Crusher for mineral substances or recycled substances

Abstract

The invention relates to a crusher for mineral substances or recycled substances, comprising a crushing unit having a first crushing body, to which a movable second crushing body is assigned, between which a crushing gap is formed, a hydraulic cylinder is coupled to one crushing body and is designed to allow a movement of the coupled crushing body that increases the crushing gap during a deflection movement, the pressure chamber of the hydraulic cylinder is coupled to a pressure chamber of a pressure relief valve of the overload trigger device, and a piston of the pressure relief valve is adjusted between a closed position, in which a fluid-conducting connection between the pressure chamber and a pressure equalization region is blocked, and an open position, in which the fluid-conducting connection is released, and the piston has a piston pressure surface, the piston defines a pressure chamber by means of the piston in the closed position. In the case of overload, the overload triggering device responds quickly, in the closed state of the pressure relief valve, the piston pressure surface of the piston defines only part of the pressure chamber in a projection plane transverse to the adjustment direction of the piston. And the crushing gap is kept constant as far as possible during normal operation.

Description

Technical Field

[0001] The invention relates to a crusher for mineral or recycled materials, in particular a rotary impact crusher, a jaw crusher, a cone crusher or a roller crusher, the crusher having a crushing unit, the crushing unit having a first crushing body, in particular a rotor or a crushing jaw, wherein a movable second crushing body, in particular an impact rocker or a crushing jaw is assigned to the first crushing body, wherein a crushing gap is formed between the crushing bodies, wherein a hydraulic cylinder is coupled to one of the crushing bodies, the hydraulic cylinder being arranged and constructed in a deflection movement to allow a movement of the coupled crushing body that increases the width of the crushing gap, wherein the pressure space of the hydraulic cylinder is connected to a pressure chamber of a pressure relief valve of an overload triggering device, wherein a piston of the pressure relief valve is adjustable in the cylinder body between a closed position and an open position, wherein in the closed position a connection of a guiding fluid between the pressure chamber and a pressure equalization area is blocked and in the open position the connection of the guiding fluid is at least partially released, and wherein the piston has at least one piston pressure surface, by means of which the piston defines the pressure chamber in the closed position transversely to the adjustment direction of the piston. Background Art

[0002] DE 10 2017 002 079 B4 discloses an impact crushing device in which a variable crushing gap is set between a rotatable rotor and an impact rocker. In normal crushing operation, the material to be crushed is transmitted to the rotor via a material input. The rotor throws the material to be crushed toward the impact rocker. The forces that occur here cause the stone to be crushed. The stone is thus crushed into the desired particle size and can fall from the crusher housing via the crushing gap. At this time, it may happen that uncrushable objects are conveyed to the rotor. For example, in this case, these may be iron parts. This is a serious overload condition for the impact crusher. There is a risk of damaging the crusher in particular. In order to be able to control this overload condition, a piston-cylinder unit is coupled to the impact rocker. The position of the impact rocker and the width of the crushing gap can be changed by means of the piston-cylinder unit. The piston-cylinder unit includes a gas spring that supports the impact rocker.

[0003] In normal crushing operation, the width of the crushing gap is set to the desired extent. In the event of severe overload, the gas spring can be compressed and the impact rocker can be deflected. In this way, the crushing gap can be increased in a pulsed manner. Objects that cannot be crushed can now fall through the crushing gap. The width of the crushing gap is then set again to the desired extent.

[0004] With the aid of the gas spring proposed in DE 10 2017 002 079 B4, elasticity is introduced into the support of the impact rocker. During the crushing operation, the forces vary to a certain extent due to the different hardness and different size of the rocks. The elastic gas spring, in response to this changing force, causes a continuous change in the crushing gap and a continuous change in the particle size of the crushed material, which is undesirable.

[0005] EP 0 019 541 B1 discloses an impact mill in which the crushing gap can be set via a hydraulic cylinder. The hydraulic cylinder has a piston to which a piston rod is coupled. The piston is adjustable in the hydraulic cylinder space. The piston rod is connected to an impact rocker. An overload valve is provided in the event of an overload situation. If an object that cannot be crushed reaches the crushing space, the overload valve is triggered. As a result, the crushing gap is enlarged and the object that cannot be crushed can fall out of the crushing space again.

[0006] In crushers, in particular in rotary impact crushers, it is now customary, as described above, to feed stones of different sizes and different hardnesses to the crushing unit in normal crushing operation. The stones are controllable and can be crushed for the rotary impact crusher. In this respect, this less serious situation must be distinguished from a serious overload situation, in which objects that cannot be crushed reach the area of ​​the crushing unit. The method known from EP 0 019 541 B1 is suitable for slowly running crusher variants. In this case, the mechanical components for setting the crushing gap and the piston rod of the hydraulic cylinder must be moved so that the chamber pressure is set by fluid compression, which causes the triggering of the pressure relief valve. Obviously, the setting pressure of the pressure relief valve cannot be too low, because otherwise the adjustment of the crushing gap will occur due to the normal crusher load, which brings about a significant loss of final material quality. In fast-running crusher variants, a rapid opening of the crushing gap is required. Therefore, the pressure relief valve must be able to react quickly and at the same time be of sufficient size to be able to limit the pressure increase caused by the very fast accelerating mechanical components to set the crushing gap.

[0007] Other crushers with an overload triggering device are known from EP 3 919 177 B1 and EP 2 774 681 B1. Summary of the invention

[0008] The object of the present invention is to provide a crusher of the type mentioned at the outset, in which the overload triggering device responds quickly in the event of an overload and in which at the same time the crushing gap is kept as constant as possible during normal operation of the crusher.

[0009] This object is achieved in that, in the closed state of the pressure relief valve, a projection of one or more piston pressure surfaces of the piston in a projection plane transverse to the adjustment direction of the piston, in particular perpendicular to the adjustment direction of the piston, only limits a part of the pressure chamber transverse to the adjustment direction of the piston.

[0010] Compared to the known implementations in the prior art, this implementation makes one or more piston pressure surfaces and one or more active surfaces for introducing forces for adjusting the piston and for triggering the pressure relief valve smaller. Since the smaller surface results in a smaller clamping force, this clamping force can be easily absorbed later. In other words, a controllable force is generated on the piston in order to keep the pressure relief valve in the closed state during normal crushing operation, which force can be easily obtained outside the pressure chamber of the pressure relief valve. In addition, this design method achieves a reduction in the mass of the piston and the accelerated components of the pressure relief valve. This further improves the response behavior in the case of overload.

[0011] The pressure relief valve according to the invention can be designed so that there are multiple piston pressure surfaces on the piston, which piston pressure surfaces only define a part of the pressure chamber transversely to the adjustment direction of the piston in a projection plane transversely to the adjustment direction of the piston. The multiple piston pressure surfaces do not need to be in one plane on the piston. However, it is conceivable that the piston pressure surfaces have different shapes from each other.

[0012] According to a preferred variant of the invention, it can be provided that a bridge device is provided, the piston can be adjusted relative to the bridge device, the bridge device has at least one pressure surface segment, which in the closed state delimits the pressure chamber transversely to the adjustment direction of the piston, and the pressure surface segment or the pressure surface segments do not cover or do not completely cover the piston pressure surface in the projection plane, in particular in the closing plane, along the direction of the adjustment movement of the piston. A simple construction is thus achieved.

[0013] The bridge device can be designed in particular in the form of a projection, preferably in the form of a mandrel.

[0014] The piston pressure surface or surfaces may extend only over a partial region of the cross section of the pressure chamber transversely to the adjustment direction of the piston. The remaining cross section of the pressure chamber may be defined by one or more pressure surface sections of the bridging device.

[0015] Preferably, the bridge device is arranged in a stationary manner in or on the cylinder.

[0016] It is also conceivable that the bridge device is movable relative to the piston. For example, the bridge device can be fixed so that the bridge device can move in the direction of the adjustment movement of the piston and / or transversely to the direction of the adjustment movement of the piston.

[0017] It is also preferred that the pressure surface section of the bridging device is arranged centrally in the pressure space, wherein an annular space is also preferably formed between a radially outer limiting wall of the pressure chamber and a corresponding outer circumference of the pressure surface section, in which the piston is adjustable.

[0018] If it is provided that the surface normals on the projection of the piston pressure surface or surfaces and the pressure section or sections point in the same direction, the bridging device can be easily assigned to the pressure chambers of the pressure relief valve.

[0019] The crusher according to the present invention can be designed, for example, that the bridge device is connected to the cylinder of the pressure relief valve by means of a connecting section, in particular fixedly or movably connected, so that the bridge device holds the head on the carrier in the cylinder interior space, and the head forms or carries at least one pressure surface section. The load in the pressure chamber can be reliably transferred via the head and the connecting section. It is conceivable that the head and / or the connecting section form a guide for a piston, in particular of a cylindrical design. This reduces the cost of components.

[0020] A particularly preferred variant of the present invention is designed such that the piston has a cylindrical outer wall, the piston is arranged opposite to the cylinder inner wall of the cylinder body by means of the outer wall, the cylinder body forms a pressure chamber, and the piston is designed in an annular shape and has a preferably cylindrical inner wall. The piston is preferably configured as a sleeve-shaped component. Based on this structural mode, the piston can be designed relatively light but still stable. The end of the piston allocated to the pressure space can at least partially form the piston pressure surface. In other words, the sleeve end side can at least partially form one or more piston pressure surfaces.

[0021] A particularly preferred variant of the present invention can be designed such that the piston is supported relative to the spring with a supporting section outside the pressure chamber, wherein the spring introduces a preload force into the piston in the direction of the closed position of the piston so that the piston is preloaded relative to the valve seat. Reliable positioning of the piston in the closed position is thereby achieved with a controllable spring force. At the same time, a rapid return of the piston after the overload condition ends is achieved in a technically simple manner. The spring can be a mechanical element, such as a helical spring or a disc spring. It is also conceivable that the spring is formed by a fluid system, in particular by a hydraulic system. It is conceivable that the hydraulic system is formed as a space that includes a hydraulic cylinder, in particular a hydraulic cylinder, to accommodate a piston rod. It is conceivable that the spring is formed by a plurality of spring elements.

[0022] A particularly preferred variant of the invention is that the piston delimits the low-pressure region of the pressure relief valve relative to the pressure chamber and that the piston moves with the adjustment section in the low-pressure region when it is adjusted from the closed position into the open position. In the closed position, the low-pressure region and the region of the piston adjustment section held therein do not offer an active surface for the fluid of the pressure chamber. The pressure difference therefore influences the closing force.

[0023] If the low-pressure area is in air-conducting connection with the surroundings, the closing force can be supported, for example, by means of a spring or a spring system, as described above. The spring or the spring system must then be dimensioned to be sufficiently strong.

[0024] However, it is also conceivable to unload the low-pressure area toward the piston rod side of the hydraulic cylinder. In this case, it is also possible to assign a pressure regulating system to the space of the hydraulic cylinder that accommodates the piston rod, which preloads the hydraulic fluid in this area. This supports (for example, a spring can be additionally installed - see above) or causes the closing force of the piston. In addition, a pressure relief valve that can respond individually to the corresponding load situation in a matching manner is realized. If the load of the crusher is relatively high, but not yet an overload situation, the pressure in the pressure chamber of the hydraulic cylinder increases, wherein the hydraulic cylinder piston of the hydraulic cylinder enters the pressure space, and the pressure on the rod side decreases (this is the area of ​​the hydraulic cylinder that accommodates the piston rod). The pressure regulating system then fine-tunes the pressure on the rod side. In this case, the pressure regulation has a limited capacity in order to maintain the pressure. Therefore, the pressure regulation on the pressure relief valve causes the piston of the pressure relief valve to remain in the closed position. Therefore, the crushing operation can continue in this load situation.

[0025] If an overload condition occurs at this time, the pressure on the rod side drops sharply and the pressure regulation can no longer maintain the pressure on the rod side. At the same time, the sharp pressure increase on the bottom side of the hydraulic cylinder causes the pressure relief valve to open. The pressure relief valve can thus be adaptively matched to different load conditions.

[0026] A possible variant of the present invention can be that the cylinder body of the pressure relief valve has at least one outflow opening in the area of ​​the pressure chamber, the outflow opening being covered by a main area of ​​the piston connected to the piston pressure surface in the closed position of the piston and being at least partially released in the open position of the piston, and the outflow opening is indirectly or directly connected to the oil tank via a line section and / or is indirectly or directly connected to a chamber accommodating the piston rod of the hydraulic cylinder via a return line.

[0027] A particularly preferred variant of the present invention can be designed so that a projection of one piston pressure surface or multiple piston pressure surfaces of the piston in a closed plane transverse to the adjustment direction of the piston covers a projection of one piston pressure surface or multiple piston pressure surfaces of the piston in a closed plane transverse to the adjustment direction of the piston plus a pressure surface section of the bridging device, preferably by at least 5%, by a maximum of 80%, particularly preferably by at least 10% and by a maximum of 50%.

[0028] In a preferred variant of the invention, in the closed position a maximum of 50%, preferably a maximum of 25%, of the projection of the piston pressure surface or surfaces of the piston transversely to the adjustment direction of the piston in the closing plane is located in the region of the outflow opening.

[0029] The object of the invention is also achieved by a method for operating a crusher, wherein provision is made for a piston of a pressure relief valve to be displaced when a pressure threshold in the pressure space of the hydraulic cylinder is exceeded and for the piston to be moved back into a closed position by means of a spring when a relief pressure in the pressure chamber is fallen below.

[0030] The object of the present invention is also achieved by a method for operating a crusher, wherein it is provided that in the closed state of the pressure relief valve, the projection of one or more piston pressure surfaces of the piston in a projection plane transverse to the adjustment direction of the piston only limits a part of the pressure chamber transverse to the adjustment direction of the piston, so that when a pressure threshold in the pressure space of the hydraulic cylinder is exceeded, the piston of the pressure relief valve moves and when the pressure falls below the relief pressure in the pressure chamber, the piston moves back to the closed position with the aid of a spring. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] The present invention will be described in detail below based on the embodiments shown in the accompanying drawings. It is shown in the drawings:

[0032] Figure 1 A crushing unit of a rotary impact crusher is shown in a perspective view with the coupled mechanical parts of the crusher.

[0033] Figure 2 and Figure 3 The schematic diagram shows the method with an overload trigger device. Figure 1 Crusher unit,

[0034] Figure 4 The overload triggering device is shown schematically, and

[0035] Figure 5 The pressure relief valve of the overload triggering device is shown schematically. DETAILED DESCRIPTION

[0036] exist Figure 1 1 shows a crushing unit 10 of a rotary impact crusher. The crushing unit 10 comprises a crusher housing in which a movable crushing body 11 is rotatably supported. Accordingly, the movable crushing body 11 is designed as a rotor. The rotor carries a striking bar 12 in the region of its outer circumference.

[0037] The upper impact rocker 13 is arranged in the crusher housing. In addition, another crushing body 14 is also arranged in the crusher housing, and this other crushing body forms the lower impact rocker here.

[0038] A crushing gap 15 is formed between the rotor (crushing body 11) and the lower impact rocker (crushing body 14). When the rotor rotates, the radially outer ends of the impact bars 12 form an outer crushing circle. This crushing circle forms the crushing gap 15 together with the facing surfaces of the lower impact rocker. The lower impact rocker 14 is pivotably supported by means of a pivot bearing 14.1. The width of the crushing gap 15 can be set via the selected pivot position of the lower impact rocker.

[0039] like Figure 1 It can also be seen that a material inlet 16 is assigned to the crushing unit 10. The material 19.1 to be crushed can be fed into the crushing chamber via the material inlet 16. Figure 1 The conveying direction is symbolically indicated by arrows in FIG. When the material 19.1 to be crushed reaches the region of the crushing body 11, it is thrown outward by means of the impact bar 12. Here, the material hits the upper impact rocker 13 and the lower impact rocker 14. When the material to be crushed in the crushing space hits the impact bar 12 or the two impact rockers 13, 14, the material 19.1 to be crushed is crushed.

[0040] For example, in the case of the lower impact rocker 14 Figure 2 and Figure 3 When the material 19.1 to be crushed hits the crushing body 14, crushed material 19.2 is generated, such as Figure 2 As soon as the crushed material 19.2 has a particle size smaller than the crushing gap 15, the crushed material 19.2 falls through the crushing gap 15. The crushed material then reaches the collection area 17 below the movable crushing body 11 (rotor). Figure 1 As shown, a conveyor device 18 is connected to the collection area 17. The shredded material 19.2 can be transported away via the conveyor device 18.

[0041] like Figure 2 As further shown, the crushing body 14 is supported relative to the mechanical structure of the crusher by means of an actuator in the form of a hydraulic cylinder 20. The support on the mechanical structure, for example on the frame of the crusher, is not shown in detail in the figures. Figure 1 It can be seen in FIG. 1 that the hydraulic cylinder 20 is mounted in a protected manner substantially outside the crusher housing in which the rotor is accommodated.

[0042] like Figure 2 and Figure 3As shown, the hydraulic cylinder 20 has a cylinder body 25, in which the hydraulic cylinder piston 23 is guided so as to be displaceable. The hydraulic cylinder piston 23 carries a piston rod 22. The piston rod 22 is provided with a coupling part 21 at its end facing away from the hydraulic cylinder piston 23, which coupling part has a bearing part. The coupling part 21 is connected to the bearing 14.2 of the crushing body 14 by means of the bearing part. As a result, the hydraulic cylinder 20 can be pivotally coupled to the crushing body 14. The coupling point is spaced apart from the pivot bearing 14.1.

[0043] like Figure 2 As can be seen, the hydraulic cylinder-piston 23 defines a pressure space 24 in the cylinder 25. The pressure space 24 is filled with a hydraulic fluid, in particular hydraulic oil. The hydraulic cylinder-piston 23 is supported relative to this medium. As a result, the piston rod 22 and the crushing body 14 are held in place. Figure 2 The preset crushing position is shown.

[0044] The operating position of the crushing gap 15 needs to be set appropriately according to the existing crushing task. For this purpose, the crusher has a control device. Figure 2 If, starting from the position shown in FIG. 1 , the crushing gap 15 needs to be set wider, hydraulic fluid is released from the pressure space 24. As a result, the hydraulic cylinder-piston 23 moves further into the cylinder 25 until the desired crushing gap 15 is set. If, on the other hand, a narrower crushing gap 15 is desired, additional hydraulic fluid is filled into the pressure space 24. The hydraulic cylinder-piston 23 is thereby adjusted by increasing the pressure space 24. The piston rod 22 moves further out of the cylinder 25. As a result, the crushing body 14 pivots clockwise, resulting in a narrowing of the crushing gap 15.

[0045] like Figure 2 and Figure 3 As shown, an overload release device 30 is used. The overload release device can be directly connected to the hydraulic cylinder 20 or can be configured separately therefrom on the machine side.

[0046] The invention can also be implemented on different rock crushers, for example on a jaw crusher, a cone crusher or a roller crusher.

[0047] In a jaw crusher, the crushing unit has a fixed crushing jaw as a first crushing body 11 and a crushing body 14 in the form of a movable crushing jaw opposite the fixed crushing jaw. The fixed crushing jaw and the movable crushing jaw extend obliquely relative to each other, thereby forming a shaft between them that tapers conically toward the crushing gap 15. The movable crushing jaw is driven, for example, by an eccentric wheel.

[0048] The movable crushing jaw is moved toward the fixed crushing jaw and away from it in an elliptical motion by means of the eccentric. During this stroke, the spacing between the crushing jaws also changes. The material 19.1 to be crushed is constantly crushed further along the conical shaft by the movement of the movable crushing jaw until it reaches a particle size that allows it to leave the shaft through the crushing gap 15. The crushed material 19.2 falls onto the crusher delivery belt and is further transported via the crusher delivery belt. The movable crushing jaw can be supported relative to the frame by means of an actuator 20, which can be constructed, for example, in the form of a hydraulic cylinder 20. The hydraulic cylinder 20 can be constructed, for example, in the manner described above. An overload trigger device 30 can then be coupled to the hydraulic cylinder 20.

[0049] Figure 4 A variant of an overload triggering device 30 is shown. The schematic diagram again shows a hydraulic cylinder 20, which has a hydraulic cylinder piston 23 guided in a cylinder 25 and coupled to a piston rod 22. The piston rod 22 is guided out of the cylinder 25. The piston rod 22 is arranged in a chamber 26 of the cylinder, which forms the rod side of the hydraulic cylinder 20. Outside the cylinder 25, the piston rod 22 is coupled to the crushing body 14 by means of a transmission device 27. In the simplest case, the transmission device 27 can be formed by the coupling element 21.

[0050] The pressure space 24 of the hydraulic cylinder 20 is connected to the pressure relief valve 40 via a pressure line 31 . The chamber 26 (rod side) of the hydraulic cylinder 20 is hydraulically connected to the pressure relief valve 60 via a return line 33 and a collecting line 34 .

[0051] Reference below Figure 5 Possible variants of the pressure relief valve 40 are described. Preferably, the pressure relief valve 40 is installed at a location of the overload triggering device 30 which is hydraulically connected to the pressure chamber 24 via the pressure line 31 .

[0052] Figure 5 It is shown that the pressure relief valve 40 has a cylinder 41 . A piston 43 is guided in the cylinder 41 so that it can be adjusted linearly.

[0053] The cylinder body 41 has a cylinder inner wall 41.1, which is preferably designed as a hollow cylinder. The cylinder inner wall 41.1 forms a sliding surface 41.8. The piston 43 is guided on the sliding surface 41.8 in a sealing manner. Here, the piston 43 can have a cylindrical outer wall, which is opposite to the sliding surface 41.8 and is preferably guided on the sliding surface.

[0054] The cylinder 41 has one or more passages 41.3, which connect the low pressure area 41.2 of the pressure relief valve 40 to the surrounding environment, which will be described in detail later. At least one passage 41.3 can preferably be introduced in the bottom of the sleeve part, such as Figure 5As shown, the sleeve part is preferably designed as a cylinder bottom 41 . 4 of the cylinder drum 41 .

[0055] As from Figure 5 It can also be seen that the cylinder 41 has at least one outflow opening 41.5, which is preferably introduced into the cylinder wall as a notch. Preferably, at least one outflow opening 41.5 can be arranged spaced apart from the cylinder bottom 41.4, preferably in the region of the cylinder 41 facing away from the cylinder bottom 41.4.

[0056] A bridge device 42, for example in the form of a projection that projects into the cylinder interior, in particular in the form of a mandrel, is held in the cylinder body 41. Figure 5 As shown. Preferably, the bridge device 42 is connected to the cylinder body 41 in a fixed position. It is also possible that the bridge device 42 is not connected to the cylinder body 41 in a fixed position. For example, the bridge device 42 can have a gap in the radial direction. This can, for example, compensate for manufacturing tolerances. Additionally or alternatively, it is also conceivable that the bridge device 42 has an axial gap in order to, for example, be used as a reservoir.

[0057] According to this exemplary embodiment, the bridge device 42 can be coupled to the cylinder 41 , preferably to the cylinder bottom 41 . 4 , by means of a connecting section 42 . 1 .

[0058] The bridge device 42 has a carrier 42.2 which carries a head 42.3. The head 42.3 has a pressure surface section 42.4 which delimits a pressure chamber 41.6 in the cylinder 41 in the closed state of the pressure relief valve 40.

[0059] The pressure surface section 42.4 can be designed as a flat surface, such as Figure 5 As shown. In particular, the pressure surface segment 42.4 can be designed in the shape of a disk, in particular as a disk. However, it is also conceivable that the pressure surface segment 42.4 consists of a plurality of surface parts, which do not necessarily need to be located in one plane, but define the pressure chamber 41.6. In this case, it is advantageous if the projection of all surface parts of the pressure surface segment 42.4 in a plane perpendicular to the center axis M of the cylinder 41 forms a disk.

[0060] Figure 5 It is shown that the projection surface of the pressure surface section 42.4 in a plane transverse to the adjustment direction of the piston 43 (in particular perpendicular to the central longitudinal axis M of the cylinder 41) does not completely define the pressure chamber 41.6 on one side. Figure 5 As shown, there is a remaining surface, in particular an annular surface, which adjoins the projection surface radially on the outside.

[0061] The piston 43 can preferably be designed in the form of a sleeve as shown. Particularly preferably, the piston 43 is designed rotationally symmetrically. The piston 43 can form a guide surface 43.6 with its preferably cylindrical inner surface. The piston 43 can be adjusted and sealed on the bridge device 42 in the direction of the longitudinal center axis M by means of the guide surface 43.6. Preferably, the piston 43 extends through the aforementioned remaining surface.

[0062] The cylindrical outer surface of the piston 43 forms an outer wall 43 . 1 which can be guided in a sealing manner on an inner sliding surface 41 . 8 of the cylinder inner wall 41 . 1 .

[0063] Facing the bottom, in particular the cylinder bottom 41.4, the piston 43 has a shoulder which forms a support section 43.4. The support section 43.4 has an adjustment section 43.5 which is supported indirectly or directly on a spring 44 which can be designed as a helical spring. At the opposite end, the spring 44 is supported indirectly or directly, for example relative to the cylinder 41 or relative to the aforementioned sleeve part, preferably on the bottom or cylinder bottom 41.4.

[0064] The spring 44 is preferably at least partially accommodated in the low-pressure region 41.2. Likewise, the piston 43 can be arranged with its support section 43.4 in the low-pressure region 41.2.

[0065] exist Figure 5 4 shows the closed position of the pressure relief valve 40. In this state, the piston 43 rests on the valve seat 41.7 of the cylinder 41, wherein the piston 43 closes at least one outflow opening 41.5. The piston 43 is loaded onto the valve seat 41.7 by means of a spring 44. The valve seat 41.7 is arranged as a surrounding surface, preferably as an annular surface, in the region of the cylinder inner wall 41.4, as shown in FIG. Figure 5 shown.

[0066] like Figure 5 As shown, the piston 43 can be pressed against the valve seat 41.7 with a sealing section in the region of its end facing the pressure chamber 41.6. Preferably, the sealing section is arranged in the region of the end of the end side of the piston 43, such as Figure 5 shown.

[0067] The piston 43 has a piston pressure surface 43.2 which partially laterally delimits the pressure chamber 41.6. As here, the piston pressure surface 43.2 can preferably be designed in the form of a circumferential annular surface.

[0068] The pressure surface section 42.4 of the bridge device 42 and the piston pressure surface 43.2 of the piston 43 define a pressure chamber 41.6 on one side in a plane transverse to the adjustment direction of the piston 43, in particular perpendicular to the middle longitudinal axis M, and in a projection in a projection plane transverse to the adjustment direction of the piston 43. In this case, the projection surfaces do not overlap. However, these surfaces can also be partially overlapped. The surface normals on the projected piston pressure surface 43.2 and the pressure surface section 42.4 preferably point in the same direction, in this embodiment, in the direction opposite to the piston bottom 41.4.

[0069] The piston 43 also partially delimits the pressure chamber 41 . 6 radially on the outside with its inner wall 43 . 3 .

[0070] The pressure relief valve 40 is connected with a pressure chamber 41 . 6 to the pressure line 31 , ie to the pressure space 24 of the hydraulic cylinder 20 .

[0071] The low-pressure region 41.2 is connected to the surroundings via at least one passage 41.3. In this case, the ambient pressure of the air can be present in the low-pressure region 41.2 when an air-conducting connection is provided via at least one passage 41.3.

[0072] Alternatively, the low-pressure region 41.2 is connected to the chamber 26 of the hydraulic cylinder 20 via the line section 32 and the return line 33. The rod-side pressure of the hydraulic cylinder 20 (the pressure in the chamber 26) is thus present at the low-pressure region 41.2.

[0073] In normal crushing operation and with the crushing gap 15 set, the pressure relief valve 40 is located Figure 5 The position shown. The pressure of the pressure space 24 is also applied to the pressure chamber 41.6. If the crushing force increases during normal crushing operation, for example, harder stone is to be crushed, the transmission device 27 adjusts the piston rod 22 of the hydraulic cylinder 20 in the cylinder 25. As a result, the hydraulic cylinder-piston 23 is moved. If a critical limit pressure is not exceeded, the crushing gap 15 is widened by a certain distance, for example due to the compressibility of the fluid (especially hydraulic oil) and / or the elastically definable components, but without triggering the pressure relief valve 40. The system is thus adapted without interrupting the crushing operation.

[0074] Preferably, it is provided that a pressure regulating system is assigned to the chamber 26, i.e. the rod side of the hydraulic cylinder 20, which preloads the hydraulic fluid in this area. As a result, the closing force of the piston 43 caused by the spring 44 is supported when the low-pressure area 41.2 is hydraulically connected to the rod side. In addition, a pressure relief valve 40 is obtained that can be adapted and individually responded to the corresponding load conditions. If the pressure in the pressure chamber 24 of the hydraulic cylinder 20 increases when the load of the crusher is relatively high, but not yet in an overload state, the pressure on the rod side decreases, wherein the hydraulic cylinder piston 23 of the hydraulic cylinder 20 enters the pressure space 24. The pressure regulating system then fine-tunes the pressure on the rod side. The pressure regulation has a limited capacity in this case in order to maintain the pressure. The pressure regulation on the pressure relief valve 40 thus causes the piston 43 of the pressure relief valve 40 to remain in the closed position. The crushing operation can therefore continue in this load condition.

[0075] If an overload condition occurs at this time, the pressure on the rod side drops rapidly and the pressure control unit no longer maintains the pressure on the rod side. This pressure drop, combined with the sudden increase in pressure in the pressure space 24 and in the pressure chamber 41.6, causes the piston 43 to move in the direction of the longitudinal center axis M. As a result, at least one outflow opening 41.5 of the pressure relief valve 40 is released. The fluid held in the pressure chamber 41.6 is unloaded via the outflow opening 41.5. In this case, the at least one outflow opening 41.5 can be opened into the line section 32.

[0076] If the low-pressure region 41.2 is in air-conducting connection with the surroundings, the pressure relief valve opens when the opening force acting on the piston 43 along the central longitudinal axis M due to the pressure prevailing in the pressure chamber 41.6 and the active piston pressure surface exceeds the closing force acting in the opposite direction. The closing force is the spring force of the spring 44 plus the pressure calculated from the surrounding pressure and the limiting surface of the piston 43 projected in a plane transverse to the direction of movement of the piston 43, by means of which the low-pressure region 42.6 is delimited.

[0077] The fluid flowing out of the pressure relief valve 40 reaches the chamber 26 of the hydraulic cylinder 20. Since the chamber 26 cannot accommodate all of the displaced fluid, a portion of the fluid is discharged into the oil tank 36. For this purpose, the line section 32 is connected to the overpressure valve 60 via the collecting line 34. Following the pressure relief valve 60, the excess fluid is conveyed to the oil tank 36 via the discharge line 35. The overpressure valve 60 is designed so that it opens only after a pressure threshold to establish a connection with the oil tank 36. For example, the overpressure valve 60 can be constructed according to the pressure relief valve 40 to reduce the cost of components.

[0078] After the overload situation has ended, hydraulic fluid is conveyed into the pressure chamber 24 of the hydraulic cylinder 20 via the regulating system until the desired width of the crushing gap 15 is again present. In this case, the hydraulic fluid can be returned from the tank 36 to the pressure chamber 24 by means of a pump (not shown).

Claims

1. A crusher for mineral or recycled materials, comprising a crushing unit (10) having a first crushing body (11), wherein: A movable second crushing body (14) is assigned to the first crushing body (11), wherein a crushing gap (15) is formed between the crushing bodies (11, 14), wherein a hydraulic cylinder (20) is coupled to one of the crushing bodies (11, 14), the hydraulic cylinder being arranged and configured to allow a movement of the coupled crushing body (11, 14) in a deflection movement that increases the width of the crushing gap (15), wherein a pressure space (24) of the hydraulic cylinder (20) is connected to a pressure chamber (41.6) of a pressure relief valve (40) of an overload triggering device (30), wherein the ... In the embodiment of the present invention, the piston (43) of the pressure relief valve (40) is adjustable between a closed position and an open position, wherein in the closed position a connection of a conducting fluid between the pressure chamber (41.6) and the pressure equalization region (B) is blocked and in the open position the connection of the conducting fluid is at least partially released, and wherein the piston (43) has at least one piston pressure surface (43.2) by means of which the piston (43) delimits the pressure chamber (41.6) transversely to the adjustment direction of the piston (43) in the closed position, It is characterized in that, in the closed state of the pressure relief valve, the projection of one piston pressure surface (43.2) or multiple piston pressure surfaces (43.2) of the piston (43) in a projection plane transverse to the adjustment direction of the piston (43) only defines a part of the pressure chamber (41.6) transverse to the adjustment direction of the piston (43).

2. The crusher according to claim 1, characterized in that: A bridging device (42) is provided, the piston (43) can be adjusted relative to the bridging device, the bridging device (42) has at least one pressure surface segment (42.4), the pressure surface segment defines the pressure chamber (41.6) transversely to the adjustment direction of the piston (43), and the projection of one pressure surface segment (42.4) or multiple pressure surface segments (42.4) in the projection plane along the direction of the adjustment movement of the piston (43) does not cover or does not completely cover the one piston pressure surface (43.2) or multiple piston pressure surfaces (43.2).

3. The crusher according to claim 2, characterized in that: The surface normals on the projections of the piston pressure surface (43.2) or the multiple piston pressure surfaces (43.2) and the pressure surface section (42.4) or the multiple pressure surface sections (42.4) point in the same direction.

4. A crusher according to any one of claims 1 to 3, characterized in that The piston (43) has a cylindrical outer wall (43.1), by means of which the piston is disposed opposite a cylinder inner wall (41.1) of a cylinder (41) which forms the pressure chamber (41.6), and the piston (43) is designed in an annular shape and has an inner wall (43.3).

5. The crusher according to claim 4, characterized in that The piston has a cylindrical inner wall (43.3).

6. A crusher according to any one of claims 1 to 3, characterized in that The piston (43) is supported by a supporting section (43.4) outside the pressure chamber (41.6) relative to a spring (44), wherein the spring (44) introduces a preload into the piston (43) in the direction of the closed position of the piston (43) so that the piston (43) is preloaded relative to the valve seat (41.7).

7. A crusher according to any one of claims 1 to 3, characterized in that The bridge device (42) is connected indirectly or directly to the cylinder of the pressure relief valve (40) by means of a connecting section (42.1).

8. The crusher according to claim 7, characterized in that The bridge device (42) is connected to the cylinder of the pressure relief valve (40) in a fixed or adjustable manner by means of a connecting section (42.1).

9. The crusher according to claim 7, characterized in that: The bridge device (42) is movable in the direction of the adjustment movement of the piston (43) and / or transversely to the adjustment direction of the piston (43).

10. The crusher according to any one of claims 1 to 3, characterized in that The bridge device (42) holds the head (42.3) on the carrier (42.2) in the cylinder interior, and the head (42.3) forms or carries the at least one pressure surface section (42.4).

11. A crusher according to any one of claims 1 to 3, characterized in that The piston (43) delimits a low-pressure region (41.2) of the pressure relief valve (40) relative to the pressure chamber (41.6), and the piston (43) moves with an adjustment section (43.5) in the low-pressure region (41.2) when it is adjusted from a closed position to an open position.

12. The crusher according to claim 11, characterized in that The low-pressure region (41.2) is in air-conducting connection with the surroundings via at least one passage (41.3) or is hydraulically connected to a hydraulic component.

13. The crusher according to claim 12, characterized in that The low-pressure region (41.2) is in air-conducting connection with the surroundings via at least one passage (41.3) or is hydraulically connected to the hydraulic cylinder (20).

14. The crusher according to claim 12, characterized in that The low-pressure region (41.2) is in air-conducting connection with the surroundings via at least one passage (41.3) or is hydraulically connected to a chamber that accommodates a piston rod (22) of the hydraulic cylinder (20).

15. A crusher according to any one of claims 1 to 3, characterized in that The cylinder body (41) of the pressure relief valve (40) has at least one outflow opening (41.5) in the area of ​​the pressure chamber (41.6), which is covered by a body area of ​​the piston (43) connected to the piston pressure surface (43.2) in the closed position of the piston (43) and is at least partially released in the open position of the piston (43), and the outflow opening (41.5) is indirectly or directly connected to the oil tank (36) via a line section (32) and / or is indirectly or directly connected to a chamber (26) accommodating a piston rod (22) of the hydraulic cylinder (20), i.e., the rod side of the hydraulic cylinder 20, via a return line (33).

16. A crusher according to any one of claims 1 to 3, characterized in that A projection of a piston pressure surface (43.2) or multiple piston pressure surfaces (43.2) of the piston (43) in the closed plane transversely to the adjustment direction of the piston (43) covers a projection of a piston pressure surface (43.2) or multiple piston pressure surfaces (43.2) of the piston (43) in the closed plane transversely to the adjustment direction of the piston (43) plus at least 5% and a maximum of 80% of a pressure surface section (42.4) of the bridging device (42).

17. The crusher according to claim 16, characterized in that A projection of a piston pressure surface (43.2) or multiple piston pressure surfaces (43.2) of the piston (43) transversely to the adjustment direction of the piston (43) in the closed plane covers a projection of a piston pressure surface (43.2) or multiple piston pressure surfaces (43.2) of the piston (43) transversely to the adjustment direction of the piston (43) in the closed plane plus at least 10% and a maximum of 50% of a pressure surface section (42.4) of the bridging device (42).

18. A crusher according to any one of claims 1 to 3, characterized in that A maximum of 50% of the projection of a piston pressure surface (43.2) or multiple piston pressure surfaces (43.2) of the piston (43) in the closing plane transversely to the adjustment direction of the piston (43) is located in the area of ​​the outflow opening (41.5).

19. The crusher according to claim 18, characterized in that A maximum of 25% of the projection of a piston pressure surface (43.2) or multiple piston pressure surfaces (43.2) of the piston (43) in the closing plane transversely to the adjustment direction of the piston (43) is located in the area of ​​the outflow opening (41.5).

20. A crusher according to any one of claims 1 to 3, characterized in that The crusher is a rotary impact crusher, a jaw crusher, a cone crusher or a roll crusher.

21. A crusher according to any one of claims 1 to 3, characterized in that The first crushing body (11) is a rotor or a crushing jaw.

22. A crusher according to any one of claims 1 to 3, characterized in that The second crushing body (14) is an impact rocker or a crushing jaw.

23. A crusher according to any one of claims 1 to 3, characterized in that In the closed state of the pressure relief valve, a projection of a piston pressure surface (43.2) or multiple piston pressure surfaces (43.2) of the piston (43) in the closing plane only defines a part of the pressure chamber (41.6) transversely to the adjustment direction of the piston (43).

24. Method for operating a crusher for mineral or recycling material, the crusher having a crushing unit (10) with a first crushing body (11), wherein: A movable second crushing body (14) is assigned to the first crushing body (11), wherein a crushing gap (15) is formed between the crushing bodies (11, 14), wherein a hydraulic cylinder (20) is coupled to one of the crushing bodies (11, 14), wherein the hydraulic cylinder performs a deflection movement in an overload operating state to allow a movement of the coupled crushing body (11, 14) to increase the width of the crushing gap (15), wherein the pressure space (24) of the hydraulic cylinder (20) is connected to a pressure chamber (41.6) of a pressure relief valve (40) of an overload triggering device (30), wherein the piston (43) of the pressure relief valve (40) is adjustable between a closed position and an open position, wherein in the closed position a connection for conducting a fluid between the pressure chamber (41.6) and the pressure equalization region (B) is blocked and in the open position the connection for conducting a fluid is at least partially released, and wherein the piston (43) has at least one piston pressure surface (43.2) by means of which the piston (43) in the closed position delimits the pressure chamber (41.6) transversely to an adjustment direction of the piston (43), It is characterized in that the projection of one piston pressure surface (43.2) or multiple piston pressure surfaces (43.2) of the piston (43) in a projection plane transverse to the adjustment direction of the piston only limits a part of the pressure chamber (41.6) transverse to the adjustment direction of the piston (43), and when the pressure threshold in the pressure space (24) of the hydraulic cylinder (20) is exceeded, the piston (43) of the pressure relief valve (40) moves and when the pressure is lower than the relief pressure in the pressure chamber (41.6), the piston (43) moves back to the closed position with the help of a spring (44).

25. The method according to claim 24, characterized in that The crusher is designed according to any one of claims 1 to 23.

26. The method according to claim 24 or 25, characterized in that The crusher is a rotary impact crusher, a jaw crusher, a cone crusher or a roll crusher.

27. The method according to claim 24 or 25, characterized in that The first crushing body (11) is a rotor or a crushing jaw.

28. The method according to claim 24 or 25, characterized in that The second crushing body (14) is an impact rocker or a crushing jaw.

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