, the rotary crusher 11 consists of a cone 13, a crushing head 17, a drive assembly and a bearing assembly 20a, 20b at opposite ends of the head. In addition, the bearing assemblies 20a,

..,. . - -,. --- - - _

-5t

20b typically comprise a joint 19 near the base of the cone 13, a shaft 21 above / crushing head 17, and a bearing pin 23, between the axle 21 and the crushing head \. .

i

The cone 13 has an inner conical chamber 15 with an upper inlet-opening 25 through which the material can be inserted into the chamber 15 for crushing between the head 37 and the chamber 39 of the chamber, and a lower discharge opening 27 through which the crushed material is emptied from the crusher . The discharge opening 27 defines a throat 38 with an extensive, generally tapered wall 39, within which is a crushing head 17. The chamber 15 is usually symmetrical about the center axis of the AC, and can also be shaped in the form of an extensive conical wall 24 with an opposite cone slope relative to the throat wall 39. Towards the frills, the wall 24 narrows starting from the inlet 25 to the discharge opening 27 to connect tangentially to the throat 38. The circumferential wall 39 generally extends from the chamber 15 to the position of the cone 13. Accordingly, the friction wall 24 and widening of the wall 39 can crop ring constriction 29 within cone 13 at their junction, although some forms of cone 13 may not necessarily indicate the exact location of this constriction 29.

The wrist 19 is fixed centrally in the discharge opening 27 and typically has a half-blade face 31 on chamber 15. This half-blade face 31 represents the seat where the crushing head 17 is located, defining the ball joint so that the head 17 can pivot (tilt) , rotate and / or stack rotate about pivot point B, which lies on the center axis of the AC chamber 15, its own pivot axis GB of the crushing head 17 and the bottom of the crushing head 17. The crushing head 17 is usually of the shape of a serrated cone having an upper circularly axial end 33 having a diameter smaller than the diameter of the annular narrowing 29, a lower circularly straight axial end 35 parallel to the upper axial end 33 having a greater diameter than the diameter of the annular narrowing 29, and one a conical crushing forehead 37 extending between the upper and lower axial ends 33 and 35, respectively. The lower axial 'end 35 of the head 17 is hollowed out in the middle to obtain a bearing surface, which extends to the semi-ball face 31 of the joint 19 and allows universal rotation and rotation of the head 17 around the joint point B.

The wrist 19 and the head 17 are correctly shaped so that the head 17 can be located in the area of the discharge opening 27 so that its crushing forehead 37 is close to, but away from, the bulk wall 39 and the throat 38 and extends below the narrowing and so on defines annular recess 41 between wall 39 and forehead 37

- 6 _t J crushing heads. According to the torne, the diameter of the lower axial end is 35 heads. . 17 is smaller than the largest diameter of the discharge opening 27, so cla-; the amount of annular recess 41 between the crushing cone 37 and the wall 39 can be adjusted by axially moving the cone 13 with respect to the lower joint and head 17 by moving the joint 19 and head 17 in the axial direction in 'relative to the cone 13.

'i

According to the concept, the upper straight axial end 33 of the head 'is formed by a single circular recess 49, with a central axis directed at rSvan of the axial end 33 and coinciding with the pivot o, s0m of the head 17. The recess 49 is

V is provided to accommodate one end of the bearing pin 23, which connects the head 17 and the shaft 21.

The shaft 21 is connected to the shaft of the drive assembly 43, which is located near the tip of the cone 13 in order to allow the shaft 21 to rotate about the center axis of the AC chamber 15. The outer axial end 47 has a face 48 in an oblique plane relative to the right side of the shaft 21.

In the first embodiment, the outer axial end 47 of the axle, as well as the head 17, is provided with a circular recess 51 on its front 48, the central axis of which is directed relative to the plane of the front 48 and is displaced laterally for the prescribed distance from the central axis of the AC axis. The recess 51 is arranged to accommodate the second end of the bearing pin 23 so that the shaft 21 and the head 17 are connected by means of the bearing wedge 23.

The bearing pin 23 is in the form of a straight circular cylinder, with the opposite halves of the wedge forming outwardly directed bearing members, which are pivotally received within the corresponding recesses 49 and 51 on the head 17 and the shaft 21 and thus fixing the head 17 in the prescribed angular position with respect to the central axis of the AC, thereby allowing a relative rotation between the head 17 and the shaft 21 and the rotation of the head 17 about the center axis of the AC crushing chamber 15. Accordingly, the center axis of the recesses 49 and 51 and the bearing pin 23 coincide with the rotary axis GB of the head 17.

The axial portion of the bearing wedge 23 may be slightly longer than the sum of the dimensions of the recesses 49 and 51 to displace the forehead 48 and the upper axial end 33 so that the only bearing surface of the shaft 21 and the head 17 is on the bearing wedge. A dust seal (not shown) is provided between the front 48 and the upper axial end 33 to seal the wedge 23 and

- 7 and 4-well recesses of penetrated cone material '13:, '

In another embodiment, not shown, the opposite, el'o 48 and axial end 33 may be held separately in other ways, such as holding opposite axial ends on the inner rings of the tapered roller bearing (tapered roller bearing).

In operation, the drive shaft 43 receives typically a direct drive from a single hydraulic motor (not shown), which drives the Shaft 21 · in terms of rotation about the center axis of the AC crusher chamber. When the shaft 21 is turned, it causes rotation and the crushing heads 17 at a predetermined angular position, about the central axis AC, With rotation about the pivot point B of the joint 19, remaining usually free to rotate in each direction with respect to the cone 13 and the shaft about its own rotary axes GB.

If the pivot point B is placed close to or coincides with the bottom of the crushing head 17, and due to the relative spatial position and constriction of the constriction 29, the wall 39 of the throat 38 and the conical forehead 37 of the head, as well as the clearance of the annular recess 41, change only slightly around the lower the circumference of the head 37 of the head 17, throughout the entire stroke of the shaft of the drive train 43, while the upper obint EF of the tip of the forehead 37 for crushing, of the head 17 usually achieves a relatively large change in the size of the gap relative to the narrowing 29 in the cone, during this full rotation of the shaft 21.

In the absence of any resistance force on the head 17 while rotating it about the central axis AC, the head 17 can be rotated with respect to the cone 13 and with respect to the shaft 21. However, when brittle or easily brittle material enters the chamber 15 through the filling opening 25 and being adopted into the annular recess 41, the material will counteract the rotation of the head 17 relative to the cone 13. According to the friction axis, the shaft 21 will continue to rotate about the center-center axis AC, and the crushing head 17 will actually rotate about the turning point B During this rotation of the head 17, the head itself will rotate about its pivot axis GB. The rotation period for full rotation of the head 17 about the rotary axis GB is approximately equal to the rotation period of the rotary axis GB about the central axis AC; however, slight deviations may occur due to the friction effect of the crushing material between the wall 39 and the crushing forehead 37. This may cause a small circumferential movement of the lower circumference of the IH head relative to adjacent points on the circumferential wall 39 of the opening 27 for

- 8. 1 discharge clockwise or counterclockwise during head 17 rotation.

Thus, when the material is trapped in the annular recess 41, it creates a brake force due to the rotation of the head 17, which provides a relative rotation between the shaft 21 and the head 17. As a consequence, it provides a rotation of the head 17 around its rotating shaft GB and thus compound rotational motion around the pivot point B of the joint 19. According to the friction, the complex rotary motion of the head daje7 gives oscillatory motion along an I-trajectory at some point of the surface of the iflave 17, which has both a vertical and a transverse component of motion relative to the central axis of the AC crushes the face. It should be noticed. that this complex pivoting motion is achieved only when pivot point B is positioned close to or coincides with the bottom of the crushing head 17, with the bottom of the crushing head 17 defined as lying in a plane which coincides with the bottom of the forehead. · 37 for crushing. In this position, oscillations of the tip of the crushing head 37 generally occur in a direction usually transverse to the central axis AC (i.e., horizontally), and the oscillatory heads of the crushing head 37 occur substantially parallel to the central axis AC (i.e., vertical). Thus, the crushing movements are always transferred to the inserted material in the annular recess 41 in the form of a combination of transverse and vertical oscillations of the crushing head 17.

This type of crushing action gives a more effective force distribution to the material trapped within the gap, which reduces the tendency of the head 17 to collide with the material during its rotation and causes the use of compressive force for the constant pressing of the material between opposite sides of the annular recess 41 after contact is made.

Although not clearly seen in the drawing, this principle of complex rotation of the head 17 around the joint point B not only provides that different parts of the surface of the crushing head 17, which alternately determine the largest and smallest clearance in the recess during one revolution of the head 17, the corresponding smallest clearance between the bottom and top of the crushing forehead 37, which are diagonally opposite in relation to each other at any given time, and similarly to the corresponding largest clearances, are in phase position with a 180 ° intersection with each other. For example, when the head 17 is tilted to one side, as shown in FIG. 1, points F and H of the head surface cooperate with the circumferential wall 39 and thus determine the smallest gap in the recess 41 up and down on the crushing head 37, simultaneously meno, while opposite points E and I determine the corresponding maximum clearance in the recess 41 up and down on the crushing head 37.

It should also be noted that when one part of the recess 41 changes in view of its clearance from the minimum to the maximum, it is worse. or down. on the head, then the opposite situation occurs on the opposite part of the recess 41, so that there is always a partial progression of the material through the recess 41, in its entirety, as opposed to the complete collapse of the material through the recess 41, when the same material reaches its smallest dimension. For example, when the largest is reached at the top of one side of Chapter 17. a gap, at the top of the crushing forehead 37, at some point in time, then the smallest gap appears at the bottom of the same side of head 17, at the bottom of the crushing forehead 37, and the material actually fills the recess 41 in the form of letter V. However, when the head 17 turns for further 18θ dal the V-shape will become in the form of a letter V standing upside down (head), with the top on one side now defining the smallest gap at the top of the forehead 37 for crushing and the bottom on the same side the largest gap at the bottom of the same forehead. According to Torn, the material that was placed within the largest gap will become increasingly crushed, while the material placed in the zone of the smallest gap will gradually be released from the crushing pressure and be allowed to fall out of the crusher through the lower discharge opening. In this way, the material travels through the recess during multiple oscillations. Thus, a more efficient crushing operation is achieved than in previous types of crusher structures.

An important advantage of this embodiment lies in the towers, which by maintaining the smallest and largest clearance at any point in the circumference of the recess 41 during the rotation of the head 17, the variation of the material dimension, which is allowed to fall through the discharge opening 27 from the annular recess 41, small, allowing by accurately determining the dimensions of the milled material, thus avoiding or significantly reducing the need for matter! crushes again, the part that has not been reduced to the required measure. Adjusting the size of the annular recess 41 s.e is easily accomplished by simply raising or lowering the joint 19 along the axis inside

- 10 cones 13, or otherwise »cones with respect to / joint 19, Similarly, adjusting the size of the gap to compensate for the wear of the forehead 37 of the head. '

The first embodiment is shown in FIG. 3. and based on the essential description of the crusher. According to Torn, the call numbers used in the essential description of the crusher were also used in the drawing. identification-appropriate parts. .

The first derivation differs from the essential description only in the minor details.

The cone 13 is of segmental shape, and contains an inner portion 1.3a, which. is adjustably mounted inside the outer frame 13b, with the bottom 13c and the upper portion 13d, which protrudes above the inlet 25 for filling to allow the bearing of a large bearing to be secured to the shaft 21. One jamming mechanism may be of the usual construction (not shown) allowing the non-crushing material to penetrate the annular recess 41 without damaging the corresponding crushing forehead 37 on the head 17 and throat 38.

Another embodiment of the crusher is shown in FIG. 4 and its construction is very different from the first embodiment, although it fits in with the essential description, the crushers. According to the torn, used. are the same reference numbers in the drawings to identify the respective parts of the crusher, which were previously described in the essential description.

The second embodiment deviates from the previous one in the towers, which is provided by the upper portion 13d via the inlet 25 on the crusher chamber 15, thus achieving a double shaft bearing bracket 21.

According to the thorns, the shaft 21 may be of a different construction from that described in the previous embodiment, wherein the shaft of the drive assembly 43 may be longer in length and comprise an outer sleeve 53 and suction within a part 55 of a part 13d>, 'which part extends along the diameter , and one .57 inner sleeve housed in the 59 frame portion, which also extends along the diameter. The shaft 1 of the drive assembly 43 narrows symmetrically from its axial end 45 to the second axial end 47 within the cone 13. The axial end 47 is made with an end 61 having an external> - Λ * <- - · '· -11, straight forehead positioned obliquely with respect to the center axis of the chamber in the exact same manner as the yari axial end of the 33 axis in the previous embodiment. However, instead of having a circular recess 51 into which the articulated wedge enters, the outer face 63 is made at the same time as the positioning handle 54, so that the sleeve 54 protrudes outwards in the required lateral position relative to the center axis. As with the previous embodiment, the sleeve 54 is pivotally engaged in the recess 49, which is made in the upper circular axial end 33 of the crushing head. According to the thorns, the shaft 21 imposes the required position of the crushing head 17 as in the previous embodiment with the aim of achieving the rotary and compound-rotary movement of the crushing head 17 during the rotation of the shaft 21.

In a further embodiment, the sleeve 54 may be made at the same time as the head 17 and may be pivoted into a recess 31 made in the connecting straight face 63 of the shaft.

In one modification of the foregoing embodiments, the crushing head 17 may be made with any shape of the crushing forehead 37, such as an arch recess or a crushed forehead crushing, instead of a heaped heap shape.

According to the thorns, the shape of the 'extensive wall 39 can generally be such a gap creates a gap that is reduced between the forehead 37 for crushing the head and the wall 39 of the chamber, from narrowing 29 to the opening 27 for discharging on the crush face.

In a further embodiment, the position of point B may be higher or lower with respect to the head 17, as illustrated in the drawings above.

In a further embodiment, the axial bearing between the upper axial end 33 of the head 17 and up to its face 48 of the shaft 21 may be provided.

The present invention provides numerous advantages over prior art crushers. These benefits include:

1. Manufacturing costs are much lower than those for existing crushers, due to the simplicity of construction and the reduction in the number of components. For example, in conventional structures there are 30 or more major components, while in typical construction according to this one

И Л.

there are about 8 major components to the invention.

/

2. The foregoing solutions typically have 14 or more major moving parts ^x , while in the typical embodiment of the present invention there are only 3 or more major moving parts.

3. Due to the simplicity of construction, a significant reduction in the number of spare parts required for on-site maintenance has been achieved and the frequency of maintenance work is not great. '?

4. Relatively simple hydraulic actuators may be used in the construction of the present invention, as opposed to the use of electric motors and gearboxes in previous structures.

5. Lubrication is a simple process in this solution due to the simplicity of the components, while it is a complex job with previous structures.

6. Maintenance time is significantly reduced due to the reduced number of kbmpohenates compared to the previous ones. solutions ..

7. Due to the better mechanism of the new solution according to the invention, the driving force for the crushing of the face can be significantly less than. those of the previous solutions, 'for which the efficiency ratio' is only about 65%.

8. The operating efficiency of the present invention can reach 100% due to the small amount of material that needs to be crushed as opposed to the previous structures, where efficiency of the order of magnitude of only 60% is usually achieved.

9. The dimensions of the crushed grains may, when used in the present invention, be substantially less than 1/16 inch, with the practical absence of the need for repeated crushing, as opposed to conventional solutions which are difficult to achieve in the typical case of a grain size of 3/16 inch (with 40% or more of the product to be crushed)

10. The working mechanism has a small centrifugal imbalance (or none at all, depending on the external axle solution) compared to previous crusher solutions. Towne, habafia, loss

- 13 power and unbalance are minimized and thus enable · \

production of crushers of larger dimensions than was the case before.

11. Due to the simplicity and small number of components used, crushers of a small enough size can be produced for transport in ordinary vehicles for the transport of personnel or in the case of processing small quantities. 'Conventional crushing plants are expensive and of such dimensions that require heavy transport vehicles.

It is to be appreciated that the scope of the present invention is not limited to the particular embodiments disclosed herein. In particular, this solution is not limited to applications of ore crushing or in the mining industry, but may be useful in other fields, since crushing applied to the present invention is not limited by the size of the components.

Claims (18)

Patent claims 1. A conical crusher with a vertical pivot shaft _; or easily brittle materials, consisting of a cone (13) with a chamber (15) for receiving material and a central discharge opening (27) having a central axis (AC), is mounted at the base of the cone (13) and connected to the chamber (15) and defines a throat (38) with an extensive wall-lift (39), a sail head (17) for crushing with a rotary axis (GB), which is generally centrally located inside the opening (27) for discharge and has a crushing forehead (37) at a distance from the wall (39) of the neck (38) defining the annular recess (41) between the wall (39) and the head (37) for crushing the head (17) and the drive assembly (43) that drives the head (17) for crushing inside cone (13), characterized in that the crushing head (17) is mounted on its opposite axial ends by a carrier assembly (20a, 20b), which hold the crushing head (17) in a position offset relative to the center axis ( AC) about a stationary articulated point (B), located at the intersection of axes (AC) and axes (GB), for the rotational and oscillatory kr of moving the head (17) about point (B), and having point (B) near or coinciding with the bottom of the crushing head (17) such that the oscillations of the tip of the crushing forehead (37) are transverse to the median axis (AC) and oscillations of the bottom of the crushing forehead (37) are in the direction parallel to the central axis (AC). Cone crusher according to claim 1, characterized in that the carrier assembly (20a, 20b) comprises a pivot shaft (21) positioned centrally inside the chamber (15) for rotation about a central axis (AC), wherein the axial end (47) is axial (21) is connected to the leading axial end (33) of the head (17) and the other axial end is connected to the drive assembly (43) so that the axial end (47) holds the head (17) in a fixed angular position obliquely towards the central axis ( AC). Cone crusher according to claim 2, characterized in that the fixed angular position of the head (17) is secured by a bearing wedge (23) or a sleeve (54) inserted between the head (17) and the shaft (21), wherein the wedge ( 23) or sleeve (54) have a central axis which coincides with the pivot axis (GB) of the head (17). Cone crusher according to claim 3, characterized in that the angular position of the wedge (23) is fixed by connecting one axial end of that wedge to the axial end (47) of the shaft (21) in a position which is displaced sideways and oblique with respect to the central axis (AC) such that the center axis of the wedge (23) is fixed in the angular position and the other axial end of the wedge (23) is connected to the leading axial end (33) of the head (17) in a position coinciding with the rotated axis (GB) heads (17), wherein the center axis of the wedge (23) is coaxially connected to the pivot axis (GB). Cone crusher according to claim 4, characterized in that the wedge (23) is circular cylindrical in shape and its opposite axial ends make up the outer parts of the bearing, wherein the axial ends (47,33) of the shaft (21) and the head (17) have recesses (51,49) for receiving these bearings and fixing the head (17) and wedge (23) in a fixed angular position. Cone crusher according to claim 5, characterized in that the axial portion of the wedge (23) is slightly longer than the sum of the recess depth (51,49) to displace the axial ends (47,33) of the shaft (21) and the head (17). Cone crusher according to claim 3, characterized in that the angular position of the sleeve (54) is fixed by being either the axial end (47) of the shaft (21) and the sleeve (54) or the leading axial end (33) of the head (17) and sleeve (54) integrally shaped in a lateral and oblique position relative to the center axis (AC) such that the center axis of the sleeve (54) is in a fixed angular position in conjunction with the axial end (47) of the shaft (21) and with the axial at the end (33) of the head (17) such that the center axis (AC) of the sleeve (54) is coaxially connected to the pivot axis (GB). Cone crusher according to claim 7, characterized in that the sleeve (54) is circular cylindrical in shape and extends outwardly at the axial end (47) of the shaft (21) forming a projecting bearing and the end (33) of the crushing head (17) has a recess (49) for receiving that bearing and holding the head (17 in a fixed angular position. 9. Tapered crusher according to claim 7, characterized in that the sleeve (54) extends outwardly at the leading axial end (33) of the head (17) forming a protruding bearing corresponding to the recess at the axial end (47) of the shaft (21) thereby allowing the head (17) holds in a fixed angular position. 16 10. Cone crusher according to claim 8 or 9, characterized in that the axial length of the sleeve (54) is slightly greater than the depth of the recess (49) to displace the axial ends (47, 33) of the shaft (21) and the head (17). Cone crusher according to claim 6 or 10, characterized in that a gasket is inserted between the spaced axial ends (47,33) of the shaft (21) and the head (17) to seal the wedge (23) or sleeve (54) and the recess (49). ) against penetrating cone contents (13). 12. Cone crusher according to any one of the preceding claims, characterized in that the carrier assembly (20a, 20b) comprises a ball joint for crushing the head (17) for crushing relative to the cone (13) for free rotation and rotation of the head (17) about a joint point (B), said joint comprising a pair of coupled components, one of which is centrally located inside the discharge opening (27) at the bottom of the cone (13) and the other is mounted at the accompanying axial end (35) of the head (l7) ). 13. Cone crusher according to claim 12, characterized in that one of the aforementioned components consists of a joint (19) fixed at the bottom of the cone (13), and the other component is a single central recess at the accompanying axial end (33) of the head (17). , wherein the joint (19) has a semi-spherical forehead (31) facing the chamber (15) and said recess represents a bearing surface of a semi-spherical shape, corresponding to the joint (19), which forms a seat for rotation and nutrition of the head (17). 14. Cone crusher according to claim 12 or 13, characterized in that a device for adjusting the annular recess clearance (41) is provided between one of said components and the bottom of the cone (13). Cone crusher according to any one of the preceding claims, characterized in that the crushing head (17) has the form of a straight conical cone with leading and supporting axial ends (33, 35) defining circular, parallel foreheads and one large forehead (37 ) which narrows and lies between said two foreheads, wherein the axial end (33) has a smaller diameter than Also the axial end (35), and the forehead (37) defines together with the throat wall (38) a annular recess (41). 16. Tapered crusher according to claim 15, characterized in that the large forehead (37) has a portion recessed outwards extending from the leading end (33) to the accompanying axial end (35) with a curving portion that grows and a cylindrical portion of substantially constant diameter. , extending from the joint with said recessed portion to the accompanying axial end (35) Cone crusher according to any one of the preceding claims, characterized in that the chamber (15) is provided with a filling opening (25) through which the material is inserted and a large wall (24), which narrows from the opening (25) to the opening (27) for discharge to tangentially attach to the throat (38) whose circumferential wall (38) extends the cd chamber (15) towards the bottom of the cone (13), wherein the chamber (15) and the discharge opening (27) define one circular narrowing at its junction. A conical crusher according to any one of the preceding claims, characterized in that the shaft (21) is mechanically or electrically driven to rotate it.