DE102023106730A1 - Cone crusher with skewed axis - Google Patents

Abstract

The invention relates to a cone crusher (1) for crushing lumpy feed material (crushed material), with a crushing cone (6) supported on an axial bearing, inclined to the axis of rotation (R) and driven by an eccentric bushing (12), wherein the eccentric bushing (12) rotates in a radial guide about a fixed axle journal (10). The invention is characterized in that a central axis (Z) of the crushing cone (6) is aligned skewed to the axis of rotation (R) of the eccentric bushing (12). The invention further relates to an eccentric bushing (12) and a method.

Description

The invention relates to a cone crusher for crushing lumpy feed material (crushed material), with a crushing cone supported on an axial bearing, inclined to the axis of rotation and driven by an eccentric bush, wherein the eccentric bush rotates in a radial guide around a fixed axle pin. The invention further relates to an eccentric bush for use with such a cone crusher, as well as a method for crushing lumpy feed material (crushed material) using the cone crusher.

Crushers are mechanical crushing systems for crushing lumpy feed material (crushed material), whereby the grain shape and average grain size of the feed material are mechanically reduced during the crushing process, so that its grain size distribution is specifically influenced. Crushers can also be used to break down agglomerates, composites and other composite structures in the feed material in order to expose their subunits or components. The feed material is typically a mineral raw material with grain sizes in the coarse to medium size range. For example, crushers are used industrially in mining operations to process coal, ores, salts or other minerals, in quarries and gravel works to extract sand, gravel, grit and crushed stone with the desired properties, in industrial operations to crush the raw materials used such as lime works, coal-fired power plants or chemical plants (in the latter also to process products), in cement works to process cement or in the construction industry to process construction rubble, for which these crushers can be stationary or mobile. Crushers naturally offer particularly many advantages when feed material that exhibits brittle fracture behavior is to be crushed.

For the continuous coarse crushing and pre-crushing of brittle, medium-hard and hard feed material, cone crushers and gyratory crushers are used, among others, in which pressure crushing and/or impact crushing is carried out, in which the feed material is subjected to high mechanical stress. This type of crusher has a crushing chamber that is at least essentially formed by a hollow cone-shaped housing and a crushing cone. The hollow cone-shaped housing is at least partially lined with a wear-resistant crusher shell (crushing ring). Accordingly, at least part of the shell surface of the crushing cone is also lined with a wear-resistant crushing cone shell. The crusher shell and crushing cone shell are subject to high wear due to the mechanical stress during the crushing process and are therefore designed to be replaceable as wearing parts. The crushing cone is arranged as a movable conical crushing element on a crushing cone axis (also called crushing axis, crushing cone shaft, or crushing cone pin) in the crushing chamber. The center line of the predominantly rotationally symmetrical crushing axis is deflected at an angle to the crushing ring, which forms the hollow cone-shaped housing, with the intersection point of the center line of the crushing axis and the crushing ring axis being in the upper area of the cone crusher. The crushing chamber is limited at the bottom by an annular gap, which is formed by the lower area of the crushing cone shell and the lower area of the crusher shell and represents the discharge gap for the crushed material.

The lower end of the crushing cone axis extends into an eccentric bushing, so that the axis of rotation of the shaft that drives the eccentric does not coincide with the center axis of the crushing cone axis. During crushing operation, the crushing cone axis - and thus also the crushing cone - is therefore set in a circular wobbling motion. As a result, the annular gap does not have a constant gap width; rather, it has a gap width that changes periodically along the circumference of the lower area of the crushing cone shell during operation. During the wobbling motion of the crushing cone in the crushing chamber, the annular gap opens and closes all the way around, with the opening and closing taking place simultaneously on opposite sides of the crushing chamber. The gap width is typically changed by raising and lowering the crushing cone or the crushing ring.

Depending on the type of feed material and the characteristics of the crushed material to be achieved, different designs of crushing ring and crushing cone can be used, the characteristic size of which is the opening angle (cone angle) of the crushing cone: In a flat cone crusher, the crushing cone has a large opening angle (in particular opening angle between about 65° and about 100°), whereas the crushing cone of a steep cone crusher has a small opening angle (in particular opening angle between about 13° and about 45°). Steep cone crushers are typically used as primary crushers in order to subject feed material of large grain size with different grain shapes and sometimes a broad grain size distribution to pre-crushing. The cones of steep cone crushers are operated at relatively low rotation speeds, so that the material chunks fed into the crushing chamber mainly migrate downwards and are thereby crushed by the perio Flat cone crushers are crushed using periodically changing pressure (principle of pressure crushing). Flat cone crushers, on the other hand, are used as secondary crushers to crush feed material of medium or small grain size with at least essentially similar grain shape; secondary crushers are often arranged in the material flow path behind primary crushers. Flat cone crushers are operated at relatively high rotation speeds; in addition to the periodically changing pressure stress, a further, pulse-like stress is added, which crushes the feed material (principle of impact crushing).

If a cone crusher is used as a coarse crusher, both crushing surfaces - the outside of the crushing cone shell and the inside of the crusher shell - are often straight, so that they have the geometric shape of a truncated cone. If, however, the crusher is used as a fine crusher, the crushing surfaces can also be concave/convex. In addition, the surfaces of the crushing cone shell and/or crusher shell can also have a ribbed structure.

Gyratory crushers and cone crushers basically have a similar structure. In a gyratory crusher, the crushing cone axis is mounted in the upper part of the crusher (in the area where the crushing cone center line and the crushing ring axis cross) in a spherical bearing as a head bearing, which is arranged on a crossbeam. In this arrangement, the crushing cone axis transfers the horizontal crushing forces into the crusher housing via a bearing at the lower end as well as via the head bearing. Gyratory crushers can be used as steep cone crushers or as flat cone crushers. In contrast, with a cone crusher, the upper end of the crushing cone axis can be cantilevered in the area of the axis crossing, so that there is no head bearing. In this arrangement, the crushing cone axis can only transfer the horizontal crushing forces via a bearing at the lower end. Here, a short, particularly strong vertical axle journal absorbs all forces and transfers them into the crusher housing. Cone crushers can be used as flat cone crushers. The vertical forces can also be transferred via a spherical plain bearing cup, attached to the axle journal. The ball head support joint associated with the plain bearing cup is formed inside the crushing cone, the center of the ball roughly coinciding with the intersection point of the axles.

Cone crushers typically have three sections, namely the lower section (which, among other things, contains the drive and the discharge device for the crushed material), the middle section (which, among other things, contains the crushing chamber with the crushing cone and at least part of the crusher shell) and the upper section (which, among other things, contains the feed device).

The crushing effect of a cone crusher is achieved with the rotating wobbling movement of the crushing cone, whereby the changing annular gap between the crushing cone shell and the crusher shell exerts pressure on the feed material, causing it to break open and be crushed. The crushing cone shell and crusher shell are therefore exposed to particularly high mechanical loads and must be replaced from time to time, which is why they are detachably attached to the cone crusher. For this purpose, the crushing cone typically has a crushing cone body that is connected to the crushing cone axis in a rotationally fixed manner. The crushing cone shell rests on the outside of the crushing cone body and is typically designed as a bell-shaped hollow cone with an opening in its upper section through which the crushing cone axis is guided. The crushing cone shell is fixed to the crushing cone body, for which different fastening systems exist.

Various efforts have been made to reduce wear on cone or gyratory crushers, for example by using certain designs of the crushing cone shell and/or crusher shell or by using certain materials. The maintenance of such a crusher is also a relevant topic on which a lot of research has been carried out.

For example, EP3 129 148 B1 A cone crusher is known in which the axle journal is clamped in a certain way. EN 10 2012 110 267 A gyratory crusher is known, with a hydraulic clamping device on the traverse. Furthermore, for example, EP 3 132 853 A1 A special type of eccentric sleeve is known which enables distributed bearings in order to achieve improved weight compensation.

Another problem that exists in the area of cone and gyratory crushers is that the relative stroke in the upper area, i.e. the intake area of the crusher, is smaller and sometimes significantly smaller than in a lower area, i.e. the output area of the crusher. If one takes into account that a relative stroke of at least 10% is required for a high probability of breakage of 90% and more, in many cases the problem arises that only a relatively low probability of breakage can be achieved in the intake area of the crusher. This can impair the efficiency of the crushing process, since there is still a relatively large, unbroken mass in the intake area. There is a material present which prevents further crushed material from being conveyed.

An object of the invention is therefore to provide a cone crusher for crushing lumpy feed material which can achieve higher efficiency, higher throughput and/or lower and/or more balanced wear.

The invention solves the problem in a cone crusher of the type mentioned at the beginning in that the central axis of the crushing cone is aligned at an angle to the rotation axis of the eccentric bushing (claim 1). While in conventional cone crushers the central axis of the crushing cone is simply not parallel to the rotation axis, such that the central axis of the crushing cone and the rotation axis of the eccentric bushing intersect at a point approximately in the area of the cone tip or above the cone tip, the invention provides that the central axis of the crushing cone is aligned at an angle to the rotation axis of the eccentric bushing. In other words, in addition to the inclination of the center line of the crushing cone axis (central axis of the crushing cone) known in the prior art, which leads to the eccentricity of the eccentric bushing, the invention provides an offset of the central axis of the crushing cone preferably perpendicular to the plane of the inclination, so that the central axis of the crushing cone (crushing cone center line) and the rotation axis of the eccentric bushing) are skewed to each other and do not intersect.

The invention is based on the knowledge that the skewed alignment of the axes causes an axial offset between the two axes, which in turn means that a higher relative stroke can be achieved, particularly in the upper area of the crushing cone, which in turn can lead to an increased probability of breakage. A higher probability of breakage can in turn lead to an increased throughput and thus to an increased efficiency of the cone crusher. Maintenance can also be improved, since more even wear of the crushing elements can be expected due to the higher probability of breakage in the upper area of the cone crusher.

In a first preferred embodiment, a vertical distance between the central axis of the crushing cone and the rotation axis of the eccentric bushing is 5% or more of the eccentricity of the eccentric bushing. The eccentricity of the eccentric bushing is a consequence of the axial inclination of the central axis of the crushing cone and therefore variable over the axial length of the eccentric bushing. The eccentricity of the eccentric bushing is determined as the average of the minimum and maximum deviation of the bushing central axis from the rotation axis.

Preferably, the distance is 10% or more, 20% or more, or 50% or more. Preferably, the distance is simultaneously 30% or less, 50% or less, 70% or less.

In a preferred development, it is provided that a phase shift between the closed gaps (GSS) in the upper and lower areas of the crushing chamber is at least 5°, preferably at least 15°, and particularly preferably at least 45°. The phase shift is due to the skewed alignment of the central axis of the crushing cone to the axis of rotation. Phase shift here means that the position of the closed gap (GSS), i.e. the smallest distance between the crushing cone shell and the crusher shell in the upper area, and the closed gap (GSS), i.e. the smallest distance between the crushing cone shell and the crusher shell in the lower area, are not at the same rotational position around the axis of rotation, but have a (fixed) phase shift to one another. The phase shift between the lower closed gap and the upper closed gap is preferably at most 90°. If the point of a minimum distance between the central axis of the crushing cone and the axis of rotation is positioned below an upper end of the upper crushing chamber, the phase shift between the closed gap (GSS) in the upper and lower crushing chamber can also assume values over 90°, preferably a maximum of 180°.

The phase shift between the upper and lower closed gap can lead to an increased throughput. This is due to the path of the crushed material through the crusher. Crushed material is typically crushed in the area of the closed gap, or shortly before it, because the area of the closed gap has the greatest relative stroke and thus the greatest probability of breakage. Without a phase shift between the upper and lower closed gap, assuming vertical movement of the crushed material, it takes half a revolution of the eccentric bushing until the same crushed material is positioned again in the area of the closing gap. The fall time can be changed by a phase shift. For example, it can be provided that the upper closed gap leads the lower closed gap in the direction of rotation. In this way, it can be provided that the crushed material, which moves vertically through the crusher, initially in the area of the upper closed gap, then moves vertically and radially downwards and is then immediately broken again in the lower closed gap when the crushing cone continues to rotate. This means that the falling time for the crushed material is longer at the same speed, which can significantly increase the throughput.

In a further preferred embodiment, the cone crusher comprises a head eccentric bushing which is axially spaced from the eccentric bushing along the axis of rotation and guides the crushing cone radially on the axle journal in the region of a minimum distance between the axis of rotation and the central axis of the crushing cone. In this way, a distributed bearing or a distributed eccentric bushing can be achieved, which enables improved support of the crushing cone on the axle journal. In addition, such a divided eccentric bushing can advantageously be provided with a counterweight.

The cone crusher preferably also has a balancing weight, which is arranged with its center of mass out of phase with the deflection plane of the central axis of the crushing cone. Preferably or alternatively, the center of mass of the balancing weight is arranged at least approximately, preferably exactly diametrically opposite the resulting center of mass of the eccentric on the eccentric bushing. The balancing weight is preferably connected to the eccentric bushing or is part of it. In conventional cone crushers, the balancing weight, or counterweight, is typically exactly diametrically opposite the center of mass of the eccentric, relative to the axis of rotation, so that the imbalance of the eccentric can be compensated by the balancing weight. Due to the inclined position of the crushing cone, the center of mass of the crushing cone in conventional cone crushers is also arranged exactly diametrically opposite the balancing weight. This means that in conventional cone crushers, a center of mass of the balancing weight is exactly diametrically opposite the center of mass of the eccentric and the center of mass of the crushing cone in relation to the axis of rotation. However, in the cone crusher according to the invention described here, the balancing weight should be approximately opposite the resulting centers of mass from the eccentric and the crushing cone. The three centers of mass, the center of mass of the eccentric, the center of mass of the crushing cone and the center of mass of the balancing weight do not lie on a plane that also contains the axis of rotation, but rather span a plane that is intersected by the axis of rotation.

According to a further preferred embodiment, the central axis of the crushing cone is aligned with the rotation axis of the eccentric bushing in such a way that a relative stroke of at least 3%, preferably at least 5%, can be carried out in an upper region of the crushing chamber. Preferably, a relative stroke of 7% and more, 8% and more, 9% and more, 10% and more can be carried out. In this way, the probability of breakage in the upper region of the crushing chamber is significantly increased.

In a preferred development, the crushing cone is mounted in a floating manner. A crushing cone with a floating bearing is typically referred to as a classic cone crusher. For axial support of the crushing cone, a spherical bearing surface is preferably provided under the crushing cone, which is axially mounted on a spherical bearing cup, which is also preferably slidably mounted on the axle journal. In this way, a preferred axial support of the crushing cone can be achieved. In the floating bearing, the crushing cone is therefore only guided and supported by the axial bearing, which is preferably spherical as described, and radially by the eccentric bush.

In a preferred development, the cone crusher comprises a head support for the crushing cone, wherein the crushing cone is mounted on the head support so that it can rotate freely but preferably eccentrically. The crushing cone preferably comprises a support ring, via which the crushing cone is mounted so that it can rotate on the head support. The head support is preferably arranged in the region of the minimum distance between the axis of rotation and the central axis of the crushing cone, since this enables a particularly simple construction. A cone crusher with such a head support is also referred to as a gyratory crusher, wherein the head support typically does not absorb any axial forces, but only offers radial support.

In order to compensate for the wobbling movement, the head support preferably comprises a first outer radial bearing and a second inner radial bearing, wherein the second inner radial bearing is mounted eccentrically radially within the first outer radial bearing and the crushing cone is mounted on the second inner radial bearing. An eccentric ring is preferably formed between the first and second radial bearings, which enables the second bearing to be mounted eccentrically in the first bearing. Preferably, the inner, second radial bearing also carries a support ring which is in contact with the crushing cone in order to support the crushing cone radially.

The angular positions of the eccentric bushing and the eccentric ring are advantageously synchronized with one another in order to avoid high restoring forces due to the misalignment of the central axis of the crushing cone in the eccentric bushing. While synchronization can occur solely through the reaction forces in the eccentric bushing when the crusher is idling, a deviation from the specified phase shift of the two eccentrics can cause bearing forces. In order to ensure synchronization during operation, the crusher preferably has a synchronization device. For example, the synchronization device can comprise a mechanical coupling between the eccentric bushing and the eccentric ring in order to maintain the phase position of the eccentric bushing and the eccentric ring. Alternatively or additionally, a kinematic connection can preferably be provided within the crushing cone, such as a shaft that is mounted centrally in an axial passage in the crushing cone or the crushing axis, and/or a drive unit for the eccentric ring, which preferably drives it depending on the phase position.

In a second aspect, the invention solves the problem mentioned at the outset by an eccentric bushing which is intended for use with a cone crusher according to one of the above-described preferred embodiments of a cone crusher according to the first aspect of the invention. The eccentric bushing according to the second aspect of the invention preferably has a radially inner and a radially outer plain bearing, wherein the radially inner plain bearing is in contact with the axle journal and the radially outer plain bearing is in contact with a corresponding section of the crushing cone. The radially inner plain bearing and the radially outer plain bearing are preferably arranged skewed to one another. Each of the inner and outer plain bearings forms a cylinder shell and the central axes of these cylinder shells are skewed to one another.

In a further aspect, the invention achieves the object mentioned at the outset by a method for crushing lumpy feed material by means of a cone crusher according to one of the above-described preferred embodiments of a cone crusher according to the first aspect of the invention, wherein the crushing cone is driven such that an upper closed gap precedes a lower closed gap. Alternatively, it is provided that the crushing cone is driven such that an upper closed gap follows a lower closed gap.

It should be understood that the cone crusher according to the first aspect of the invention, the eccentric bushing according to the second aspect of the invention and the method according to the third aspect of the invention have the same and similar sub-aspects as are particularly set out in the dependent claims. In this respect, for preferred embodiments and developments of the eccentric bushing according to the second aspect of the invention and the method according to the third aspect of the invention, reference is made in full to the above description of the first aspect of the invention.

Embodiments of the invention are now described below with reference to the drawings. These are not necessarily intended to show the embodiments to scale; rather, the drawings are schematic and/or slightly distorted if this is useful for explanation. With regard to additions to the teachings immediately apparent from the drawings, reference is made to the relevant prior art. It should be noted that a wide variety of modifications and changes can be made to the shape and detail of an embodiment without deviating from the general idea of the invention. The features of the invention disclosed in the description, drawings and claims can be essential for the development of the invention both individually and in any combination. In addition, all combinations of at least two of the features disclosed in the description, drawings and/or claims fall within the scope of the invention. The general idea of the invention is not limited to the exact shape or detail of the preferred embodiments shown and described below or limited to an object that would be limited compared to the object claimed in the claims. For specified design ranges, values within the specified limits should also be disclosed as limit values and can be used and claimed as required. For the sake of simplicity, the same reference symbols are used below for identical or similar parts or parts with identical or similar functions.

• 1 einen Querschnitt durch einen Kegelbrecher gemäß der Erfindung;
• 2 eine schematische Ansicht eines Kegelbrechers gemäß dem Stand der Technik;
• 3 eine schematische Ansicht eines Kegelbrechers gemäß der Erfindung;
• 4 eine schematische Draufsicht auf den Brechkegel gemäß den 1 und 3;
• 5a, 5b schematische Ansichten einer Exzenterbuchse gemäß dem Stand der Technik und gemäß der Erfindung;
• 6 ein Diagramm, das Exzentrizität und Einzugswinkelreduzierung in Abhängigkeit von der Höhenposition im Brechraum zeigt;
• 7 ein Diagramm, das die Kraftwirkung auf den Achszapfen des Kegelbrechers illustriert; und
• 8 eine schematische Darstellung einer Traverse für einen als Kreiselbrecher ausgebildeten Kegelbrecher.

Further advantages, features and details of the invention will become apparent from the following description of the preferred embodiments and from the drawings, which show:

• 1 a cross-section through a cone crusher according to the invention;
• 2 a schematic view of a cone crusher according to the prior art;
• 3 a schematic view of a cone crusher according to the invention;
• 4 a schematic plan view of the crushing cone according to the 1 and 3 ;
• 5a , 5b schematic views of an eccentric bushing according to the prior art and according to the invention;
• 6 a diagram showing eccentricity and feed angle reduction as a function of the height position in the crushing chamber;
• 7 a diagram illustrating the force acting on the cone crusher’s axle journal; and
• 8 a schematic representation of a traverse for a cone crusher designed as a gyratory crusher.

A cone crusher 1 is known in the prior art in its basic structure. It has a crusher housing 2, which defines a crushing chamber 4 inside. The crushing chamber 4 is formed between a crusher casing (not shown in detail here) on the radially inner area of the crusher housing (crushing ring) and a crushing cone casing of the crushing cone 6 (also not shown in detail here). The crushing cone 6 has a spherical plain bearing 8, which rests against a spherical plain bearing cup 9. The spherical plain bearing cup 9 is supported and mounted horizontally on a fixed axle pin 10, which in turn is firmly and rigidly connected to the crusher housing 2. In this respect, the spherical plain bearing 8 and the spherical plain bearing cup 9 together form an axial bearing for the crushing cone 6.

The axle journal 10 also defines a plain bearing on its outer surface, which interacts with a radially inner surface of an eccentric bushing 12 in a basically known manner. The axle journal 10 itself is aligned vertically and the outer surface forms a cylindrical surface, which is also aligned vertically. The central axis of the axle journal 10 forms the rotation axis R, about which the eccentric bushing 12 can rotate. The eccentric bushing 12 is driven via a drive pin 14 driven by a drive motor (not shown), which interacts with a gear ring 16 at the axially lower end of the eccentric bushing 12 and drives it.

In the embodiment shown here, the radially outer surface 18 of the eccentric bushing 12 is inclined to the rotation axis R, i.e. the central axis defined by the radially outer surface 18 is inclined to the rotation axis R and is also offset from it and thus skewed. A crushing cone sliding bearing 20 is seated on the radially outer surface 18 of the eccentric bushing 12, which is essentially cylindrical and is designed coaxially to a central axis of the crushing cone 6. The central axis Z of the crushing cone 6 is thus skewed to the rotation axis R.

The 2 and 3 now show schematically the difference between a conventional cone crusher according to the state of the art ( 2 ) and a cone crusher according to the invention ( 3 ). According to the 2 and 3 the crushing cone 6 is shown once with a solid line in a position in which the closed gap at the lower crushing chamber edge (GSS-U) is on the right side of the 2 and 3 and a dashed line shows a position of the crushing cone 6 in which the closed gap is located at the lower crushing chamber edge (GSS-U) on the left side of the 2 is located. In 2 In the upper area or above the crushing cone 6, an intersection point S between the rotation axis R and the central axis Z of the crushing cone is shown, which is caused by the fact that in the prior art only an inclination of the eccentricity specified by the eccentric bushing 12 is provided, but no offset. The rotation axis R and the central axis Z are in the prior art, as in 2 shown, not skewed to each other.

On the right side of the 2 Particles P are also shown, which are arranged at three different positions in the crushing chamber. The solid lines show the height H of the particles P in the GSS and the dashed lines show the position of the particles P after the gap opening, depending on the position of the crushing cone 6.

3 now shows an inventive arrangement of the crushing cone, in which the rotation axis R and the central axis Z are skewed to each other. As can easily be seen from a comparison of the 2 and 3 is in particular the relative stroke in the upper area of the crushing cone (the relative movement of the crushing cone 6 back and forth; visible by the distance between the solid and dashed line). As a result, the height of the particles P is also different, particularly in the upper area. The higher relative stroke in the upper area of the crushing cone 6 leads to a higher probability of breakage, the different height H of the particles P also leads to a higher throughput and thus to higher efficiency.

4 now illustrates the shell surface, which is described by the central axis Z of the crushing cone 6, in a schematic plan view. 6-O and 6-U are in 4 an upper section (6-O) or lower section (6-U) of the shell surface is drawn. The two concentric circles are the sum of points that the crushing cone describes in the upper or lower section on its wobbling motion. R again denotes the axis of rotation and Z the central axis of the crushing cone. net. The rotation axis R is perpendicular to the drawing area of the 4 , while the central axis Z of the crushing cone 6 is skewed. GSS-O and GSS-U are the directions of the closed gap in the upper area and the closed gap in the lower area, and OSS-U and OSS-O are the opposite directions for the open gap in the lower area and the open gap in the upper area. As can be seen from 4 The closed gap in the lower area GSS-U is located at approximately 15° to the deflection plane of the central axis Z, while the closed gap in the upper area GSS-O is positioned at approximately 75°. This results in a phase difference PD between the point of the lower closed gap GSS-U and the point of the upper closed gap GSS-O of 60°. Depending on the direction of rotation of the eccentric bushing 12, the lower closed gap GSS-U can run ahead of or behind the upper closed gap GSS-O. In particular, running behind can be positive in achieving a high throughput.

The 5a and 5b now show schematically in a plan view an eccentric bushing 12 according to the prior art ( 5a) and an eccentric bushing 12 according to the invention ( 5b) . In the case of the eccentric bushing 12 according to the state of the art ( 5a) There is an eccentricity e in the cross-sectional area, which is caused by the tilting or deflection of the central axis Z of the crushing cone relative to the axis of rotation R.

In the case of the skewed bearing, the deflection of the central axis Z to the rotation axis R is initially reduced; however, according to the invention ( 5b) also an offset of the central axis Z of the crushing cone 6 to the axis of rotation R is implemented, which is perpendicular to the plane defined by the deflection or tilting of the central axis Z of the crushing cone 6 and the axis of rotation R known in the prior art.

The offset direction is in 5b indicated with an arrow. This results in a resulting eccentricity, which is shown in the cutting surface of the 5a and 5b can be approximately the same size, larger or smaller than the eccentricity e in the prior art, but differs in that the central axis Z and the rotation axis R are skewed to each other.

6 shows an effect of the changed eccentricity and the skewed arrangement of the rotation axis R and the central axis Z. The values are shown using a cone crusher with a crushing chamber height of 1200 mm as an example. The eccentricity, as it is known in the state of the art, is shown by the closely dashed line that runs from top left to bottom right. It changes linearly over the height of the crushing chamber, which, as described above, is due to the intersection point S of the rotation axis R and the central axis Z above the crushing cone 6. The eccentricity, i.e. the distance of the central axis Z to the rotation axis R (central axis Z in 6 also called "cone axis") as a function of the height position in the crushing chamber, is shown in the cone crusher 1 according to the invention by the solid line that runs from top left to bottom right. This means that the eccentricity in the upper region of the cone crusher does not approach zero and will not be zero either, since the axis of rotation R and the central axis Z are skewed and do not intersect. Rather, the eccentricity in the illustrated embodiment runs out to a value of around 10 mm, so that there is still a significant eccentricity in the upper region of the crushing chamber. In the example shown, the eccentricity in the intake area of the cone crusher is around 10 mm, while in the prior art it is around 3 to 4 mm. This enables a significantly larger relative stroke to be achieved, which also leads to a significantly increased probability of breakage in the intake area of the cone crusher. At the same time, the intake angle is also reduced, which is indicated by the longer dashed line.

7 shows a circular load diagram in which the load distribution over the crushing cone is shown in one revolution. The solid line shows the crushing cone 6 in a circle, the ordinate shows the offset direction of the central axis Z (cone axis) and the abscissa shows the deflection direction of the central axis Z (cone axis). The closely dashed line shows the force distribution in conventional cone crushers that have no offset between the rotation axis and the central axis, while the longer dashed line shows the design according to the invention with a skewed offset between the central axis and the rotation axis. As can be seen from 7 As can be seen, due to the phase shift between the upper and lower closed gap, a significantly larger circumference of the crushing cone is loaded (approx. 240°), while in the case of crushing cones in the prior art, only around 180° is loaded. This allows opposing forces to partially cancel each other out, which makes the circular load distribution on the crushing cone surface more favorable. The total force according to the prior art F(SDT) assumed to be 100% can be reduced to a total force F(E) of approx. 84% in embodiments of the invention. In addition, the phase of the total force changes, which means that the balancing weight must be positioned differently than is known in the prior art.

8 finally shows a traverse 22 with a first and second traverse arm 24a, 24b, which in turn are supported on the crusher housing 2 (not shown). The crossbeam arms 24a, 24b initially carry a first outer radial bearing 28, in which an eccentric ring 29 is then arranged, and radially inward of this a second inner radial bearing 30, which in turn carries a support ring 26. The support ring 26 is intended to come into contact with the crushing cone and to support it radially in a head region in order to form a gyratory crusher in this way.

List of reference symbols (part of the description)

1

Cone crusher

2

Crusher housing

4

Crushing room

5

Breaking ring

6

Crushing cone

6-O

upper section of the crushing cone

6-U

lower section of the crushing cone

8

spherical plain bearing

9

spherical plain bearing cup

10

Axle journal

12

Eccentric bushing

14

Drive pin

15

Output gear

16

Sprocket

18

radial outer surface of the eccentric bushing

20

Crushing cone bearing

22

traverse

24a

first traverse arm

24b

second traverse arm

26

Support ring

28

first outer radial bearing

29

Eccentric ring

30

second inner radial bearing

A

minimum distance between rotation axis and central axis of the crushing cone

e

eccentricity

GSS-O

upper closed gap

GSS-U

lower closed gap

OSS-O

upper open gap

OSS-U

lower open gap

H

Height of the particle

P

Particles

R

Rotation axis of the eccentric bushing

Z

Central axis of the crushing cone

QUOTES INCLUDED IN THE DESCRIPTION

This list of documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions.

Cited patent literature

• EP 3129148 B1 [0011]
• EN 102012110267 [0011]
• EP 3132853 A1 [0011]

Claims (15)

Cone crusher (1) for crushing lumpy feed material (crushed material), with a crushing cone (6) supported on an axial bearing, inclined to the axis of rotation (R) and driven by an eccentric bushing (12), wherein the eccentric bushing (12) rotates in a radial guide about a fixed axle journal (10), characterized in that a central axis (Z) of the crushing cone (6) is aligned skewed to the axis of rotation (R) of the eccentric bushing (12). Cone crusher according to Claim 1 , wherein a vertical distance between the central axis (Z) of the crushing cone (6) and the rotation axis (R) is 5% or more of the eccentricity of the eccentric bushing. Cone crusher according to Claim 1 or 2 , wherein a phase shift (DP) between the closed gaps (GSS-O) in the upper and lower regions of the crushing chamber (4) is at least 5°, preferably at least 15° and particularly preferably at least 45°. Cone crusher according to one of the preceding claims, wherein a phase shift (DP) between a lower closed gap (GSS-U) and an upper closed gap (GSS-O) is at most 180°, preferably at most 90°. Cone crusher according to one of the preceding claims, comprising a head eccentric bushing which is spaced axially from the eccentric bushing (12) along the axis of rotation (R) and guides the crushing cone (6) radially on the axle journal (10) in the region of a minimum distance between the axis of rotation (R) and the central axis (Z) of the crushing cone (6). Cone crusher according to one of the preceding claims, comprising a counterweight which is arranged with its center of mass out of phase with the deflection plane of the central axis (Z) of the crushing cone. Cone crusher according to one of the preceding claims, wherein the central axis (Z) of the crushing cone (6) is aligned with the rotation axis (R) of the eccentric bushing (12) such that a relative stroke of at least 3%, preferably at least 5%, can be carried out in an upper region of the crushing chamber (4). Cone crusher according to one of the preceding claims, wherein the crushing cone (6) is cantilevered. Cone crusher according to one of the preceding claims, comprising a head support (22) for the crushing cone (6), wherein the crushing cone (6) is mounted on the head support so as to rotate freely but eccentrically. Cone crusher according to Claim 9 , wherein the head support (22) comprises a first outer radial bearing (28) and a second inner radial bearing (30), wherein the second inner radial bearing (30) is mounted eccentrically radially within the first outer radial bearing (28) and the crushing cone (6) is mounted on the second inner radial bearing (28). Cone crusher according to Claim 9 or 10 , comprising a synchronization device for synchronizing the eccentric bushing (12) with an angular position of an eccentric ring (29) of the bearing of the crushing cone (6) on the head support (22). Eccentric bushing (12) for use with a cone crusher (1) according to one of the preceding claims. Eccentric bushing after Claim 12 , which has a skewed arrangement of a radially inner plain bearing and a radially outer plain bearing relative to each other. Method for crushing lumpy feed material (crushed material) by means of a cone crusher (1) according to one of the Claims 1 until 11 , wherein the crushing cone (6) is driven such that an upper closed gap (GSS-O) precedes a lower closed gap (GSS-U). Method for crushing lumpy feed material (crushed material) by means of a cone crusher (1) according to one of the Claims 1 until 11 , wherein the crushing cone (6) is driven such that an upper closed gap (GSS-O) follows a lower closed gap (GSS-U).

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