WO1998036835A1 - Jaw crusher - Google Patents

Abstract

The invention relates to a jaw crusher, in particular a rapidly operating, single toggle crusher designed for crushing large quantities of rock, ore or clinker, comprising two crushing jaws (5, 7) one of which can at its lower end be vibrated by means of an eccentric drive while the other is immovably fixed in relation to the first, and the two jaws between them form a crushing mouth (13) with a crushing gap which narrows towards the bottom. The vibrating crushing jaw (5) at its lower end is mounted on the eccentric shaft (1) and its top end is held in a supporting manner against a movably held supporting element (3) by a tension spring system (4). Said jaw crusher is characterized in that the force of the eccentric shaft (1) is transmitted to the lower third of the vibrating crushing jaw (5) and the force of the supporting element (3) is transmitted to the top third of said crushing jaw.

Description

 Jaw crusher

The invention relates to a jaw crusher, in particular high-speed crusher, for high shredding performance of rock, ore or clinker with a rocker arm crusher with a vibratory exciter at its lower end by means of an eccentric drive, and one that is fixed relative to it and has a crushing jaw between it with downward crushing jaws forming a narrowing crushing gap, the oscillatable crushing jaw being mounted on the bottom of the eccentric shaft and being supported at the upper end against a movably supported support member by a tension spring arrangement.

Jaw crushers have long been known in a variety of different configurations. These features have in common the features that each jaw crusher has a movable crushing jaw and an oppositely fixed crushing jaw, between which the crushed material fed into the crushing gap is gradually crushed by periodic changes in distance.

In the prior art, a distinction is made between single toggle crusher, double toggle crusher, crank arm crusher and their design variants. Known for example is the "Blake" or double toggle crusher, which was designed and built in 1858. The crushing jaw, which swings around an upper joint, is arranged in the crushing gap at an angle of approximately 30 ° with respect to the vertical, thereby forcing the material to be shredded upwards. This creates friction, which causes wear and low performance and wastes part of the energy fed in. The "overhead" eccentric or single toggle lever crusher, constructed in 1879, also forces the material to be crushed upwards with its crushing jaw during the exercise and great wear. As a result of poor efficiency, the bearing stress is also extremely high.

To avoid these disadvantages, the long-known KUE-KEN crusher was designed, in which the crushing jaws do not move relative to the material throughput during the crushing process, and which consequently works almost smoothly.

In addition, so-called crank swing crusher in different designs are known, the movable crusher jaw being supported at one end in an eccentric shaft and supported at the other end by a movable support member.

From DΞ-OS 23 45 111 a swing arm crusher is known in a special design, which is designed for a low height and should be suitable for a fast-running mode of operation with high throughput. However, no information is given on the speed. Nor is there any information on the crushing performance. The known jaw crusher is characterized in a special way that in the upper area of the crushing area there is a limited oversize crushing zone which holds the rocks securely between the crushing tools. In addition, the vibrating crushing jaw is mounted at the lowest end in an eccentric shaft and is supported at the top end against an obliquely upward-moving rocker arm, the force vector of which is set so steeply that it just touches the top end of the rocker arm. With regard to its stress on bending, the rocker in a modified form forms a support resting on two ends with an irregular load therebetween, but in the area between the supports that means in the present case that a very high bending stress arises between the lower eccentric and the upper support member through the material to be crushed.

On the basis of the aforementioned prior art, the invention is based on the object of a jaw crusher, in particular a high-speed crank-rock crusher designed for high grinding capacity of rock, ore or clinker, with a vibrator excitable at its lower end by means of an eccentric drive , as well as with one of these fixed, between them a crushing jaw with a crushing gap to be narrowed crushing jaws, the vibrating crushing jaw being mounted on the bottom of the eccentric shaft and supported at the upper end against a movably supported support member by a tension spring arrangement which is held during the crushing process avoids an upward movement component and thus works almost smoothly, consequently realizes a relatively high crushing efficiency with high crushing performance of rock, ore or clinker and the effect of high bending stresses in the vibratable en Crushing jaw largely reduced, so that the rocker is lighter in design and can easily be operated with a reduced intrinsic inertia with a comparatively higher number of vibrations and reduced bearing stress with a compact overall height.

To achieve the object is proposed in a jaw crusher of the type mentioned in the preamble of claim 1 with the invention that the force introduction of the eccentric shaft in the vibrating jaw in the region of its lower third and the force introduction of the support member in the region of its upper third are arranged is. The fact that the crushing jaw is not supported or eccentrically at the outermost ends, as is customary up to now, but that the force application of the eccentric shaft and the support member is arranged approximately in the area of the lower and upper third of the pressure of the material to be crushed induced bending stresses are significantly reduced. The consequence of this is that the crushing jaw can be constructed and constructed with a considerably lower weight, which on the one hand saves costs and on the other hand considerably reduces the reaction forces acting on the eccentric bearing and support member, and this in particular in the desired rapid run.

Also deviating from the mostly conventional structural conditions of the prior art, it is provided in the crusher according to the invention that the drivable crushing jaw with a backward inclination is arranged at an angle between 5 ° and 10 ° relative to the vertical and the support member is preferably below the tension spring arrangement and with an angle relative to the horizontal between 15 ° and 30 ° is arranged. The interaction of the two measures results in an almost frictionless operation, in particular the forces acting on the eccentric shaft being considerably reduced. In particular, the flat position of the support member contributes significantly to this advantageous mode of operation.

In further refinements, it is provided that the eccentric stroke of the eccentric shaft is between 18 mm and 22 mm. In addition, the drive of the jaw crusher in connection with the flywheel is designed and tuned so that the crusher rocker is between 350 and 600 strokes per minute. In contrast, such a working speed has so far either not been achieved or was only achievable with above-average use of energy and wear and tear because, in the case of jaw crushers of conventional constructions, the material upward accumulation in the crushing gap increased with the operating speed in such a way that the movement of the material to be crushed became ever lower and thus lower the crushing performance decreased, what was called "supercritical" driving style in specialist circles. As a result, conventional crushers have been operated at a maximum speed of 250 revolutions per minute.

Further details, features and advantages of the invention result from the following explanation of an exemplary embodiment shown schematically in the drawing. Show it:

Figure 1 in side view of a crusher according to the invention;

FIG. 2 shows a kinematic diagram of the jaw crusher according to FIG. 1.

The illustration of the jaw crusher in the schematic diagram according to FIG. 1 shows that this crushes the material to be crushed in the lower region of the crushing gap 15 with the aid of the eccentric movement of the crushing jaw θ 5 by the eccentric shaft 1, which carries the movable rocker 5.

The crusher shows an extremely compact design, the aim of which is to meet the following requirements: 1) Low dead weight, in order to be able to move mobile or mobile systems on the road to different construction sites quickly.

2) low construction height, in order to be able to remain in road dimensions;

3) large mouth opening 13 in order to be able to accommodate even large pieces of material with the task 16;

4) suitable for high speeds in combination with a comparatively small crushing stroke in order to be able to produce material of good cubicity;

5) good pull-in properties for crushed material due to the elliptical movement of the movable crushing jaw 5, in particular to be able to process broken concrete with steel inserts.

In the upper area of the movable rocker 5, this is guided by a knee lever 3. With the downward movement of the eccentric shaft, the upper part of the movable rocker arm therefore also performs a limited relative movement in the direction of the X axis (FIG. 2).

According to the teaching of the invention, the force introduction of the eccentric shaft 1 into the oscillating crushing jaw 5 is arranged in the area of the lower third thereof, and the force application of the support member 3 is arranged in the area of its upper third. As a result, the bending forces acting on the crushing jaw θ 5 from the material to be crushed are considerably reduced, in comparison to a previously customary design in which the movable crushing jaw was supported at the outermost ends. The arrangement according to the invention shortens the distance of the cross section at risk of bending, which is why the crushing jaw 5 can be made considerably lighter and slimmer than conventional construction. On the one hand, this increases weight and saves costs, on the other hand, the carrying capacity unit compared to vibration excitation minimized, so that you can easily drive at increased speed, for example at 350 to 400 revolutions per minute. At the same time, the overall height is reduced in the manner shown in FIG. 1, so that the crusher according to the invention is suitable for mobile use on different construction sites.

The measure that the drivable crushing jaw 5 is arranged with a backward inclination relative to the vertical y-y at an angle β between 5 ° and 10 ° also contributes to this extremely advantageous result.

The design according to the invention is also characterized in that the support member 3 is preferably arranged below the tension spring arrangement 4 and at an angle relative to the horizontal x-x between 15 ° and 30 °. The requirement for a comparatively small stroke is met in that the eccentric stroke of the eccentric shaft 1 is between 18 mm and 22 mm.

As a result, the design of the jaw crusher and in particular its drive in cooperation with the flywheel 14 can be designed so that the crusher rocker 5 executes between 350 and 400 strokes per minute. For safety reasons, the flywheel 14 is loosely mounted on the eccentric shaft 1 and connected to it in rotation by an overload torque safety device, for example a shear pin.

In order to be able to adjust the crushing gap 15, the fixed crushing rocker 7 is designed in the lower region in such a way that a larger or smaller gap can easily be set by inserted strips 11 on the abutment 8. The required pivot point is arranged in the upper re-stock by a simple pan. Both the movable crushing back θ 5 and the fixed one Crushing jaws 7 are provided with crushing jaws 6 and 10 as wear parts in a manner known per se.

Figure 2 shows the kinematic situation of the crusher and in particular the angle of attack of the support member 3 and the angle β of the backward inclination of the

Crushing jaw 5. It is also clear from this that the crushing jaw 5 executes an elliptical or elliptical movement when the eccentric shaft rotates through 360 °.

Claims

claims 1. jaw crusher, in particular high-speed crusher, for high shredding capacities of rock, ore or clinker, with a rocker arm crusher, with a vibratory excitation at its lower end by means of an exciter drive, and one that is fixed to this, a crushing jaw (13) with a narrowing gap between them (15) forming crushing jaws (5, 7), the swingable crushing jaw (5) being mounted on the bottom of the eccentric shaft (1) and being supported at the upper end against a movably supported support member (3) by a tension spring arrangement (4), characterized that the force introduction of the eccentric shaft (1) into the vibrating jaw (5) is arranged in the area of the lower third thereof, and the force application of the support member (3) is arranged in the area of the upper third thereof. 2. Jaw crusher according to claim 1, characterized in that the drivable crushing jaw (5) with a backward inclination relative to the vertical (y-y) is arranged at an angle (β) between 5 and 10 degrees. 3. Jaw crusher according to claim 1 or 2, characterized in that the support member (3) is preferably arranged below the tension spring arrangement (4) and at an angle (α) relative to the horizontal (xx) between 15 and 30 degrees. 4. jaw crusher according to one or more of claims 1 to 3, characterized in that the eccentric stroke of the eccentric shaft (1) is between 18 and 22 mm. 5. jaw crusher according to one or more of claims 1 to 4, characterized in that its drive and flywheel (14) are designed and coordinated with one another so that the crusher arm (5) performs between 350 and 400 strokes per minute. 6. jaw crusher according to one or more of claims 1 to 5, characterized in that the flywheel (14) is loosely mounted on the eccentric shaft (1) and is rotatably connected to this by an overload torque safety device, for example a shear pin.