EP3784403A1

EP3784403A1 - Jaw crusher

Info

Publication number: EP3784403A1
Application number: EP19718120.9A
Authority: EP
Inventors: Jochen Meier; Till KRAUSS
Original assignee: Kleemann GmbH
Current assignee: Kleemann GmbH
Priority date: 2018-04-27
Filing date: 2019-04-11
Publication date: 2021-03-03
Also published as: US20210138477A1; DE102018110265B4; DE102018110265A1; WO2019206654A1; CN112041080B; CN112041080A; US11819855B2

Abstract

The invention relates to a jaw crusher with a stationary crusher jaw (21) and a movable crusher jaw (22), between which a crushing area (23) and a crushing gap (24) are formed. The movable crusher jaw (22) can be driven by a crusher drive (30) in order to generate a crushing movement, and one of the crusher jaws (21, 22), preferably the movable crusher jaw (22), is paired with an overload protection mechanism, wherein the overload protection mechanism has an adjustment unit (60) which produces a movement of the crusher jaws (21, 22) relative to each other in the event of an overload such that the crushing gap (24) is increased. When using such a jaw crusher, an improved operation is achieved if an actuation unit (100) is driven using the movement energy of a driven component of the jaw crusher, in particular the flywheels or the crusher drive (30) which drives the flywheels and the movable crusher jaw, and at least one actuator (80) is acted upon by the actuation unit (100) by means of a transmission means in order to produce the gap adjustment.

Description

jaw crusher

The invention relates to a jaw crusher with a fixed crushing jaw and a movable crushing jaw, between which a crushing space and a crushing gap are formed, wherein the movable crushing jaw for generating a crushing movement of a crusher drive is driven, wherein one of the crushing jaws, preferably the movable crushing jaw, a Overload protection mechanism is assigned, wherein the overload protection mechanism has an actuating unit which causes a movement of the crushing jaws relative to each other in case of overload, so that the crushing gap is increased.

Jaw crushers of the above type are used for crushing rock material, for example natural stones, concrete, bricks or recycled material. The material to be shredded is a task unit of the material crushing plant, for example in the form of a funnel fed and fed via transport means the crushing unit. In a jaw crusher, two crushing jaws arranged at an angle to one another form a wedge-shaped shaft, into which the material to be shredded is introduced. While a crushing jaw is arranged stationary, the opposite crushing jaw can be moved by means of an eccentric, and is supported on an actuating unit by means of a pressure plate. This is articulated relative to the movable crushing jaw receiving rocker and the actuator. This results in an elliptical movement of the movable crushing jaw, whereby the crushed material is crushed and guided in the shaft down to a crushing gap. The gap width of the crushing gap can be adjusted by means of an actuator.

During the crushing process, the crusher is exposed to high mechanical loads. These result from the feed size, the particle size distribution and the compressive strength of the supplied material as well as from the desired comminution ratio and the level of the material to be crushed within the crushing space of the crusher. In case of incorrect operation of the material crusher, especially when a non-breakable body, such as a steel body, enters the crushing space, it may cause an overload of the crusher. As a result, components of the crusher can be damaged or excessively fast wear.

The pressure plate can also serve as a predetermined breaking point in case of overload. Thus, if a non-breakable object blocks the crushing jaws against each other in the crushing space, the forces acting on the movable crushing jaw increase. These forces are transmitted to the pressure plate. If the forces are too high, then the pressure plate buckles. As a result, the movable crushing jaw deviates and the crushing gap increases. In this way, then the non-breakable object fall out of the crushing chamber. Damage to important system components of the jaw crusher is thereby reliably prevented. It can be seen that, because of the damage to the printing plate, this procedure is usefully applicable only at a very low frequency of foreign bodies reaching the crushing space. It was therefore sought in the prior art for ways to avoid damage to the printing plate. For this reason, EP 2 662 142 B1 proposes a jaw crusher in which the movable crushing jaw is again supported by a pressure plate. The pressure plate itself is supported on its side facing away from the movable crushing jaw with respect to a hydraulic cylinder. The hydraulic cylinder is associated with a high pressure valve. If an overload situation now occurs, the valve opens and the hydraulic cylinder triggers. Then the movable crushing jaw can dodge, whereby the crushing gap increases. The disadvantage of this design is that via the hydraulic cylinder no rigid support of the movable crushing jaw during the crushing process is more ensured. The hydraulic cylinder introduces too high elasticity into the system, which affects the crushing result.

It is an object of the invention to provide a jaw crusher of the type mentioned, which is characterized by improved performance.

This object is achieved in that an actuating unit by means of the kinetic energy of a driven component of the jaw crusher, in particular at least one flywheel of a crusher drive, the movable crushing jaw and / or of the movable crushing jaw driving crusher drive (30) is driven, and that at least one actuator ( 80) is acted upon by the actuating unit (100) with a transmission means to effect the gap adjustment.

It is thus the case that the kinetic energy of a driven component of the jaw crusher, in particular of the flywheel or of the flywheel drive or the movable crushing jaw driving the flywheels and the movable crushing jaw itself, is utilized to drive the actuating unit. There is enough power available to operate the overload protection. Accordingly, one or more actuators are actuated with the actuation unit, wherein the energy provided by the actuation unit is transmitted to the actuator. In particular, an adjusting device, for example, against which the crushing jaw is supported, can be moved during the crushing operation, for example, with an actuator, in order to allow evasion of the movable crushing jaw. The transmission of the actuating unit to the actuator is carried out according to the invention with a transfer agent, which may be particularly preferably an oil, in particular a hydraulic oil.

According to a preferred variant of the invention, it may be provided that the movable crushing jaw is supported relative to the crusher frame on a setting body of the setting unit, wherein the adjusting body relative to the movable Clamping jaw is adjustable in order to effect adjustment of the refractive gap, and that the actuator acts on the actuator body, so that it adjusts it in case of overload.

The setting unit can, for example, serve to set the movable crushing jaw for the normal crushing operation. According to the desired grain size, the crushing jaw is adjusted so that there is a defined crushing gap. The crushing jaw is now supported relative to the crusher frame on a setting body of the adjusting unit, in particular on a Verstellkeil. As a result, a fixed assignment of the movable crushing jaw to the actuating unit is created. This fixed assignment creates a clear and mechanically stable support. If, during the crushing operation, a non-breakable object enters the crushing space, the setting body, in particular the adjusting wedge, can preferably be adjusted transversely to the direction of movement of the movable crushing jaw. The movable crushing jaw dodges. The crushing gap is increased.

Particularly preferably, it may be provided that the actuator has two actuating elements designed as wedge elements, which are slidably supported against each other at their wedge surfaces, that one or both actuators is assigned in each case an actuator, and that one or both actuators are adjustable by the actuating unit. By means of this wedge adjustment, the gap can be set in a defined manner, if necessary with the aid of the actuators for the breaking process. If an overload situation now occurs, one or both actuators is used to effect an adjustment of the wedge elements. If both wedge elements adjusted so within a short time, a relatively large displacement can be driven to protect the crusher effectively against an overload situation. Of course, with a suitable design, it may also be sufficient to equip only one wedge element with an actuator and to drive it by the actuating element.

A further preferred variant of the invention is such that the movable crushing jaw is supported by means of a pressure element, preferably by means of a pressure plate relative to the setting unit, that a clamping cylinder, the pressure element keeps under pretension on the actuator, and that in case of a

Overload adjustment of the movable crushing jaw, caused by the

Actuator, the clamping cylinder is also re-tensioned by the actuator unit. The pressure element serves as a transmission element to perform the movement of the movable crushing jaw defines defined. The pressure plate is supported against the actuator. The actuator can be used to set the crushing gap defined. Now, if the actuator or an actuator associated with the element is adjusted in an overload situation of the actuator, the pressure plate must be reliably held in position. This is guaranteed by the clamping cylinder. The fact that the clamping cylinder is also acted upon by the actuating unit, the functionality of the actuator unit can be extended. It can be used for the adjustment of the clamping cylinder, the force which is generated via the kinetic energy of the crusher drive or the movable crushing jaw.

A particularly preferred variant of the invention is such that an overload situation is detected by means of a load sensor and a connected controller, and that the controller activates the actuating unit upon detection of this overload signal. This has the particular advantage that the present system is not only passive responsive to an overload case, but rather active and controlled the actuator unit can be activated to counteract an overload case. As a load sensor, for example, a force transducer can be used, which determines directly or indirectly the force in a component of the jaw crusher. For example, a part of the machine chassis, in particular of the breaker frame, can be measured, on which one of the two crushing jaws, particularly preferably the stationary crushing jaw, is supported. Particularly preferred, a strain gauge can be used, which detects the strain in the loaded component. This strain can be used to draw conclusions about the load behavior of the component.

A particularly preferred variant of the invention is characterized in that the actuating unit is a fluid pump, preferably a hydraulic oil pump. The fluid, preferably the hydraulic oil, can effectively act as a transfer means between the actuator and the actuator and / or the clamping cylinder can be used. The high forces can be reliably transmitted thereby.

One possible embodiment of the invention is such that the movable crushing jaw rotatably receives a drive shaft of the crusher drive, that the drive shaft has a deflecting piece, in particular an eccentric or a cam, and that an actuating element of the actuating unit cooperates with the deflecting piece to drive the actuating unit. In this way, the energy from the crusher drive can be introduced into the actuating element of the actuating unit with little technical effort. In this case, it may in particular also be provided that the actuating element rotatably receives a rolling body on a head, and that the rolling body with its running surface runs on the deflection piece, in particular the cam disc. The rolling body can roll on the deflection piece, in particular of the cam, whereby with little wear accurate guidance is possible.

For the operating unit a simple construction is obtained when it is provided that the actuating unit in a housing receives the actuating element adjustably, that the actuating element has at least one piston or at least connected to such a piston that the / the piston in one or more Pumping chambers is adjustable / are, and that at least one pumping chamber can be brought into fluid-conducting connection with the actuator and / or the clamping cylinder.

A particularly preferred embodiment of the invention provides that the actuating element against the bias of a spring in a waiting position in the housing is blockable, preferably hydraulically blocked. The actuator is held in the standby mode during normal operation of the crusher, so when no overload situation exists. Now, if the actuator unit is activated in case of overload, so the blockage of the actuator can be released and the actuator is supported by the spring quickly brought into its functional position. As a result, the functionality of the system and the operational readiness are given quickly. Thus can on one Overload case can be responded in no time. For this purpose, it may also be additionally or alternatively provided that a pressure accumulator is used, which presses a fluid under pressure in a first pumping chamber of the actuating unit and thereby expelled the adjusting movement of the actuating element from a waiting position or a pump end position in one Activation position moves or supports this movement.

According to a particularly preferred embodiment variant of the invention, it may be provided that the lower part of the movable crushing jaw during the crushing operation makes a partial movement in the direction of the fixed crushing jaw (closing movement) and a further partial movement away from the fixed crushing jaw (opening movement), and that at least an actuator is acted upon by the actuating unit with the transmission means to effect the gap adjustment, preferably in synchronism with this movement, in particular preferred when the movable crushing jaw moves towards the fixed crushing jaw or moves away therefrom. The gap adjustment can thus counteract either the closing part movement, so that the resulting closing movement is reduced or support the opening part movement, and thus increase the opening movement.

Of course, it is also possible to effect the gap adjustment when the crushing jaws are in an intermediate partial movement.

In the invention, one makes use of the knowledge that when the movable crushing jaw moves away from the fixed crushing jaw (opening movement), a relief situation arises. Accordingly, the force on the support of the movable crushing jaw is reduced during this movement, so that an easier gap adjustment with less required force is possible.

The invention will be explained in more detail below with reference to an embodiment shown in the drawings. Show it: FIG. 1 shows a schematic side view of a crushing plant,

Figure 2 in side view and schematic representation of a crushing unit of

Crushing plant according to FIG. 1,

3 shows a schematic representation of the breaking unit according to FIG. 2 in FIG

View from below of the crushing gap and in a first operating position,

4 shows the illustration according to FIG. 3 in a changed operating position, FIGS. 5 to 7 show an actuating unit in different operating positions and FIGS. 8 to 12 show hydraulic circuit diagrams.

FIG. 1 shows a crushing plant 10, namely a mobile jaw crusher plant. This crushing plant 10 has a hopper 11. By means of e.g. an excavator, the crushing plant 10 can be loaded in the hopper 11 with crushing rock material. Following the feeding hopper 11, a screening unit 12 is provided. The screening unit 12 has at least one screening deck 12.1, 12.2. In the present embodiment, two screen decks 12.1, 12.2 are used. With the first screen deck 12.1, a grain fraction can be screened from the crushed, which already has a suitable size. This partial flow does not have to be conducted through the crushing unit 20. Rather, it is guided past the breaking unit 20 in the bypass in order not to burden the crushing unit 20. At the second screen deck 12.2, a finer grain fraction is again screened from the previously screened fraction. This so-called fine grain can then be discharged via a sideband 13, which is formed for example by an endlessly circulating conveyor.

The material flow, which is not screened out on the first screen deck 12.1, is fed to the crushing unit 20. The crushing unit 20 has a fixed crushing jaw 21 and a movable crushing jaw 22. Between the two Crushing jaws 21, 22 is a crushing chamber 23 is formed. At its lower end, the two crushing jaws 21, 22 delimit a crushing gap 24. The two crushing jaws 21, 22 thus form a crushing space 23 converging toward the crushing gap 24. The fixed crushing jaw 21 is firmly mounted in the crusher frame 17. The movable crushing jaw 22 is driven by a crusher drive 30 in a known manner. The crusher drive 30 has a drive shaft 31 on which a flywheel 30.1 is rotatably mounted. This will be explained later. As can be seen further from FIG. 1, the crushing plant has a crusher discharge belt 14 below the crushing nip 24 of the crushing unit 20. Both the screened material bypassing the crushing unit 20 in the bypass, which is screened out on the first screen deck 12.1, and the crushed rock material falls onto the crusher discharge belt 14. The crusher discharge belt 14 conveys this rock material from the working area of the machine to a stockpile to transport. As shown in FIG. 1, a magnet 15 may be used which is arranged in a region above the breaker withdrawal belt 14. With the magnet 15 iron parts can be lifted out of the transported crushed material.

Finally, FIG. 1 shows that the crushing plant 10 in question is a mobile crushing plant. It has a machine chassis, which is supported by two suspensions 16, in particular two chain suspensions. Of course, the invention is not limited to use in mobile crushers. Also conceivable is the use in stationary systems.

In Figure 2, the kinematic structure of the crushing unit 20 in side view is schematically detailed again. From this view, the fixed crushing jaw 21 and the movable crushing jaw 22 are clearly visible. The movable crushing jaw 22 may, as in the present case be in the form of a crushing rocker. It has at the top a bearing point over which it is rotatably mounted, connected to the drive shaft 31. The drive shaft 31 is on the one hand rotatably mounted on the crusher frame 17 and the other with the eccentric part of the drive shaft, for example a lever, rotatably mounted in a bearing 32 of the movable crushing jaw 22. With the drive shaft 31 is a flywheel 30.1 with large mass rotatably coupled. The drive shaft 31 itself is designed eccentrically. Thus, in a rotary motion of the drive shaft 31, the movable crushing jaw 22 also performs a tumbling circular motion following the eccentric motion. In the region of the free end of the movable crushing jaw 22, a pressure plate 50 is provided. The pressure plate 50 is supported on the movable crushing jaw 22 via a pressure plate bearing 51. Another pressure plate bearing 52 supports the pressure plate 50 relative to an actuating unit 60.

The adjusting unit 60 serves to set the crushing gap 24 between the two crushing jaws 21, 22.

In order to maintain defined during the breaking process, the assignment of the pressure plate 50 to the actuator 60 on the one hand and to the movable crushing jaw 22 on the other hand, a clamping cylinder 40 is provided. The clamping cylinder 40 has a piston rod 41 which carries at its one end a fastening element 42. The fastener 42 is pivotally secured to the movable crushing jaw 22. The piston rod 41 is connected to a piston 45. The piston 45 is linearly adjustable in the clamping cylinder 40. The housing of the clamping cylinder 40 is supported by a carrier 44. The carrier 44 is supported via at least one, preferably two compression springs 43 with respect to a component of the crusher frame 17. Accordingly, a spring preload is introduced. The spring bias pulls the housing of the clamping cylinder 40 and with this the piston 45 and the piston rod 41. In this way, a clamping force is introduced into the movable crushing jaw 22, which transmits into the pressure plate 50. Accordingly, the pressure plate 50 between the movable crushing jaw 22 and the actuator 60 is clamped and held biased.

FIG. 3 shows that the pressure plate 50 is held between the two pressure plate bearings 51, 52. In the present exemplary embodiment, the setting unit 60 has, inter alia, two adjusting bodies 60.1, 60.2 which, as in the present case, may be designed in the form of adjusting wedges. The adjusting wedges are placed with their wedge surfaces 63 together. The adjusting wedges are designed so that they are in assembled state, so when they abut against the wedge surfaces 63, the opposite support surfaces 62 of the adjusting wedges 60.1, 60.2 are substantially parallel to each other.

As FIGS. 3 and 4 show, each actuator 60.1, 60.2 is assigned an actuator 80. The actuators 80 are preferably of identical construction. The actuators 80 may be designed as a hydraulic cylinder. The actuators 80 have a coupling piece 81. With this coupling piece 81, they are each connected to their associated adjusting body 60.1, 60.2. Coupled to the coupling piece 81 is a piston 82 which can be guided in a cylinder housing of the actuator 80 as a result of an adjustment of a hydraulic fluid. For attachment of the actuators 80 brackets 83 are used. With these brackets 83, the actuators 80 are connected to the crusher frame 17.

According to a preferred variant of the invention, the actuators 80 are bidirectional. They are used to allow adjustment of the crushing gap 24 during normal crushing operation. Accordingly, they can be controlled, for example via a controller. Since both actuators 80 are fixedly coupled to the adjusting bodies 60.1, 60.2, the adjusting bodies 60.1, 60.2 can be linearly displaced with the actuators 80. Depending on the Einsteil position of the actuating body 60.1, 60.2, the gap width of the crushing gap 24 is then determined. The clamping cylinder 40 retracts the adjusting movement, so that it is guaranteed that the pressure plate 50 is always securely held between the two pressure plate bearings 51, 52.

While a small crushing gap 24 is set in FIG. 3, a large crushing gap 24 is set in FIG.

As can be further seen in FIGS. 3 and 4, the fixed crushing jaw 21 is supported on the crusher frame 17. In the area behind the fixed crushing jaw 21, a load sensor 70 is attached to the crusher frame 17. The load sensor 70 measures the elongation of the breaker frame 17 in the area where the load sensor 70 is moored. Of course, the load sensor 70 also at another be fastened at the appropriate place on the crusher frame 17. It is also conceivable that the load sensor 70 is associated with one of the two crushing jaws 21, 22 or a machine component that is heavily loaded in the crushing operation.

As the illustration of Figure 2 shows, an additional deflection piece 33 is rotatably mounted on the drive shaft 31. The deflecting piece 33 may be formed, for example, by a disc-shaped element, in this case in particular by a cam disc. The disk-shaped element forms with its circumference a control cam.

FIG. 2 further shows that the breaking unit 20 is assigned an actuating unit 100. The structure of the operating unit 100 will be explained later with reference to FIGS. 5 to 7.

In Figures 5 to 7, the structure of the operating unit 100 is now detailed. As these illustrations show, the actuating unit 100 has a housing 101. The housing 101 may form at least one, in the present embodiment preferably three pumping chambers 102, 103 and 104. Each pumping chamber 102, 103 and 104 is equipped with a fluid connection 100.2, 100.3, 100.4. In the housing 100.1, an actuating element 110 is mounted.

The actuating element 110 can be adjusted linearly in the housing 100.1. The actuating element 110 has a first piston 110.1 and a second piston 110.2. Also conceivable are embodiments in which only one piston

110.1 is used. The first piston 110.1 faces the second piston

110.2 a relatively smaller diameter.

To the second piston 110.1, a connector 110.3 is connected. By means of the connector 110.3, the actuator 110 is led out of the housing 100.1, the connector 110.3 carries a head 120. With the head 120, a roller 130 is rotatably connected. The rolling body 130 may, as shown, have the shape of a wheel. The rolling body 130 has an outer circumferential raceway 131. As the drawings show, the actuating element 110 is supported in the housing 100.1 against the bias of a spring 140. In this case, the spring 140 preferably acts on the actuating element 110 in the area of one of the pistons 110.1, 110.2 and can be accommodated in one of the pumping chambers, preferably in the first pumping chamber 102, to save space.

The actuating unit 100 is spatially associated with the deflection piece 33 (see FIG. 2). The rolling body 130 is designed to unroll on a control cam of the deflection piece 33 when it rotates together with the drive shaft 31.

FIG. 5 shows the actuating unit 100 in its basic position. The jaw crusher works normally. There are no overload situations. In this state, a control pressure is applied to the pumping chamber 104 via the fluid connection 100.4. This control pressure blocks the actuating element 110 in the position shown in FIG. The spring 114 exerts a spring bias on the actuating element 110 against the pressure in the pumping chamber 104.

If an overload occurs, the operating position according to FIG. 6 initially results. Accordingly, the actuating element 110 is extended. For this purpose, the control pressure is removed from the pumping chamber 104. Via a fluid-conducting connection, the fluid is diverted from the pumping chamber 104 into the second pumping chamber 103. The spring 140 can relax, whereby the actuating element 110 is extended in the image plane according to Figure 6, therefore, the actuator 110 is offset to the right. Additionally or alternatively, pressure may be applied to the actuator 110 via the fluid port 100.2 to move it to its extended position. This pressure can preferably be applied to the fluid port 100.2, so that it also acts in the first pumping chamber 102. Accordingly, this pressure causes or supports the extension of the actuating element 110. When the actuating element 110 is extended, the rolling body 130 bears against the control cam. When the drive shaft 31 and with it the control cam rotates, the rolling body 130 rolls on the control cam. Accordingly, the rolling body 130 moves the contour of Cam after. As soon as the rolling body 130 ascends onto the deflection piece 33, the situation illustrated in FIG. 7 results. Then, a force F acts on the rolling body 130. This is the force induced by the kinetic energy of the moving parts of the jaw crusher and crushing jaw drive. The force can obtain a considerable amount of force solely by the fact that high kinetic energy is available in the system here due to the high moving masses (movable crushing jaw 22, flywheel 30.1). Accordingly, a particularly high force can be made available on the actuating element 110. The deflection piece 33 thus pushes the actuating element 110 out of the position shown in FIG. 6 into the housing 100.1. At the same time, the piston 110.2 displaces the hydraulic fluid in the first pumping chamber 102. The hydraulic fluid in the pumping chamber 103 is supplied to the clamping cylinder 40. The hydraulic fluid in the pump chamber 102 is supplied to the actuator 80. Flierdurch both the clamping cylinder 40 and the actuator 80, both of which are designed as hydraulic raulikzylinder adjusted.

As mentioned above, it is advantageous if not only one actuator 80, but both actuators 80 are adjusted simultaneously. As a result, the crushing gap 24 can be increased within the shortest possible time. In this case, both actuators 80 are connected to the first pumping chamber 102.

As a result of an adjustment of the two actuators 80, the two actuator 60.1 and 60.2 are shifted from each other. As a result, the movable crushing jaw 22 can escape, so that the crushing gap 24 increases. In order to prevent the pressure plate 50 from falling, as mentioned above, the tension cylinder 40 is activated. The clamping cylinder 40 pulls the movable crushing jaw 22 against the pressure plate 50, so that it is always maintained at tension.

Particularly preferably, it can be provided that, for the opening of the refractive gap 24, the actuator or actuators 80 are acted upon by the actuation unit 100 two or more times, within an overload cycle. Then, the actuator unit can be constructed with a relatively manageable volume become. For example, it can be provided that the actuating element 110 of the above-described actuating unit 100 performs two or more pump strokes. Per pump stroke then the actuator 80 and / or the clamping cylinder 40 is not moved over its entire travel, but only over a partial travel. After the deflecting piece 33 is fastened to the drive shaft 31, the pumping strokes can be realized one after the other in a temporally short sequence, so that a rapid opening of the refining gap 24 is possible.

It is also an embodiment of the invention conceivable in which the deflection piece 33 is designed so that can be realized per revolution two or more pump strokes. Likewise, an embodiment of the invention is conceivable in which two or more actuation units are used, all of which act on the actuators simultaneously or with a time delay.

The point in time at which the pumping action of the actuating unit 100 is initiated is determined by the position of the deflection piece 33 on the drive shaft 31. The deflection piece 33, which operates the rolling body 130, is arranged at an angle offset to the eccentric, which is responsible for the eccentric movement of the movable crushing jaw 22. About this angular offset, the opening movement of the actuator 60 can be synchronized to move the movable crushing jaw. Particularly preferably, the adjustment of the deflection piece 33 is such that the opening movement of the crushing gap 24 by the setting unit 60 just before the closing movement of the crushing gap 24, which is performed by the rotation of the drive unit of the crusher begins. As a result, unbreakable material in the Brechtmaul is not further crushed and the burden on the crusher mechanism is reduced. But it is also any other adjustment of the Auslenkstücks 33 relative to the eccentric conceivable. It would also be conceivable in principle that the position of the deflection piece 33 is adjustable relative to the eccentric in operation.

If, therefore, starting from the position according to FIG. 7, a pumping stroke is carried out, the actuating element 110 moves into the position shown in FIG. As soon as the deflection piece 33 releases the rolling body 130 again, the spring 140 and / or a control pressure applied to the fluid connection 100 Actuator 110 back into the position shown in Figure 6. Then the actuator 110 is available again for a subsequent further pumping stroke.

A possible embodiment of the invention is detailed in detail in hydraulic circuit diagrams in FIGS. 8 to 12. For better clarity, the individual lines are marked in the various functional positions shown in the figures. Here are lines that are depressurized, shown long dashed lines. Lines where a control pressure is pending, drawn thick drawn. Lines where a memory pressure is present, are shown in dashed lines. Lines in which a pumping pressure is present, are shown dotted.

As FIG. 8 shows, the clamping cylinder 40 and an actuator 80 are used. As mentioned above, two actuators 80 may also be used, which are then connected in parallel hydraulically. The following explanations apply to embodiments with one or two actuators 80. The actuating element 100 corresponds to the construction according to FIGS. 5 to 7. In order to avoid repetition, reference is made to the above statements. The clamping cylinder 40 has a chamber 40.1 which is filled with hydraulic oil. The actuator 80 has a first chamber 80.1 and a second chamber 80.2, which can also be filled with hydraulic oil.

It is also an accumulator 150 is provided. The pressure accumulator 150 serves to keep hydraulic oil under pressure. In the present embodiment, for example, a housing may be used to construct the pressure accumulator 150, in which a piston 152 is biased against a spring 151. The housing is used to hold hydraulic oil, which is biased by the piston 152 and the spring 151. The spring chamber can be relieved of atmospheric pressure or have a gas pressure.

As FIG. 8 shows, pressure is built up in the basic position by the pressure accumulator 150, which pressure is present as accumulator pressure in the hydraulic system. The accumulator pressure is shown in a dashed line. As the illustration further shows, stands the pumping chamber 104 to a control pressure (solid bold representation). The remaining lines, which are connected to the first pumping chamber and the second pumping chamber 102 and 103, via the unlockable check valves 188, 189 depressurized (long dashed line). FIG. 8 shows the waiting position which corresponds to the position according to FIG.

If an overload occurs, the situation shown in FIG. 9 results. The overload case is detected at the load sensor 170 and the associated controller. The controller then switches the electrically switchable valves 181 and 183. As a result of this switching operation, the control pressure is removed from the pumping chamber 104, so that here a pumping pressure is present (dotted line). At the same time on the one hand valve 182 is switched so that a free flow through the valve is possible, on the other hand, the lockable check valves 191 and 192 are unlocked. Since the hydraulic blockade of the actuating element 110 is now released as a result of the cancellation of the control pressure on the pumping chamber 104, the actuating element 110 can be moved in the image plane according to FIG. 9 from left to right. This adjustment is supported or effected by the accumulator 150. Which is now connected via the switching valve 182 with the pumping chamber 102. Since now the pumping chamber is in communication with the pumping chamber 103 via the release of valve 191, the actuating element 110 can shift in the image plane from left to right. In this case, the hydraulic oil, which is located in the pumping chamber 104, pumped into the pumping chamber 103. The hydraulic oil, which is present at the fluid port 100.2, is pumped into the pumping chamber 102. In this way, the actuating element 110 moves into its extended position, which is shown in the illustration according to FIG. 6 or FIG. 7. As mentioned above, in this position, the rolling body 130 is at the running surface of the cam, which has the deflection piece 33 at.

When the deflecting piece 33 strikes the rolling body 130, the pumping movement which presses the actuating element 110 back from its extended position according to FIGS. 6 and 7 into its retracted position according to FIG. 5 begins. This is illustrated in FIG. This creates pumping pressures. On the one hand, a pumping pressure is generated in the pumping chamber 103. The pumping chamber 103 is connected to the chamber 40.1 of the clamping cylinder 40 via the fluid connection 100.3. Accordingly, a pressure is introduced into the chamber 40.1, which acts on the piston 45 and thus activates the clamping cylinder 40. Accordingly, the piston rod 41 is moved with the piston 45 (the chamber 40.2 must be relieved of this). At the same time, the first pumping chamber 102 communicates via the fluid connection 100.2 with the chamber 80.2 of the actuator 80. This pumping pressure causes a displacement of the piston 82 in the actuator 80. With this adjustment, the coupling piece 81 is taken from right to left. So that the actuator 80 is not blocked, the chamber 80.1 is relieved on the other side of the piston 82 and that in the line leading away from the pressure accumulator 150. The Hyd rauliköl is thus relieved in this memory line and fills the accumulator 150 until the pressure exceeds the set pressure in the valve 187. Therefore, the accumulator pressure at maximum filling quantity and the pressure setting value of valve 187 are particularly preferably matched to one another. At the same time, the front chamber 80.2 is refilled by the returning oil via the check valve 193, which gains in volume during the pumping operation. For this purpose, the actuator 80 must have a specific area ratio or the return oil quantity of clamping cylinder 40 is used for this purpose. If, as a result of this process, the pressure in the line increases above a predefined limit value, a discharge into the tank 160 takes place via the limiting valve 187.

As mentioned above, following the first pumping stroke, a second or several pumping strokes may be provided. In order to secure the pressure in the clamping cylinder 40 and the actuator 80 after the first pumping stroke (see FIG. 11), two unidirectional valves 184, 185 are used. These are installed in the conduction path in front of the chambers 40.1 and 80.2 of the clamping cylinder 40 and the actuator 80. As FIG. 11 shows, the line path is blocked by way of these unidirectionally acting valves 184, 185, so that only the pumping pressure (dotted line) up to these unidirectionally acting valves 184, 185 is present. If further pumping strokes are to be carried out, the valves 181 and 183 remain open again. Flierdurch then results again in the situation shown in Figure 9, wherein the actuating element 110 extended becomes. Subsequently, the further pumping process according to Figure 10 and, if necessary, the pressure protection according to FIG 11.

As the pressure increases above the value set in the valve 186, the effluent oil will fill the accumulator 150. As the pressure increases above the value set in the valve 190, the oil is recirculated from chamber 103 to 104. The oil is retained in the system and is always ready for use in the next pump stroke even after longer phases at the pressure limit.

When the overload has ended, ie the crushing gap 24 has been opened and the non-breakable object has left the crushing space 23, then the valves 181 and 183 are switched to their original position. In this case, the triggered actuating unit 100 is also returned to its prepared waiting position. drove in accordance with Figure 8. For this purpose, an external pump 170 is activated. This is shown in FIG. The external pump 170 applies a storage pressure to the pumping chamber 104. The two other pumping chambers 102 and 103 are relieved. In this way, the actuating element 110 is moved back completely to the left into the waiting position, so that the rolling body 130 occupies a distance from the deflection piece 33.

Claims

claims

1. Jaw crusher with a fixed crushing jaw (21) and with a movable crushing jaw (22), between which a crushing space (23) and a crushing gap (24) are formed,

wherein the movable crushing jaw (22) is drivable by a crusher drive (30) for generating a breaking movement,

one of the crushing jaws (21, 22) preferably having an overload protection mechanism associated with the movable crushing jaw (22),

wherein the overload protection mechanism has an actuating unit (60) which, in the event of an overload, causes the crushing jaws (21, 22) to move relative to one another in such a way that the crushing gap (24) is enlarged,

characterized,

in that an actuating unit (100) is driven by the kinetic energy of a driven component of the jaw crusher, in particular at least one flywheel of a crusher drive, of the movable crushing jaw (22) and / or of the crusher drive (30) driving the movable crushing jaw, and in that at least one actuator ( 80) is acted upon by the actuating unit (100) with a transmission means to effect the gap adjustment.

2. jaw crusher according to claim 1,

characterized,

that the movable crushing jaw (22) relative to the crusher frame (17) on a control body (60.1, 60.2) of the actuating unit (60) is supported,

wherein the adjusting body (60.1, 60.2) relative to the movable crushing jaw (22) is adjustable in order to effect adjustment of the refractive gap (24), and that the actuator (80) acts on the actuating body (60.1, 60.2), so that he it is adjusted in case of overload.

3. jaw crusher according to claim 2,

characterized, the setting unit (60) has two adjusting elements (60.1, 60.2) designed as wedge elements, which are slidably supported against one another on their wedge surfaces (63),

in that one activator (80) is assigned to one or both actuators (60.1, 60.2),

and that both activators (80) are adjustable by the actuator unit (100).

4. Jaw crusher according to one of claims 1 to 3,

characterized,

the movable crushing jaw (22) is supported relative to the setting unit (60) by means of a pressure element, preferably by means of a pressure plate (50),

a clamping cylinder (40) holds the pressure element under pretension on the setting unit (60),

and that in the case of an overload adjustment of the movable crushing jaw (22), effected by the actuating unit (100), the clamping cylinder (40) is also tensioned by the actuating unit (100).

5. Jaw crusher according to one of claims 1 to 4,

characterized,

that an overload situation is detected by means of a load sensor (70) and a connected controller,

and that upon detection of this overload signal, the controller activates the actuator unit (100).

6. jaw crusher according to one of claims 1 to 5,

characterized,

in that the actuating unit (100) is a fluid pump, preferably a hydraulic oil pump.

7. Jaw crusher according to one of claims 1 to 6,

characterized, in that the movable crushing jaw (22) is rotatably coupled to a drive shaft (31) of the crusher drive (30),

the drive shaft has a deflection piece (33), in particular an eccentric or a cam disk,

and that an actuator (110) of the actuator (100) cooperates with the deflector (33) to drive the actuator (100).

8. jaw crusher according to claim 7,

characterized,

in that the actuating element (110) rotatably receives a rolling body (130) on a head (120),

and that the rolling body (130) with its running surface (131) on the deflection piece (33), in particular the cam disc, (33) expires.

9. jaw crusher according to one of claims 1 to 8,

characterized,

the actuating unit (100) adjustably receives the actuating element (110) in a housing (100.1),

the actuating element (110) has at least one piston (110.1, 110.2) or is connected to at least one such piston (110.1, 110.2),

the piston (110.1, 110.2) is / are adjustable in one or more pumping chambers (102, 103, 104),

and that at least one pumping chamber (102, 103, 104) can be brought into fluid-conducting connection with the actuator (80) and / or the clamping cylinder (40).

10. Jaw crusher according to one of claims 1 to 9,

characterized,

the actuating element (110) can be blocked against the bias of a spring (140) in a waiting position in the housing (100.1).

11. Jaw crusher according to one of claims 1 to 10,

characterized,

in that a pressure accumulator (150) is used which, when activated, presses a pressurized fluid into a first pumping chamber (102) of the actuating unit (100) and thereby converts the adjusting movement of the actuating element (110) from a waiting position or a pumping end position into one pushed out activating position moves or supports this movement.

12. jaw crusher according to one of claims 1 to 11,

characterized,

the lower part of the movable crushing jaw (22) makes a partial movement in the direction of the stationary crushing jaw (closing movement) and a further partial movement away from the stationary crushing jaw (opening movement) during the breaking operation, and at least one actuator ( 80) is acted upon by the actuating unit (100) with the transmission means to effect the gap adjustment, preferably in synchronism with this movement, particularly preferred when the movable crushing jaw (22) moves towards the stationary crushing jaw (21) or moves moved away from this.