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 crushing bodies a crushing gap is formed, a hydraulic cylinder is coupled to one of the crushing bodies and is arranged and configured to allow a movement of the coupled crushing body that increases the width of the crushing gap during a deflection movement, the pressure space of the hydraulic cylinder being coupled to a pressure chamber of a pressure relief valve of an overload trigger device (30), the piston of which can be adjusted between a closed position and an open position, the piston has a closed position in which the fluid-conducting connection between the pressure chamber and the pressure compensation region is blocked and an open position in which the fluid-conducting connection is released, the piston having a piston pressure surface, by means of which the piston defines the pressure chamber in the closed position. The piston has a surface region on the side facing away from the pressure chamber, which in the piston closed position defines a chamber region transversely to the piston adjustment direction in order to introduce a closing force into the piston in the chamber region under the action of pressure.

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 second movable 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 to allow a movement of the coupled crushing body in a deflection movement 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 can be adjusted 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. In particular, there is a risk of damaging the crusher. 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 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 the crushing gap is simultaneously kept as constant as possible in normal operation and in crushing operation.

[0009] This object is achieved in that the piston has a surface area on its side facing away from the pressure chamber, which surface area limits the chamber area transversely to the adjustment direction of the piston in the closed position of the piston so that under the action of pressure, a closing force is introduced into the piston in the chamber area in the direction of the closed position.

[0010] In the closed position of the piston, an opening force is caused in the opening direction of the piston. The opening force is calculated from the pressure in the pressure chamber and the effective piston pressure surface that defines the pressure chamber, and the pressure is applied to the piston pressure surface. A closing force is caused in the closing direction of the piston. The closing force is calculated from the pressure in the chamber area and the surface content of the surface area that defines the chamber area, and the pressure in the chamber area is applied to the surface area. In other words, at least a part of the opening force can be compensated by means of the closing force. As a result, the piston can be designed particularly simply, so that a small mass to be moved is obtained. A pressure relief valve is thus provided, which can open quickly in the event of an overload. This achieves a short response performance of the pressure relief valve in the event of an overload. Advantageously, it can be provided that the mass of the piston (in grams) is proportional to the rated opening area (in mm 2 The ratio of φ (in units) is selected between 0.03 and 0.15. The set opening area is the area enclosed by the surrounding surface of the valve seat, against which the piston rests in the closed position.

[0011] It is preferably provided that in the closed position the pressure in the chamber region is lower than in the pressure chamber.

[0012] More preferably, the pressure of the hydraulic fluid is applied to the pressure chamber and to the chamber region, ie the pressure chamber and the chamber region are filled with the hydraulic fluid.

[0013] Particularly preferably, the chamber region is connected to a chamber of the hydraulic cylinder which accommodates the piston rod of the hydraulic cylinder (rod side of the hydraulic cylinder). In this case, it can be provided in particular that a pressure regulator is assigned to the rod side of the hydraulic cylinder, which is provided and designed to fine-tune the pressure on the rod side of the hydraulic cylinder when adjusting the hydraulic cylinder piston of the hydraulic cylinder.

[0014] A preferred variant of the invention is designed such that the balancing pressure surface is indirectly or directly connected to the piston of the pressure relief valve, the balancing pressure surface is held outside the pressure chamber in an external pressure region, and the balancing pressure surface is designed and arranged such that, under the effect of the pressure in the external pressure region, a closing force is introduced into the piston in the direction of the closed position. This measure additionally supports the closing force. An additional closing force is calculated from the pressure at the balancing pressure surface and the size of the balancing pressure surface, which additional closing force acts in the closing direction.

[0015] For example, it can be provided that in the closed position of the piston the pressure in the external pressure region is lower than in the pressure chamber and that the external pressure region is in an air-conducting connection with the surroundings, so that atmospheric pressure is present there. This results in a simple design with low component and installation costs. Alternatively, the pressure of the hydraulic fluid can act on the equilibrium pressure surface in the closed position of the piston. It can be provided that the pressure in the external pressure region is lower than the pressure in the pressure chamber. However, the pressure in the pressure chamber can also be greater than or equal to the pressure in the external pressure region.

[0016] It is preferably provided that the chamber region is spatially separated from the external pressure region.

[0017] By suitably selecting the size of the piston pressure surface delimiting the pressure chamber, the size of the surface area delimiting the chamber area and the size of the equilibrium pressure surface acted upon by the pressure in the external pressure area, the closing force can be influenced in a targeted manner, while at the same time achieving a simple design of the piston.

[0018] Compared to the known implementations in the prior art, this implementation makes the piston pressure surface and the effective surface for introducing forces for adjusting the piston and for triggering the pressure relief valve smaller. Correspondingly, less force is required to adjust the piston in the event of an overload. This generates a controllable force on the piston in order to keep the pressure relief valve in the closed state during normal crusher operation, which force can be easily obtained outside the pressure chamber of the pressure relief valve. In addition, this design makes it possible to reduce the mass of the piston and the accelerated components of the pressure relief valve. This further improves the response behavior in the event of an overload.

[0019] A simple construction is achieved when the adjusting element, in particular a piston rod, is coupled to the piston, which forms a compensating pressure surface outside the pressure chamber. If the piston rod is guided through the chamber area and coupled to the piston, the cross section of the piston rod simultaneously reduces the active surface area in the chamber, whereby the surface area can be influenced in a targeted manner via the cross section of the piston rod.

[0020] It is provided that a spring, in particular a mechanical spring, acts indirectly or directly on the piston, and in the closed position of the piston the spring exerts a closing force on the piston in the closing direction, so that in normal operation of the crusher (i.e. in the absence of an overload) the crushing gap remains essentially constant. By suitable dimensioning of the spring the closing force can be influenced such that an overload is not accidentally triggered when hard stone material has to be crushed in the crushing chamber.

[0021] If the spring is arranged in the external pressure region, in particular in the cylinder of the pressure relief valve, a compact design is achieved for the pressure relief valve.

[0022] When the pressure balance surface is formed by the pressure piece of the piston and the spring is supported on the pressure piece, the spring force can be directly transmitted via the piston, which improves functional reliability. Preferably, it can be provided that the pressure piece has an area that projects radially outwardly above the pressure balance surface, on which the spring is supported, so that good support and force transmission are provided for the spring.

[0023] A particularly preferred variant of the invention provides that in the closed position of the piston of the pressure relief valve the pressure of the hydraulic fluid acts on the surface area, wherein preferably provision is made for the pressure in the chamber area to be lower than the pressure in the pressure chamber.

[0024] In addition, it can be provided that the chamber area of ​​the pressure relief valve is connected to the chamber of the hydraulic cylinder in a hydraulic transmission connection, which chamber accommodates the piston rod of the hydraulic cylinder and holds the hydraulic fluid in the chamber. The chamber can also be called the rod side of the hydraulic cylinder. By including the rod side in the overload triggering device, the structural cost is first reduced, because there is no need to replenish oil separately. If a pressure adjustment device is assigned to the rod side, the pressure adjustment device fine-adjusts the pressure in the chamber, and an adaptive pressure relief valve is provided. In normal operation of the crusher, that is, when there is no overload condition, the pressure relief valve can compensate for the fluctuations of the crushing force that occur in the crushing gap. If harder stones reach the crushing gap, the hydraulic cylinder-piston and the piston rod of the hydraulic cylinder are adjusted. Because the pressure adjustment fine-adjusts the pressure on the rod side, the piston of the pressure relief valve remains in the closed position. Inadvertent triggering of the pressure relief valve is thus prevented. The pressure relief valve can therefore be adapted to different load conditions. If, however, the hydraulic cylinder-piston is adjusted quickly in an overload situation, the pressure adjustment device no longer replenishes the pressure on the rod side. At this time, a pressure drop occurs, thereby triggering the pressure relief valve.

[0025] In order to prevent the piston of the pressure relief valve from tilting in its cylinder, provision can be made for a surface area of ​​the pressure relief valve to form an annular surface which preferably extends concentrically around the adjusting element, in particular the piston rod.

[0026] Stable guidance of the adjusting element, in particular the piston rod, in the cylinder of the pressure relief valve can be simply achieved in that the adjusting element, in particular the piston rod, extends through a chamber area in the closed position of the piston, wherein it is preferably provided that the chamber area is defined by a piston guide at a distance from the piston, wherein the piston guide has a notch, through which the adjusting element, in particular the piston rod, passes in a sealed manner by means of a guide surface.

[0027] In order to be able to quickly and effectively reduce the pressure in the pressure chamber of the pressure relief valve in an overload situation, it can be provided that the piston of the pressure relief valve has a piston head, an adjusting element, in particular a piston rod, is coupled to the piston head, preferably is connected to the piston head in one piece, and the piston head can be moved from its closed position into the chamber area, and it is preferably provided that the piston head at least partially passes by at least one outflow outlet when it moves from the closed position into the open position or the partially open position to establish a hydraulically conductive connection between the pressure chamber and the pressure equalization area.

[0028] In an improved solution of the present invention, it can be provided that the unloading piston is adjustable in the chamber area of ​​the pressure relief valve, wherein the unloading piston can be adjusted between a closed position and an open position, wherein in the closed position, the connection of the guiding fluid between the pressure chamber and the unloading balance area is blocked and in the open position, the connection of the guiding fluid is at least partially released, so that the unloading piston has at least one piston pressure surface, by means of which the unloading piston defines the chamber area transversely to the adjustment direction of the unloading piston in the closed position, and due to the pressure increase of the pressure in the hydraulic cylinder, the piston and the unloading piston are opened in sequence. If the piston of the pressure relief valve is opened to reduce the pressure in an overload situation, it can be ensured by this implementation that the pressure is additionally reduced via the unloading piston. This is particularly advantageous when there is still a relatively high pressure in the pressure balance area after the piston is opened, and this relatively high pressure can then be reduced to the pressure relief area by opening the unloading piston. For example, the pressure relief area can be connected to an oil tank, and excess hydraulic oil is discharged into the oil tank.

[0029] It is conceivable that in this case the pressure balance region is connected to the rod side of the hydraulic cylinder. In the case of overload, the excess oil that cannot be accommodated by the smaller volume caused by the piston rod of the hydraulic cylinder on the rod side can be output into the oil cylinder via the pressure relief region.

[0030] The response performance of this pressure relief valve can be improved in the following way: in the closed state of the unloading piston, the projection of one or more piston pressure surfaces of the unloading piston in a projection plane transverse to the adjustment direction of the unloading piston only limits a part of the chamber area transverse to the adjustment direction of the unloading piston. 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 schematic diagram shows the overload triggering device.

[0035] Figure 5 The schematic diagram shows the pressure relief valve of the overload trigger device.

[0036] Figure 6 Another embodiment of a pressure relief valve of an overload triggering device and

[0037] Figure 7 A further variant of the invention is shown in a schematic diagram. DETAILED DESCRIPTION

[0038] 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.

[0039] 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.

[0040] 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.

[0041] 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.

[0042] For example, in the lower impact rocker 14 Figure 2 and Figure 3When 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.

[0043] 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.

[0044] like Figure 2 and Figure 3 As shown, the hydraulic cylinder 20 has a cylinder body 25, in which the hydraulic cylinder piston 23 can move. 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, and the coupling part has a bearing part. By means of the bearing part, the coupling part 21 is connected to the bearing 14.2 of the crushing body 14. 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.

[0045] 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.

[0046] 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 the crushing gap 15 needs to be set wider starting from the position shown in FIG. 2 , hydraulic fluid is released from the pressure space 24. As a result, the hydraulic cylinder-piston 23 moves further into the cylinder body 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 body 25. As a result, the crushing body 14 is pivoted clockwise, so that a narrowing of the crushing gap 15 is achieved.

[0047] 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.

[0048] The invention can also be implemented on different rock crushers, for example on a jaw crusher, a cone crusher or a roller crusher.

[0049] 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.

[0050] 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.

[0051] 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.

[0052] The pressure chamber 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 .

[0053] Reference below Figure 5A possible variant of the pressure relief valve 40 is described. As shown in this schematic diagram, the pressure relief valve 40 has a cylinder 41 with a cylinder wall. A cylinder bottom 41.4 is coupled to the cylinder wall. The cylinder wall forms the cylinder inner wall 41.1. The cylinder bottom 41.4 has at least one passage 41.3. However, it is also conceivable that such a passage 41.3 is arranged in the cylinder wall. Via the passage 41.3, a connection between the external pressure region 41.2 and the surrounding environment can be established. The external pressure region 41.2 forms a space in the cylinder 41.

[0054] Figure 5 It is shown that the external pressure region 41.2 is defined by the cylinder bottom 41.4 and the cylinder inner wall 41.1 of the cylinder 41. In addition, the piston guide 41.9 defines the external pressure region 41.2 on the side facing away from the cylinder bottom 41.4. A spring 44 is arranged in the external pressure region 41.2. The spring 44 can be designed as a helical spring as shown in the figure. However, it is also conceivable that other mechanical springs, such as a spiral spring or a combination of mechanical spring elements form the spring 44.

[0055] The piston 50 is arranged in the inner space of the cylinder 41. The piston 50 has a pressure piece 55. The piston 50 is supported relative to the spring 44 by means of the pressure piece 55. In addition, the spring 44 can be supported on the cylinder bottom 41.4 or at another suitable position in the cylinder 41.

[0056] Figure 5 The piston 50 shown can have a piston head 51. A piston rod 52 is connected to the piston head 51, preferably in one piece.

[0057] The piston rod 52 may be Figure 5 Shown is a cylindrical outer contour.

[0058] The piston rod 52 is guided linearly in the cylinder 41 along the central longitudinal axis M of the cylinder 41 at the piston guide 41. In this case, the piston rod 52 can have an outer guide surface 53, which is preferably formed by the cylindrical outer contour of the piston rod 51. The guide surface 53 passes through the recess 41.10 of the piston guide 41.9 in a sealing manner and is guided in the recess 41.10.

[0059] according to Figure 5 The chamber region 41.11 can be designed separately from the external pressure region 41.2 in the cylinder 41. The chamber region 41.11 can preferably be delimited by means of a piston guide 41.9 on the side of the chamber region facing the cylinder bottom 41.4 in order to achieve a compact design.

[0060] The chamber area 41.11 is advantageously delimited radially on the outside by the inner wall 41.8 of the cylinder wall. Figure 5In the closed position shown, the chamber region 41.11 can be closed on its side facing away from the cylinder bottom 41.4 by the piston head 51. In this case, the surface region 58 of the piston head 51 delimits the chamber region 41.11 on the side facing away from the cylinder bottom 41.4.

[0061] like Figure 5 As shown, the cylinder wall of the cylinder 41 can have at least one outflow opening 41.5. The outflow opening 41.5 establishes a guide connection between the pressure equalization region B and the chamber region 41.11.

[0062] exist Figure 5 In the closed position shown, the piston head 51 rests with its valve face 59 in close contact with the valve seat 41 . 7 of the cylinder 41 .

[0063] Advantageously, in Figure 5 In the closed position shown, the piston head 51 delimits the pressure chamber 41.6 with the piston pressure surface 56. The piston pressure surface 56 can be connected to the valve seat 41.7.

[0064] The pressure chamber 41 . 6 is connected to the pressure space 24 of the hydraulic cylinder 20 via the pressure line 31 and is in fluid-conducting connection therewith.

[0065] The piston pressure surface 56 of the adjusting device which delimits the pressure chamber 41.6 transversely to the piston 50 is the piston 51 in the closed position of the pressure relief valve 40. Figure 5 The surface to which the pressure in the pressure chamber 41.6 is applied in the closed position shown. Here, the surface is constructed and arranged so that, under the action of the pressure in the pressure chamber 41.6, the opening force is directed in the direction of the open position (in Figure 5 The piston 50 is introduced from bottom to top into the piston 50. The piston pressure surface 56, which is projected into the projection plane in the direction of the center longitudinal axis M, generates an opening force in the direction of the center longitudinal axis M in cooperation with the pressure in the pressure chamber 41.6.

[0066] Further surfaces of the piston 50 which are not suitable for introducing an opening force into the piston 50 are not piston pressure surfaces 56 in the present invention.

[0067] The surface area 58 which delimits the chamber area 41.4 transversely to the adjustment direction of the piston 50 is designed and arranged in the sense of the invention to direct the closing force in the direction of the closed position (in Figure 5 The surface of the surface area 58 projected into the projection plane in the direction of the middle longitudinal axis M together with the pressure in the chamber area 41.11 generates a closing force acting in the direction of the middle longitudinal axis M.

[0068] Other surfaces of the piston 50 which are not suitable for introducing a closing force into the piston 50 are not surface regions 58 of the piston 50 within the meaning of the present invention.

[0069] Figure 5 It is shown that the piston 50 is guided into the external pressure region 41.2 by means of the adjusting element 54. In the external pressure region, the adjusting element 54 forms a compensating pressure surface 57. The compensating pressure surface 57 forms a surface which delimits the external pressure region 41.2 transversely to the adjustment direction of the piston 50.

[0070] The balancing pressure surface 57 is constructed and arranged to direct the closing force in the direction of the closed position (at Figure 5 The surface of the balancing pressure surface 57 projected into the projection plane in the direction of the middle longitudinal axis M together with the pressure in the outer pressure region 41.2 generates a closing force acting in the direction of the middle longitudinal axis M. It can be clearly seen that there are other surface areas on the pressure piece 55. However, these surface areas are not suitable for introducing a closing force into the piston 50 and therefore cannot be understood as balancing pressure surfaces 57.

[0071] The pressure relief valve 40 is connected to the overload triggering device 30 , so that the pressure space 24 of the hydraulic cylinder 20 is in fluid-conducting connection with the pressure chamber 41 . 6 .

[0072] The chamber region 41 . 11 is in fluid-conducting connection with the rod side 26 of the hydraulic cylinder via the return line 33 .

[0073] Advantageously, the outer pressure region 41 . 2 is connected to the surrounding atmosphere, ie atmospheric pressure prevails there.

[0074] During normal crushing operation, ie when there is no overload, the pressure relief valve 40 is Figure 5 The closed position is shown in FIG.

[0075] In the overload situation, the pressure in the pressure space 24 of the hydraulic cylinder 20 increases sharply, that is, the piston rod 22 moves into the cylinder body 25 of the hydraulic cylinder 20. This pressure is then present in the pressure chamber 41.6. As a result, the piston 50 overcomes the prestress of the spring 44 and moves from Figure 5 4. The closed position shown in FIG. 4 is moved out and the valve seat 57 is released. As a result, the hydraulic fluid can pass from the pressure chamber 41.6 into the pressure balance region B via the outflow opening 41.5.

[0076] The unloaded hydraulic fluid is conducted to the rod side 26 of the hydraulic cylinder 20 via the line section 32 and the return line 33. The excess hydraulic fluid that cannot be accommodated on the rod side 26 is conducted via the collecting line 34 and the now open pressure relief valve 60 into the tank 36. After the overload situation has ended, the pressure chamber 24 can be filled again with this hydraulic fluid in the tank 36. The hydraulic cylinder piston 23 is then set back into the initial position, so that the hydraulic cylinder 20 is again in its operating position.

[0077] If the pressure in the pressure chamber 41.6 decreases, the spring 44 sets the piston 50 of the pressure relief valve 40 back to the Figure 5 Shown in the closed position.

[0078] exist Figure 6 Another variant of the pressure relief valve 40 according to the present invention is shown in FIG. Figure 5 The function of the pressure relief valve 40 is based on Figure 4 The function of the overpressure valve 60 is integrated into the pressure relief valve 40 .

[0079] and Figure 5 In comparison, Figure 6 The same reference numerals are assigned to the same components in the embodiment, so in order to avoid repetition, reference can be made to the above embodiment. Figure 5 and Figure 6 The difference between two variants of the pressure relief valve.

[0080] like Figure 6 As shown, a cylinder 41 with a cylinder bottom 41.4 and a cylinder wall is used again. A spring 44 is arranged in the external pressure area 41.2, which supports the piston 50. In this embodiment, the connecting section 42.1 is disconnected in the external pressure area, which accommodates the spring 44. The area accommodating the spring 44 is connected to the surroundings via at least one passage 41.3. The remaining space of the external pressure area 41.2 is also connected to the surroundings via at least one passage 41.3. In addition, another spring 44.1 is arranged here.

[0081] Preferably, the connecting section is part of a bridge device 42 arranged in the cylinder 41, which bridge device forms the piston guide 41.9. The bridge device 42 again separates the chamber area 41.11 from the external pressure area 41.2.

[0082] According to Figure 5 Unlike the embodiment of the present invention, the bridge device 42 does not cover the entire cross section of the inner space of the cylinder 41. Instead, a relief piston 43 is arranged between the radial outer environment of the bridge device 42 and the cylinder inner wall 41.1. The relief piston can be configured as a cylindrical sleeve as shown in the present embodiment.

[0083] For guiding the relief piston 43 , the bridge device 42 has a head 42 . 3 which can be connected in one piece to the connecting section 42 . 1 via a carrier 42 . 2 .

[0084] The head 42.3 is provided with a guide on the radially outer side, on which the unloading piston 43 is guided in a sealing manner by means of a guide surface 43.6. The unloading piston 43 has an outer wall 43.1 on the radially outer side, which is guided in a sealing manner on the cylinder inner wall 41.1.

[0085] The unloading piston 43 can be designed so that it partially defines the chamber area 41.11 with its inner wall. Figure 6 In the closed state shown, the inner wall 43.3 covers the fluid outlet 41.12. The fluid outlet 41.12 can be connected to the oil tank 36 via a connecting line (not shown).

[0086] Figure 6 It is also shown that the unloading piston 43 can enter the external pressure area 41.2 with a support section 43.4. The support section 43.4 has an adjustment section 43.5. The unloading piston 43 is supported on another spring 44.1 with this adjustment section 43.5. The other spring 44.1 is supported relative to the cylinder bottom 41.4 or another component of the cylinder body 41, wherein the other spring 44.1 applies the prestress along the Figure 6 The orientation of the closed position shown is imposed on the unloading piston 34 .

[0087] In the closed position, the unloading piston 43 is held sealingly on the other valve seat 41.13 of the cylinder 41. Figure 6 In this closed state, the unloading piston 43 unlocks the connection between the fluid outlet 41 . 12 and the chamber area 41 . 11 .

[0088] The unloading piston 43 has at least one pressure relief surface 43.7 in the region of the support section 43.4 and a piston pressure surface 43.2 is provided on the unloading piston 43 facing the chamber region 41.11. Preferably, the piston pressure surface 43.2 and / or the pressure relief surface 43.7 are configured as circumferential annular surfaces. Particularly preferably, the two surfaces are identical, i.e., have identical surface contents.

[0089] The pressure in the chamber region 41.11 is applied to the piston pressure surface 43.2, and the pressure of the external pressure region 41.2 is applied to the pressure relief surface 43.7.

[0090] The piston pressure surface 43.2 of the unloading piston 43, which defines the chamber area 41.4 transversely to the adjustment direction of the unloading piston 50, can be constructed and arranged as shown so that the opening force is directed in the direction of the opening movement (in Figure 5The piston pressure surface 43.2 is projected into the projection plane in the direction of the middle longitudinal axis M and the pressure in the chamber area 41.11 jointly generates an opening force acting in the direction of the middle longitudinal axis M.

[0091] The pressure relief surface 43.7 defining the external pressure region 41.2 transversely to the adjustment direction of the unloading piston 50 can be constructed and arranged as shown in the drawings so that the closing force is directed in the direction of the closed position (at Figure 5 The pressure relief surface 43.7 is projected into the projection plane in the direction of the middle longitudinal axis M and the pressure in the external pressure area 41.2 jointly generates a closing force acting in the direction of the middle longitudinal axis M.

[0092] In the normal operation of the above crusher, the pressure relief valve 40 is in Figure 6 Shown in the closed position.

[0093] In the case of overload, the piston 50 moves into the chamber area 41.11 with its piston head 51, overcoming the prestress of the spring 44. In this case, the connection between the pressure chamber 41.6 and the pressure equalization area B is opened (see above). If the pressure at the unloading piston 43 exceeds the force acting on it for closing, the unloading piston 43 also opens and releases the connection between the chamber area 41.11 and the pressure relief area C. As a result, the hydraulic fluid can flow out of the chamber area 41.11 into the oil tank 43.

[0094] When the closing force exceeds the opening force again after the overload condition ends, the unloading piston 43 and the piston 50 close and enter again. Figure 6 Shown in the closed position.

[0095] Figure 7 Another variant of the invention is shown. Identical components are provided with the same reference numerals here, so that reference is made to the above description to avoid repetitions.

[0096] As shown in the schematic diagram, a pressure relief valve 40 is used which has a cylinder 41. The cylinder 41 in turn has a cylinder inner wall 41.1.

[0097] An external pressure region 41 . 2 is provided corresponding to the cylinder 41 . The external pressure region 41 . 2 is spatially connected to the conversion hydraulic system 80 .

[0098] The cylinder 41 has a chamber area 41.11, which has at least one outflow opening 41.5. The piston 50 is arranged in the cylinder 41 so that it can be adjusted. Figure 6In the closed position shown, the piston 50 rests with the valve surface 59 on the valve seat 41.7 of the cylinder 41. The inner wall 41.8 at least partially forms a sliding surface on which the bridge device 42 is adjustable.

[0099] The bridge device 42 can be formed, for example, by a control piston 70 or can have a control piston, such as Figure 7 shown.

[0100] The bridge device 42, which can be designed in particular in the form of a control piston 70, is guided adjustably in the cylinder 41. For this purpose, the control piston 70 or the bridge device 42 has a head 71, which is guided at its outer circumference in a sealing manner on the inner wall 41.8 of the cylinder 41 designed as a sliding surface.

[0101] The control piston 70 has a chamber 73 which is spatially connected to the external pressure region 41 . 2 via at least one passage 72 .

[0102] like Figure 6 As shown, the control piston 70 can have a connecting section 74 which projects into the chamber region 41 . 11 . The connecting section 74 extends into the chamber region 41 . 11 in particular in the direction of the central longitudinal axis. The connecting section 74 can at least partially form the chamber 73 .

[0103] The control piston 70 may have a guide 75 which may be formed in particular by a recess 76. The guide 75 accommodates the piston rod 52 of the piston 50, wherein the piston rod 52 may be coupled directly or indirectly to the piston 50. The piston 50 is preferably guided in the recess 76 in a sealing manner.

[0104] According to a possible variant, the control piston 70 can form a housing 77. The stop 50.2 of the piston 50 is accommodated in this housing 77. The stop 50.2 can have a first stop 50.1 and a second stop 50.3. The stops 50.1 and 50.3 serve to limit the movement of the piston 50 relative to the control piston 70. For this purpose, a counter stop is arranged on the control piston 70. One of the counter stops can be formed by a removable cover 78.1, which allows the piston 50 to be mounted on the control piston 70. The cover 78.1 can form the piston guide 41.9.

[0105] As shown in the figures, the receptacle 77 can be delimited by a circumferential wall 78 of the control piston 70 .

[0106] The receiving portion 77 can be connected to the chamber area 41.11 via the through portion 79. Here, the through portion 79 is arranged on both sides of the stop 50.1, 50.3, such as Figure 7 Clearly shown.

[0107] The control piston 70 is preloaded in the direction of the closed position of the valve by means of the support spring 44.2. The support spring 44.2 can be arranged in the external pressure area 41.2. The support spring 44.2 can be supported on the cylinder bottom 41.4 of the cylinder 41 and can lie oppositely against the head 71 of the control piston 70, such as Figure 7 shown.

[0108] Figure 7 It is shown that the piston 50 can have a stop 50 . 2 in the region of the piston rod 52 .

[0109] like Figure 7 As can be seen, the piston 50 can have an adjustment piece 54, which is introduced into the external pressure region 41.2 through the notch 76. In this embodiment, the pressure piece 54 is guided into the region of the chamber 73. Above the through portion 72, the chamber 73 forms part of the external pressure region 41.2.

[0110] The pressure piece 54 again forms a balanced pressure surface 57. The piston 50 has a piston-pressure surface 56. Figure 7 In the closed state shown, the piston pressure surface delimits the pressure chamber 41.6. The pressure chamber 41.6 is spatially connected to the pressure chamber 24 (or, if necessary, the chamber 26) of the hydraulic cylinder 20. Opposite the pressure chamber 41.6, the piston 50 forms a surface area 58. This surface area 58 is arranged according to Figure 7 The closed state defines a chamber area 41.11, such as Figure 7 shown.

[0111] The piston 50 is supported with spring preload relative to the control piston 70 by means of the spring 44. In the closed position of the piston 50, the spring element 44 exerts a prestress in the direction of the center longitudinal axis, which presses the piston 50 with its valve face 59 against the valve seat 41.7.

[0112] As shown in the drawing, the switching hydraulic system 80 can be spatially connected to the external pressure area 41.2 via a control line 81. For this purpose, the switching hydraulic system can be connected to at least one passage 41.3. The control line 81 is connected to the pressure chamber 41.6 or is spatially connected to it. A baffle 83 or a throttle can be installed in the control line 81.

[0113] Starting from the control line 81 , a branch 82 is connected to the passage 41 . 3 , which branch is spatially connected to the chamber region 41 . 11 via a line section 85 , for example to the outflow opening 41 . 5 .

[0114] A valve 84 is integrated in the branch 82. The valve 84 can be designed as a pressure-limiting valve which opens when a limit pressure is reached and releases a path for conducting hydraulic fluid from the passage 41.3 to the chamber region 41.11.

[0115] In an alternative variant, the line section 85 can also be connected not to the chamber region 41.11 but to an external space which is, for example, at ambient pressure and which can be designed, for example, in the form of a tank. This makes it possible to relieve the external pressure region 41.2 for a short time when the valve 84 is switched, since only a low counterpressure is present.

[0116] In use, during normal crushing operation, the pressure of the pressure space 24 of the hydraulic cylinder 20 is present at the pressure chamber 41.6. This pressure is also present in the outer pressure area 41.2, that is, applied via the connected control line 81. The spring 44 and the supporting spring 44.2, which can be connected in series here, support the closing force, which holds the piston 50 in place. Figure 7 Shown in closed state.

[0117] If the crushing force increases within permissible limits during the crushing operation, the pressure in the pressure space 24 of the hydraulic cylinder 20 increases. Correspondingly, the pressure in the outer pressure region 41.2 or in the chamber 73 is also increased via the control line 81. The piston 50 is held in the closed position with the aid of the spring 44 or the supporting spring 44.2 until a certain limit pressure is reached.

[0118] If the crushing force increases rapidly during the crushing operation due to an overload, the spring 44 is compressed and the piston 50 is lifted from the valve seat 41.7. The hydraulic fluid in the pressure chamber 41.6 flows out into the pressure balance area B. The moving mass formed by the piston 50 and the spring 44 is formed very small, because the valve stroke of the mechanical structure formed by the piston 50 and the spring 44 is kept relatively small. Therefore, the pressure relief valve 40 can be opened quickly in the case of an overload. In particular, the spring 44 can be designed to be simple, because in this embodiment, the ratio of the spring stroke of the spring 44 relative to the cylinder bottom 41.4 to the piston stroke of the piston 50 relative to the cylinder bottom 41.4 can be designed to be smaller.

[0119] Due to the adjustment of the piston 50 in the overload situation, an additional load is built up on the control piston 70 via the spring 44. In addition, due to the opened piston 50, the pressure in the pressure chamber 41.6 is now present in the chamber area 41.11. If this pressure in the chamber area 41.11 is now greater than the preset limit pressure, the control piston is also adjusted following the movement of the piston 50. The adjustment is performed against the prestress of the supporting spring 44.2. Since the adjustment of the control piston 70 increases the opening area towards the pressure balance area B, a larger amount of hydraulic fluid can flow into the pressure balance area B in a short time.

[0120] When adjusting the control piston 70 , hydraulic fluid is forced from the external pressure region 41 . 2 into the branch 82 . If the switching pressure at the valve 84 is exceeded, the valve 84 opens and the hydraulic fluid can flow away, whereby the control piston 70 is adjusted.

[0121] During adjustment of the control piston 70 , the control piston slides along the inner wall 41 . 8 , which can be designed as a sliding surface and against which the control piston 70 is guided in a sealing manner.

[0122] After the overload condition has ended, the spring 44 and the supporting spring 44.2 return the piston 50 and the control piston 70 to the Figure 7 The initial position is 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 first crushing body (11) and the second crushing body (14), wherein a hydraulic cylinder (20) is coupled to one of the first crushing body (11) and the second crushing body (14), the hydraulic cylinder being arranged and configured to allow a movement of the coupled first crushing body (11) and the second crushing body (14) in a deflection movement to increase the width of the crushing gap (15), wherein a pressure space (24) of the hydraulic cylinder (20) is coupled to a discharge port of an overload trigger device (30). The invention relates to a pressure relief valve (40) comprising a piston (50) which is arranged on a pressure chamber (41.6) of a pressure relief valve (40), wherein the piston (50) 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 a 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 (50) has at least one piston pressure surface (56) by means of which the piston (50) delimits the pressure chamber (41.6) transversely to an adjustment direction of the piston (50) in the closed position, It is characterized in that the piston (50) has a surface area (58) on its side facing away from the pressure chamber (41.6), which surface area limits the chamber area (41.11) transversely to the adjustment direction of the piston (50) in the closed position of the piston (50) so that under the action of the pressure, a closing force is introduced into the piston (50) in the chamber area (41.11) in the direction of the closed position.

2. The crusher according to claim 1, characterized in that: A balancing pressure surface (57) is indirectly or directly connected to the piston (50), the balancing pressure surface is maintained outside the pressure chamber (41.6) in an external pressure area (41.2), and the balancing pressure surface (57) is constructed and arranged to introduce a closing force into the piston (50) in the direction of the closed position under the action of the pressure in the external pressure area (41.2).

3. The crusher according to claim 2, characterized in that: An adjusting element is coupled to the piston (50).

4. The crusher according to claim 3, characterized in that: A piston rod (52) is connected to the piston (50), which forms a compensating pressure surface (57) outside the pressure chamber (41.6).

5. The crusher according to any one of claims 2 to 4, characterized in that In the closed position of the piston (50), the pressure in the external pressure region (41.2) is lower than the pressure in the pressure chamber (41.6), and the external pressure region (41.2) is in air-conducting connection with the surroundings, Alternatively, in the closed position of the piston (50), the pressure of the hydraulic fluid acts on the equilibrium pressure surface (57), and the pressure in the external pressure area (41.2) is less than, equal to or greater than the pressure in the pressure chamber (41.6).

6. A crusher according to any one of claims 2 to 4, characterized in that The external pressure area (41.3) is connected in a hydraulically conductive manner to a chamber (26) of the hydraulic cylinder (20), which chamber accommodates a piston rod (22) of the hydraulic cylinder (20) and holds a hydraulic fluid in the chamber.

7. The crusher according to claim 2, characterized in that: A spring (44) acts indirectly or directly on the piston (50), wherein in the closed position of the piston (50) the spring exerts a closing force on the piston (50) in a closing direction.

8. The crusher according to claim 7, characterized in that The mechanical spring (44) acts on the piston (50) indirectly or directly.

9. The crusher according to claim 7, characterized in that: The spring (44) is arranged in the outer pressure region (41.2).

10. The crusher according to claim 9, characterized in that The spring (44) is arranged in the cylinder (41) of the pressure relief valve (40).

11. The crusher according to claim 7, characterized in that The pressure compensation surface (57) is formed by a pressure piece (55) of the piston (50), and the spring (44) is supported on the pressure piece (55).

12. The crusher according to claim 11, characterized in that The pressure piece (55) has a region which projects radially outwardly above the pressure compensation surface (57) and on which the spring (44) is supported.

13. A crusher according to any one of claims 1 to 4, characterized in that In the closed position of the piston (50), the pressure of the hydraulic fluid acts on the surface area (58).

14. The crusher according to claim 13, characterized in that The pressure in the chamber area (41.11) is lower than the pressure in the pressure chamber (41.6).

15. The crusher according to claim 13, characterized in that The chamber area (41.11) can be connected in a hydraulically conductive manner to a chamber (26) of the hydraulic cylinder (20), which chamber accommodates a piston rod (22) of the hydraulic cylinder (20) and retains hydraulic fluid in the chamber.

16. A crusher according to any one of claims 1 to 4, characterized in that The surface area (58) forms an annular surface.

17. The crusher according to claim 16, characterized in that The annular surface extends concentrically around the adjusting element.

18. The crusher according to claim 16, characterized in that The annular surface extends concentrically around the piston rod (52).

19. A crusher according to any one of claims 1 to 4, characterized in that In the closed position of the piston (50), the adjusting element extends through the chamber region (41.11).

20. The crusher according to claim 19, characterized in that In the closed position of the piston (50), a piston rod (52) extends through the chamber area (41.11).

21. The crusher according to claim 19, characterized in that The chamber region (41.11) is delimited at a distance from the piston (50) by a piston guide (41.9), wherein the piston guide (41.9) has a recess (41.10) through which the adjusting element is passed in a sealing manner by means of a guide surface (53).

22. The crusher according to claim 21, characterized in that The chamber region (41.11) is defined at a distance from the piston (50) by a piston guide (41.9), wherein the piston guide (41.9) has a recess (41.10) through which the piston rod (52) passes in a sealing manner by means of a guide surface (53).

23. A crusher according to any one of claims 1 to 4, characterized in that The piston (50) has a piston head (51), to which the adjusting element is coupled, wherein the piston head (51) can be moved from its closed position into the chamber region (41.11).

24. The crusher according to claim 23, characterized in that The piston (50) has a piston head (51) to which a piston rod (52) is coupled.

25. The crusher according to claim 23, characterized in that The piston (50) has a piston head (51), to which the adjusting element is connected in one piece.

26. The crusher according to claim 24, characterized in that The piston (50) has a piston head (51) to which the piston rod (52) is integrally connected.

27. The crusher according to claim 23, characterized in that When the piston head (51) moves from the closed position into the open position or into the partially open position, it at least partially passes by at least one outflow opening (41.5) in order to establish a hydraulically conductive connection between the pressure chamber (41.6) and the pressure equalization region (B).

28. A crusher according to any one of claims 1 to 4, characterized in that The piston (50) is adjustably arranged in the bridge device (42).

29. The crusher according to claim 28, characterized in that The bridging device (42) is designed as an adjustable control piston (70).

30. The crusher according to claim 29, characterized in that The control piston is guideable in the cylinder (41) in an adjustably manner or is held in the cylinder (41) in a fixed position.

31. A crusher according to any one of claims 1 to 4, characterized in that The unloading piston (43) is guideable in the chamber area (47.11) in an adjustably manner, wherein the unloading piston (43) is adjustable between a closed position and an open position, wherein in the closed position the connection of the guiding fluid between the pressure chamber (41.6) and the unloading balance area (C) is blocked and in the open position the connection of the guiding fluid is at least partially released, the unloading piston (43) having at least one piston pressure surface (43.2), the unloading piston (43) defining the chamber area (47.11) in the closed position transversely to the adjustment direction of the unloading piston (43) by means of the piston pressure surface, and due to the increase in pressure in the hydraulic cylinder (20), the piston (50) and the unloading piston (43) open in sequence.

32. The crusher according to claim 31, characterized in that In the closed state of the unloading piston (43), a projection of one piston pressure surface (43.2) or multiple piston pressure surfaces (43.2) of the unloading piston (43) in a projection plane transverse to the adjustment direction of the unloading piston (43) only defines a part of the chamber area (41.11) transverse to the adjustment direction of the unloading piston (43).

33. The crusher according to claim 32, characterized in that A bridging device (42) is provided, the unloading 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 chamber area (41.11) along the adjustment direction of the unloading piston (43), and the projection of one pressure surface segment (42.4) or multiple pressure surface segments (42.4) in the projection plane in the direction of the adjustment movement of the unloading piston (43) does not cover or does not completely cover the projected piston pressure surface (43.2).

34. A crusher according to any one of claims 1 to 4, characterized in that The crusher is a rotary impact crusher, a jaw crusher, a cone crusher or a roll crusher.

35. A crusher according to any one of claims 1 to 4, characterized in that The first crushing body (11) is a rotor or a crushing jaw.

36. A crusher according to any one of claims 1 to 4, characterized in that The second crushing body (14) is an impact rocker or a crushing jaw.

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