阅读说明：本技术 破碎机 (Crushing machine ) 是由 G·迈耶 R·泰切特 J·梅尔 于 2021-05-26 设计创作，主要内容包括：本发明涉及一种破碎机,具有破碎机单元,其具有能够移动的第一破碎机体,第二破碎机体分配给第一破碎机体,在第一和第二破碎机体之间有破碎间隙,联接到第一或第二破碎机体的过载触发装置具有液压缸,过载触发装置允许联接的破碎机体的运动以增加破碎间隙的宽度,过载触发装置具有压力阀,在其打开位置中在压力室与低压区域间建立流体输送连接,在关闭的阀位置中阻止该连接。过载触发装置具有高压阀,高压阀由于过载情况而在其打开位置中在液压缸的压力室和低压区域间建立流体输送连接,在过载情况结束后,高压阀移动到关闭位置以阻止该连接,打开压力阀所需的触发压力低于打开高压阀所需的触发压力,增加这种破碎机的生产率和操作安全性。(The invention relates to a crusher having a crusher unit with a movable first crusher body, a second crusher body assigned to the first crusher body, a crushing gap between the first and second crusher bodies, an overload triggering device coupled to the first or second crusher body with a hydraulic cylinder, the overload triggering device allowing movement of the coupled crusher body to increase the width of the crushing gap, the overload triggering device having a pressure valve, in an open position of which a fluid conveying connection is established between a pressure chamber and a low pressure area, the connection being blocked in a closed valve position. The overload triggering device has a high-pressure valve which, as a result of an overload situation, establishes a fluid-conveying connection between the pressure chamber of the hydraulic cylinder and the low-pressure region in its open position, and which, after the overload situation has ended, moves into a closed position to block this connection, the triggering pressure required to open the pressure valve being lower than the triggering pressure required to open the high-pressure valve, increasing the productivity and operational safety of such a crusher.)

1. A crusher for mineral or reclaimed material, having a crusher unit (10), which crusher unit (10) has a movable first crusher body (11), to which first crusher body (11) a second crusher body (14) is assigned, wherein a crushing gap (15) is formed between the first crusher body (11) and the second crusher body (14), wherein an overload triggering device (30) is coupled to the first crusher body or to the second crusher body, which overload triggering device has a hydraulic cylinder (20), and which overload triggering device is designed to allow movement of the coupled crusher bodies (11,14) to increase the width of the crushing gap (15), wherein the hydraulic cylinder (20) has a pressure chamber (24) which is defined by a piston (23), and wherein the overload triggering device (30) has a pressure valve (31), which pressure valve (31) in its open position establishes a fluid transport between the pressure chamber (24) and a low pressure area A connection, while the pressure valve (31) prevents the connection in a closed valve position;

it is characterized in that the preparation method is characterized in that,

the overload triggering device (30) has a high-pressure valve (40), which high-pressure valve (40) establishes a fluid-conveying connection between the pressure chamber (24) of the hydraulic cylinder (20) and the low-pressure region in its open position as a result of an overload situation, and which high-pressure valve (40) is moved into a closed position after the overload situation has ended in order to prevent this connection, and the triggering pressure required for opening the pressure valve (31) is lower than the triggering pressure required for opening the high-pressure valve (40).

2. The crusher of claim 1,

the crusher is a rotary impact crusher or a jaw crusher.

3. The crusher of claim 1,

the first crusher body (11) is a rotor or a crusher jaw.

4. The crusher of claim 1,

the second crusher body (14) is an impact rocker or a crusher jaw.

5. The crusher of claim 1,

the trigger pressure required to open the pressure valve (31) is 100bar or less, and the trigger pressure required to open the high pressure valve (40) is 150bar or more.

6. The crusher of any of claims 1 to 5,

for an open pressure valve (31), the crusher body (14) coupled to the hydraulic cylinder (20) can be adjusted to cause a first increase in the crushing gap width (15), and for an open high pressure valve (40), the crusher body (14) coupled to the hydraulic cylinder (20) can be adjusted to cause a second increase in the crushing gap width (15), and the first increase in width is smaller than the second increase in width.

7. The crusher of claim 6,

the ratio of the first increase in width to the second increase in width is equal to or less than 0.5.

8. The crusher of claim 6,

the ratio of the first increase in width to the second increase in width is equal to or less than 0.25.

9. The crusher of any of claims 1 to 5,

the first pressure valve (31) is opened so that a first amount of hydraulic fluid enters the low pressure region through the fluid delivery connection, the high pressure valve (40) is opened so that a second amount of hydraulic fluid enters the low pressure region through the distributed fluid delivery connection, and the first amount is smaller than the second amount.

10. The crusher of claim 9,

the ratio of the first quantity to the second quantity is less than or equal to 0.5.

11. The crusher of claim 9,

the ratio of the first quantity to the second quantity is less than or equal to 0.25.

12. The crusher of any of claims 1 to 5,

the overload triggering device (30) is connected to the hydraulic circuit and the hydraulic fluid discharged via the fluid delivery connection of the high-pressure valve (40) is fed into the hydraulic circuit through a connecting line.

13. The crusher of any of claims 1 to 5,

the high-pressure valve (40) comprises a piston (60), which piston (60) is adjustable between a closed position and an open position against the preload of a spring (90), and which piston (60) comprises a pressure member (65), which pressure member (65) in the closed position bears in a sealing manner against a valve seat (47.6) by means of the spring preload.

14. The crusher of claim 13,

the piston (60) has a first pressure surface (66) and a second pressure surface (68), which pressure surfaces (66, 68) are pressurized by a hydraulic pressure present in a pressure chamber (24) of the hydraulic cylinder (20) in the closed position of the high-pressure valve (40), the projections of the first pressure surface (66) and of the second pressure surface (68) forming a first projection surface and a second projection surface in a plane perpendicular to the preload direction of the spring (90), wherein a surface normal to the first projection surface extends in the direction opposite to the opening movement direction of the piston (60) and a surface normal to the second projection surface extends in the opening movement direction of the piston (60), and the area of the first projection surface is larger than the area of the second projection surface.

15. The crusher of claim 13,

the piston (60) having one or more first pressure surfaces (66), the one or more pressure surfaces (66) being pressurized by a hydraulic pressure present in a pressure chamber (24) of the hydraulic cylinder (20) in a closed position of the high-pressure valve (40), a projection of the first pressure surface (66) in a plane perpendicular to a preloading direction of the spring (90) forming a first projection surface, wherein a surface normal to the first projection surface extends in a direction opposite to an opening movement direction of the piston (60), the piston (60) having at least one third pressure surface (67), a projection of the third pressure surface (67) in a plane perpendicular to a preloading direction of the spring (90) forming a third projection surface, wherein a surface normal to the third projection surface extends in a direction opposite to the opening movement direction of the piston (60), in the closed position of the high-pressure valve (40) there being no hydraulic pressure in the pressure chamber (24) of the hydraulic cylinder (20) at the third pressure surface (67), and in the open valve position a spatial connection is established between the third pressure surface (67) and the pressure chamber (24).

16. The crusher of claim 13,

the piston (60) of the high-pressure valve (40) has a passage (61) and said passage establishes a spatial connection between a region in front of the first pressure surface (66) and a fluid region (72) in front of the second pressure surface (68).

17. The crusher of claim 16,

the passage (61) is designed as a bore.

18. The crusher of any of claims 1 to 5,

a piston (60) of a high-pressure valve (40) has a support section (62), against which support section (62) a spring (90) designed as a helical spring is pushed, the piston (60) having a shoulder (63) supporting one end of the spring (90), and the other end of the spring (90) being supported on a spring holder (70), the spring holder (70) being part of a valve body (45), the piston being inserted into the valve body (45).

19. The crusher of any of claims 1 to 5,

the piston (60) of the high-pressure valve (40) has a guide section (64).

20. The crusher of claim 19,

the guide section (64) is guided in a sealing manner on an inner wall (47.2) of the guide body (47).

21. The crusher of any of claims 1 to 5,

the valve seat (47.6) for the piston (60) is formed by a valve element (47.4) of a guide body (47), which guide body (47) is inserted into a mounting of a valve body (45) of the high-pressure valve (40), and the guide body (47) forms at least one line section (47.3), through which line section (47.3) the hydraulic medium flows out of the pressure chamber (24) in the open position of the high-pressure valve (40).

22. The crusher of claim 21,

the valve element (47.4) is designed in the form of a bushing.

23. The crusher of claim 21,

the guide body (47) has an inner wall (47.2) spaced from the support section (62) of the piston (60), and the spring (90) is mounted in the spaced region.

24. The crusher of any of claims 1 to 5,

the high-pressure valve (40) has a coupling (41) and a valve body (45), which coupling (41) and valve body (45) are connected to one another by connecting ends (44,46), the coupling (41) and valve body (45) defining a decompression chamber (48) in the region of these connecting ends (44,46), and in the open position of the high-pressure valve (40), the decompression chamber (48) establishing a fluid-conveying connection between the pressure chamber (24) of the hydraulic cylinder (20) and a discharge (69) of the high-pressure valve (40).

25. The crusher of any of claims 1 to 5,

the piston (60) of the high-pressure valve (40) spatially delimits a spatial region with respect to the pressure chamber (24) of the hydraulic cylinder (20) and is spatially connected to a low-pressure region by a drain (69).

26. The crusher of claim 25,

a spring (90) is mounted in the spatial region.

27. The crusher of any of claims 1 to 5,

a displacement sensor (50) is provided, the displacement sensor (50) being used to measure or detect the position of the piston (60).

28. The crusher of any of claims 1 to 5,

the hydraulic cylinder (20) has a piston (23) delimiting a pressure chamber (24) in a cylinder area, and the piston rod (22) is coupled to the piston (23), and the piston rod (22) is rotatably coupled to the crusher body (14) by a coupling (21).

29. The crusher of any of claims 1 to 5,

the pressure valve (31) and the high pressure valve (40) are connected to the hydraulic cylinder (20) to form a structural unit.

30. The crusher of any of claims 1 to 5,

the overload situation has ended and the pressure valve (31) and the high-pressure valve (40) have been closed, the hydraulic cylinder being filled with hydraulic fluid such that the hydraulic cylinder returns to its operating position, a crushing gap (15) being formed in the operating state.

Technical Field

The invention relates to a crusher, in particular a rotary impact crusher, a cone crusher or a jaw crusher, having a crusher unit with a movable first crusher body, in particular a rotor or a crusher jaw, wherein a second crusher body, in particular an impact rocker or a crusher jaw, is assigned to the first crusher body, wherein a crushing gap is formed between the first crusher body and the second crusher body, wherein an overload triggering device is coupled to the first crusher body or to the second crusher body, which overload triggering device has a hydraulic cylinder and is designed to allow a movement of the coupled crusher bodies to increase the width of the crushing gap, wherein the hydraulic cylinder has a pressure chamber, and wherein the overload triggering device has a pressure valve which, in its open position, establishes a fluid conveying connection between the pressure chamber and a low pressure region, while the pressure valve prevents the connection in the closed valve position.

Background

An impact crusher is known from DE102017002079B4, in which a variable crushing gap is adjusted between a rotatable rotor and an impact rocker. In normal crushing operation, a material feeder is used to feed material to be crushed to the rotor. The rotor throws the material onto the impact rocker. The resulting force causes the rock material to fracture. The rock material is thus crushed to the desired grain size and can fall out of the crusher housing through the crushing gap. However, it may happen that non-fragmentable objects (e.g. iron parts) are fed into the rotor. This is a severe overload situation for an impact crusher. In particular, there is a risk of damage to the crusher during this process. In order to make this overload situation controllable, the piston cylinder unit is coupled to the impulse rocker. It can be used to change the position of the impact rocker and thereby the width of the crushing gap. The piston cylinder unit comprises a gas spring against which the impact rocker rests.

In normal crushing operation, the width of the crushing gap is set to the desired size. In the event of a severe overload, the gas spring may be compressed, thereby moving the impact rocker apart. In this way, the crushing gap can be increased in a pulsed manner. Non-fragmentable objects may then fall through the crushing gap. Subsequently, the width of the crushing gap is readjusted to the desired size.

The gas spring proposed in DE102017002079B4 introduces elasticity into the support of the impact rocker. During crushing, the forces will vary within certain tolerances due to the different hardness and different size of the rock. In response to these changing forces, the resilient gas spring causes a continuous (constant) change in the crushing gap and thus a continuous change in the particle size of the crushed material, which is undesirable.

From EP0019541B1 an impact mill is known in which the crushing gap can be adjusted via a hydraulic damper. The hydraulic damper has a piston to which a piston rod is coupled. The piston is adjustable within the cylinder chamber. The piston rod is connected to the impact rocker. An overload valve is provided in the event of an overload. If uncrushable objects enter the crushing chamber, an overload valve is triggered. This increases the size of the crushing gap and uncrushable objects may fall out of the crushing chamber.

As already indicated above, in crushers, in particular in rotary impact crushers, rock material of different sizes and different hardnesses is often fed into the crusher unit during normal crushing operation. The rotary impact crusher can process these rock materials and crush them. In this respect, such a non-severe situation must be distinguished from a severe overload situation in which uncrushable objects enter the area of the crusher unit.

However, this is not possible with the known rotary impact crusher. In particular, for safety reasons, the overload triggering device is set in such a way that it triggers without severe loading, although this is not necessary. This action reduces the effectiveness of the crushing process. In particular, it always takes a certain amount of time for the crusher unit to reset correctly after a trip has occurred.

Disclosure of Invention

The problem addressed by the present invention is to provide a crusher of the above-mentioned type, which allows an efficient crushing operation.

This problem is solved by an overload triggering device with a high-pressure valve which, due to a severe overload situation, establishes a fluid-conveying connection between a pressure chamber of a hydraulic cylinder and a low-pressure area in its open position and which, after the overload situation has ended, moves into a closed position to block the connection, and by the triggering pressure required to open the pressure valve being lower than the triggering pressure required to open the high-pressure valve.

If a short load peak occurs during the crushing operation (e.g. caused by large rocks within the crushing chamber), this indicates an allowable load situation that the crusher unit can handle. In this case, the crushing gap only needs to be increased slightly in order not to put too much stress on the crusher unit. The large rock can then be broken and the broken material has coarser particles in a short period of time. Incidentally, the setting of the crushing gap may be kept constant even for large variations in the load in the crushing chamber.

If uncrushable objects (e.g. iron nuggets) enter the crushing chamber, high load peaks may result. The overload triggering device can then react using the coupled high-pressure valve. In this way, the efficiency of the crusher and its operational safety are considerably improved in a simple manner.

According to a preferred variant of the invention, it can be provided that the triggering pressure required for opening the pressure valve is 100bar or less, and that the triggering pressure required for opening the high-pressure valve is 200bar or more.

The inventors have realized that in crushers, in particular in rotary impact crushers, a less severe overload situation may result in a pressure in the hydraulic cylinder in the range from 40 to 100 bar. Therefore, the trigger pressure for opening the pressure valve can be set to be less than 100 bar. It can be provided particularly advantageously that the pressure in the hydraulic cylinder is limited to a range from 50bar to 65bar by means of a pressure valve. In this way, the most common crushing tasks can be performed in an optimal way. In contrast, the required trigger pressure for a high pressure valve should be set to >150bar to safely control severe overload situations. Preferably, the triggering pressure in the hydraulic cylinder should be more than 200bar, more than 250bar, more than 300bar or more than 350bar, depending on the design of the crusher. Crushers with a relatively small crushing capacity tend to set a smaller pressure value, whereas crushers with a larger crushing capacity tend to have a higher triggering pressure.

In a particularly preferred embodiment of the invention, the crusher body coupled to the hydraulic cylinder is adjusted to cause a first increase in the width of the crushing gap (increment) for an open pressure valve, the crusher body coupled to the hydraulic cylinder is adjusted to cause a second increase in the width of the crushing gap for an open high pressure valve, and the first increase in the width is specified to be smaller than the second increase in the width, wherein it is preferably specified that the ratio of the first increase in the width to the second increase in the width is ≦ 0.5, particularly preferred ≦ 0.25.

The effectiveness of such a crusher design is further improved. In the case of a not severe overload, the crushing gap will only increase slightly to safely control it. After the end of the less severe overload situation, the slightly increased crushing gap can be quickly adjusted back to the desired size. On the other hand, in severe overload situations, the crushing gap must be wide open in a very short time to prevent damage to the crusher unit.

In particular, the crusher according to the invention may be designed such that, as a result of the opening of the first pressure valve, a first quantity (quality) of hydraulic fluid enters the low-pressure region through the fluid delivery connection, such that, as a result of the opening of the high-pressure valve, a second quantity of hydraulic fluid enters the low-pressure region through the distributed fluid delivery connection, and such that the first quantity is smaller than the second quantity, wherein preferably a ratio of the first quantity to the second quantity is provided which is less than or equal to 0.5, more preferably less than or equal to 0.25. This simple measure can be used to set the crushing gap to different sizes in both overload situations (no severe overload and severe overload).

If it is provided that the overload triggering device is connected to the hydraulic circuit and that the hydraulic fluid discharged via the fluid delivery connection of the high-pressure valve is supplied to the hydraulic circuit via the connecting line, the hydraulic fluid can be reused in the event of a severe overload. It can then be pumped back into the lines of the hydraulic circuit, for example using a pump.

According to a possible variant of the invention, it can be provided that the high-pressure valve comprises a piston which can be adjusted between a closed position and an open position against the preload of a spring, and that the piston comprises a pressure member which in the closed position is pressed in a sealing manner against a valve seat by the preload of the spring. A spring may be used to set the trigger pressure required to open the valve. The kit can also be designed in such a way that different springs with different spring rates can be used. By selecting a suitable spring, the triggering pressure and the triggering characteristics of the high pressure valve can be determined, and in this way the valve can be designed for a specific type of crusher.

One possible variant of the invention can be designed such that the piston has at least one first pressure surface and at least one second pressure surface, such that in the closed position of the high-pressure valve, the hydraulic pressure present in the pressure chamber of the hydraulic cylinder pressurizes the pressure surfaces, such that the projections (projections) of the first pressure surface and the second pressure surface form a first projection surface and a second projection surface in a plane perpendicular to the spring preload direction, wherein the surface normal (normal to) to the first projection surface extends in the direction opposite to the opening movement direction of the piston and the surface normal to the second projection surface extends in the opening movement direction of the piston, and the area of the first projection surface is greater than the area of the second projection surface.

This design for the high pressure valve allows for safe control of the high pressure. The closing pressure is determined by the preload force of the spring and the force generated by the difference in the projected surfaces times the applied pressure. A suitable choice of the surface difference may result in the use of a relatively soft spring to hold the high pressure valve securely in the closed state. This considerably simplifies the design work for the high-pressure valve. In addition, the plate spring characteristic can be easily realized using a soft spring such as a coil spring. These allow the piston to perform a long adjustment stroke against a relatively weak spring force. Thus, when the trigger pressure is applied, the high pressure valve may open quickly and fully, i.e. hydraulic fluid may leave the hydraulic cylinder in a short period of time. In this way severe overload situations can be safely controlled.

Within the scope of the invention, it can be provided in particular that more than the first pressure surface and/or the second pressure surface are present. Conversely, a plurality of first pressure surfaces and/or a plurality of second pressure surfaces may also be provided. The projection of these multiple pressure surfaces then results in a first total projection surface having a surface normal in the opening movement direction of the piston and a second total projection surface having a surface normal in a direction opposite to the opening movement direction of the piston. The area of the first total projection surface is larger than that of the second total projection surface.

According to the invention, provision may also be made for the piston to have a first pressure surface or a plurality of first pressure surfaces, the pressure surface or the pressure surfaces being pressurized by a hydraulic pressure present in a pressure chamber of the hydraulic cylinder in the closed position of the high-pressure valve, a projection of the first pressure surface(s) in a plane perpendicular to the spring preloading direction forming a first projection surface, wherein a surface normal to the first projection surface extends in a direction opposite to the opening movement direction of the piston, for the piston to have at least one third pressure surface, a projection of the third pressure surface(s) in a plane perpendicular to the spring preloading direction forming a third projection surface, wherein a surface normal to the third projection surface extends in a direction opposite to the opening movement direction of the piston, for the hydraulic pressure in the pressure chamber of the hydraulic cylinder not being present at the third pressure surface in the closed position of the high-pressure valve, and in the open valve position a spatial connection is established between the third pressure surface and the pressure chamber.

When the high pressure valve is closed, the pressure in the pressure chamber of the hydraulic cylinder pressurizes the first pressure surface. When the high pressure valve trips in a severe overload situation, the piston is displaced in its opening direction. Then, the region upstream of the third pressure surface is also in spatial contact with the pressure chamber. In this way, a high pressure is applied to the third pressure surface. Due to this high pressure, an additional force is generated at the third pressure surface in the opening direction of the piston. This force therefore increases the opening force for adjusting the piston. Once this force becomes effective, the piston will produce additional acceleration, helping to shorten the opening time. This may ensure a fast opening of the high pressure valve in case of a severe overload. Hydraulic fluid can be quickly discharged out of the hydraulic cylinder and the crusher body can be adjusted to quickly open the crushing gap.

According to the invention, it can also be provided that the piston of the high-pressure valve has a passage, which is designed in particular as a bore and which establishes a spatial connection between a region upstream of the first pressure surface and a fluid region upstream of the second pressure surface. The spatial connection between the two pressure surfaces is established, at least in some areas, by the piston. Machining can be performed accordingly easily.

A particularly compact design can be achieved if provision is made for the piston of the high-pressure valve to have a support section onto which a spring designed as a helical spring is pushed, for the piston to have a shoulder which supports one end of the spring, and for the other end of the spring to be supported on a spring retainer which is part of the valve body into which the piston is inserted. The springs are also fixed to prevent buckling at the support sections.

One conceivable embodiment of the invention is to provide the piston of the high-pressure valve with a guide section which is preferably guided in a sealing manner on an inner wall of the guide body.

The crusher according to the invention may be designed such that the valve seat for the piston is formed by a valve element of the guide body, which valve element is preferably designed in the form of a bushing, such that the guide body is inserted into a mounting of the valve body of the high-pressure valve, and such that the guide body forms at least one line section through which the hydraulic medium flows out of the pressure chamber in the open position of the high-pressure valve. The guide body can be easily manufactured as a separate component. Thus, the valve seat can be machined to precisely match the guide body.

In order to achieve a compact design of the high-pressure valve, it can also be provided that the guide body has an inner wall spaced apart from the support section of the piston, and that the spring is mounted in the spaced-apart region.

According to the invention, it can, for example, also be provided that the high-pressure valve has a coupling piece and a valve body which are connected to one another by connecting ends, that the coupling piece and the valve body define a pressure relief chamber in the region of these connecting ends, and that the pressure relief chamber, in the open position of the high-pressure valve, establishes a fluid-conveying connection between the pressure chamber of the hydraulic cylinder and the discharge of the high-pressure valve. In case of a severe overload, the relief chamber may quickly absorb a large amount of hydraulic fluid after opening the high pressure valve, which is then discharged through the drain. Since the pressure relief chamber is located in the region of the connecting end, it can be manufactured easily.

If the high pressure valve has moved to its open position, hydraulic fluid may inadvertently enter a chamber region separated from the pressure region of the high pressure cylinder by the piston. This hydraulic fluid may cause a risk of hindering the free adjustment of the piston. In order to be able to reliably ensure a reliable function of the high-pressure valve, it may be provided that the discharge connects the region of the piston of the chamber, which spatially separates it from the pressure chamber of the hydraulic cylinder, to the low-pressure region. Preferably, the chamber region can accommodate a spring for preloading the piston in a space-saving manner.

The operating position of the high pressure valve can be monitored if a displacement sensor is provided to measure or detect the position of the piston. For example, an overload condition may be detected. After the overload condition is over, the closed position of the piston may be detected using a displacement sensor. The machine control system may then be prompted to return the hydraulic cylinder to its operating position.

If the pressure valve and the high pressure valve are connected to the hydraulic cylinder to form one unit, the unit can be easily and quickly installed or replaced in case of damage.

It is particularly preferred to provide a control device which, after the overload situation has ended and the pressure valve and the high-pressure valve have closed, fills the hydraulic cylinder with hydraulic fluid in such a way that the hydraulic cylinder returns to its operating position, forming a crushing gap in the operating state.

Drawings

The invention is explained in more detail below on the basis of embodiments shown in the drawings. In the drawings:

fig. 1 shows a perspective view of a crusher unit of a rotary impact crusher;

fig. 2 and 3 show schematic views of a crusher unit according to fig. 1, which crusher unit has an overload triggering device;

fig. 4 shows a side view of the overload triggering apparatus according to fig. 2 and 3;

fig. 5 shows a perspective view of the overload triggering apparatus of fig. 4;

fig. 6 shows an isometric view of the high pressure valve of the overload triggering apparatus according to fig. 4 and 5 in a partial cross-sectional view;

figure 7 shows a side view and a cross-sectional view of the high pressure valve according to the details of figure 6;

figures 8 to 10 show three different manifestations of the high pressure valve according to figures 6 and 7;

FIG. 11 shows the high pressure valve in section XI-XI in FIG. 9; and

fig. 12 shows the high pressure valve in section along section labeled XII-XII in fig. 10.

Detailed Description

Fig. 1 shows a crusher unit 10 of a rotary impact crusher. The crusher unit 10 comprises a crusher housing in which a movable crusher body 11 is rotatably mounted. The movable crusher body 11 is thus designed as a rotor. The rotor carries impact struts 12 in the region of its outer circumference.

The upper impact rocker 13 is arranged inside the crusher housing. Furthermore, a further crusher body 14 is also arranged in the crusher housing, which in this case forms a lower impact rocker.

A crushing gap 15 is formed between the rotor (movable crusher body 11) and the lower impact rocker (crusher body 14). The radially outer ends of the impact bars 12 form an outer breaker ring when the rotor rotates. Which together with the opposite surface of the lower impact rocker forms a crushing gap 15. The swivel bearing 14.1 serves for the swivel mounting of the lower impact rocker 14. The width of the crushing gap 15 can be adjusted by the selected rotational position of the lower impact rocker.

As further shown in fig. 1, a material feeder 16 may be assigned to the crusher unit 10. The material feeder 16 may be used for feeding material 19.1 to be crushed into the crushing chamber. The transport direction is indicated by arrows in fig. 1. When the material 19.1 to be crushed enters the rotor area, the impact bar 12 throws it outwards. In the process, the material strikes the upper impact rocker 13 and the lower impact rocker 14. The material 19.1 to be crushed is broken when it hits the two impact rockers.

This is shown in more detail in fig. 2 and 3 by way of an example of a lower impact rocker. As shown in fig. 2, when the material 19.1 to be crushed hits the crusher body 14, crushed material 19.2 is produced. 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. It then enters the collecting area 17 below the movable crusher body 11 (rotor). As shown in fig. 1, a conveyor 18 is connected to the collection area 17. The conveyor 18 can be used to remove crushed material 19.2.

As further shown in fig. 2, hydraulic cylinders 20 are used to support the crusher body 14 relative to the machine structure of the crusher. The support at the machine structure, for example at the machine frame of the crusher, is not shown in detail in the drawings. However, fig. 1 shows that the hydraulic cylinder 20 is mainly mounted in a protected manner outside the crusher housing in which the rotor is mounted.

As shown in fig. 2 and 3, hydraulic cylinder 20 has a cylinder 25 in which piston 23 is adjustably guided. The piston 23 supports the piston rod 22. The piston rod 22 has a coupling 21 at its end facing away from the piston 23, which coupling 21 has a bearing part 21.1. The support member 21.1 is used for connecting the coupling 21 to the bearing 14.2 of the crusher body 14. In this way, the hydraulic cylinder 20 is rotatably mounted to the crusher body 14. The coupling point is at a distance from the rotary bearing 14.1.

As shown in fig. 2, the piston 23 defines a pressure chamber 24 within a cylinder 25. Hydraulic fluid, in particular hydraulic oil, is filled into the pressure chamber 24. The piston 23 is supported on this incompressible medium. In this way, the piston rod 22 and the crusher body 14 are held in the predetermined crushing position shown in fig. 2.

Depending on the crushing task at hand, the working position of the crushing gap 15 has to be adjusted accordingly. The crusher has a control device for this purpose. If the crushing gap 15 is to be enlarged starting from the position shown in fig. 2, hydraulic fluid is discharged from the pressure chamber 24. This moves the piston 23 further into the cylinder 25 until the desired crushing gap 15 is set. On the other hand, if a narrower crushing gap 15 is required, additional hydraulic fluid is added to the pressure chamber 24. This moves the piston 23 while increasing the pressure chamber 24. The piston rod 22 continues to be removed from the cylinder 25. This causes the crusher body 14 to rotate clockwise, resulting in a narrowing of the crushing gap 15.

As shown in fig. 1 to 3, an overload triggering apparatus 30 is also used. The overload triggering device 30 is preferably firmly connected to the hydraulic cylinder 20.

Fig. 4 and 5 show that the overload triggering device 30 comprises a control block 31 which holds the pressure valve. The pressure valve can be formed by a conventional pressure relief valve which is connected on the one hand to the pressure chamber 24 and on the other hand to the low-pressure region. In the exemplary embodiment, a connection to a low-pressure region is established by means of a hydraulic line 32. A hydraulic line 32 leads from the pressure valve (control block 31) to a hydraulic port 33 of the hydraulic cylinder 20. On the end of the piston 23 facing away from the pressure chamber 24, a hydraulic port 33 opens into the cylinder 25. In fig. 2 and 3, this is the area where the piston rod 22 is located. Furthermore, at least one discharge area 34 is provided, which is also spatially connected with the area of the cylinder 25 into which the hydraulic port 33 opens. This discharge area 34 can be used to lead hydraulic fluid into the hydraulic system, which hydraulic fluid is discharged from the pressure chamber 24 and is not suitable for entering the low pressure chamber of the cylinder 25 due to the volume of the piston rod 22. For example, the drained hydraulic fluid may be drained into the hydraulic tank through another relief valve. The pressure valve 31 (and further pressure relief valves) may be in the form of a simple check valve which acts in one direction to allow hydraulic fluid to drain from the pressure chamber 24.

In addition, a control element may be provided. If the piston 23 is to be reset, thereby increasing the size of the pressure chamber 24, hydraulic fluid can be introduced into the control element via the hydraulic line 32 and pumped into the pressure chamber 24 around the pressure valve 31. This moves the piston 23, thereby increasing the pressure chamber 24. The control element may for example be formed by a check valve acting on the pressure valve 31.

The pressure valve 31 is set to open in the range from 50 to 100bar, preferably in the range from 50 to 65bar, of the hydraulic pressure in the pressure chamber 24. This load situation corresponds to an operating situation in which a short-term load peak occurs as a result of the material 19.1 to be crushed. These short term load peaks occur, for example, if the material 19.1 to be crushed has large pieces of rock. In this case, the pressure valve 31 is triggered. The piston 23 moves a short distance within the cylinder 25, resulting in an increase of the crushing gap 25. The rock is then only roughly crushed.

As shown in fig. 4 and 5, a high pressure valve 40 is provided in addition to the pressure valve 31. As shown by fig. 4 and 5, the high-pressure valve 40 may also preferably be mounted to the hydraulic cylinder 20.

The high pressure valve 40 is shown in more detail in fig. 6 and 7. As can be seen from these figures, the high-pressure valve 40 has a coupling 41, into which coupling 41 a pressure line 43 is incorporated. The coupling 41 has an attachment mounting portion 42. In the assembled state, these attachment mounts 42 are aligned with the threaded seats of the hydraulic cylinder 20. In the assembled state, the pressure line 43 is spatially connected to the pressure chamber 24 of the hydraulic cylinder 20 via an opening 43.1.

The high-pressure valve 40 has a valve body 45, which valve body 45 can be designed like a housing. The valve body 45 forms a connecting end 46. The connecting end 46 may be used to connect the valve body 45 to the connecting end 44 of the coupling 41. The connection of the coupling 41 to the valve body 45 is established using a screw connection, not shown.

The valve body 45 has a recess in the region of its connecting end 46, which forms a decompression chamber 48. The decompression chamber 48 opens into a discharge opening 48.1, the discharge opening 48.1 being visible in fig. 10 and 12.

The valve body 45 is provided with a mounting portion. The guide body 47 is inserted into the mounting portion. The guide body 47 is preferably cylindrical on its outer circumference. The mounting forms an inner cylinder into which the guide body 47 is inserted in a sealing manner.

The guide body 47 surrounds the mounting region with an inner wall 47.2. The mounting area also forms a guide surface for the piston 60, as will be discussed in more detail below. The guide body 47 has a support section 47.1 at its end facing away from the connecting end 46. In contrast to the support section 47.1, the guide body 47 forms a valve element 47.4 with a valve seat 47.6. The seal 47.5 serves to seal the guide body 47 from the coupling piece 41 in the region of the connecting end 44.

As shown in fig. 7, the guide body 47 has at least one line section 47.3, which line section 47.3 is connected in a fluid-conveying manner to the decompression chamber 48. To mount the guide body 47, it is inserted into the valve body 45 at the end facing away from the connection end 46. The valve element 47.4 limits the insertion movement. As shown in fig. 7, the valve element 47.4 strikes against the coupling piece 41.

The piston 60 can be inserted into the guide body 47. The piston 60 is provided with a guide section 64 on its exterior. The guide section 64 is mainly formed of a cylindrical body, in which a seal groove may be formed in an outer circumferential surface thereof. The guide section 64 is held at the cylindrical inner wall 47.2 of the guide body 47 so as to be linearly adjustable in the direction of the central longitudinal axis M of the piston 60.

As shown in fig. 7, the piston 60 has a pressure member 65. In its closed position and thus in the closed position of the high-pressure valve 40, the pressure piece 65 of the piston is in sealing contact with the valve seat 47.6 of the guide body 47.

The piston 60 forms a first pressure surface 66 and a further second pressure surface 68. The first pressure surface 66 is preferably arranged in the region of the pressure element 65. Further preferably, the free end of the piston 60 may form a second pressure surface 68 facing the pressure member 65.

Fig. 7 shows that the piston 60 also has a third pressure surface 67. The third pressure surface 67 is smaller than the first pressure surface 66, the first pressure surface 66 being arranged rearwards in the direction of the central longitudinal axis M of the piston 60. The third pressure surface 67 is preferably formed by the guide section 64.

When the piston 60 is mounted in the guide body 47, the spring 90 can be inserted from the end facing the connection end 46 into the area between the inner wall 47.2 and the support section 62 of the piston.

In this case, the spring 90 is designed as a helical spring. In the assembled state, one end of the spring 90 rests against the shoulder 63 of the piston 60. The other end of the spring 90 rests against the support surface 71 of the spring holder 70. In particular, the spring retainer 70 may be designed as a separate component. After the piston 60, the spring 90, and the guide body 47 are installed into the valve body 45, the spring holder 70 is moved to the installation position shown in fig. 7 and fixed to the valve body 45 with bolts. In the assembled state, the guide body 47 rests against the support section 47.1 on the spring holder 70, preferably at the support surface 71. In this way, the spring holder 70 presses the valve element 47.4 of the guide body 47 against the coupling element 41. The gasket 47.5 is compressed during this process and seals tightly there. The spring retainer 70 preloads the spring 90 between the support surface 71 and the shoulder 63. In this manner, a preload force is introduced into the piston 60. This preload serves to clamp the pressure piece 65 of the piston in a circumferentially sealed manner against the valve seat 47.6 of the guide body 47.

Figure 7 shows that the closure member 80 can also be connected to the spring holder 70 in a sealing manner. However, it is also contemplated that the fastener 80 is integrally connected to the spring retainer 70.

The direction of action of the spring 90, and therefore the direction of the preload force, acts along the central longitudinal axis M of the piston 60.

The first pressure surface 66 and the third pressure surface 67 are formed such that a projection of these pressure surfaces 66, 67 in a plane perpendicular to the preload direction of the spring 90 forms a first projection surface and a third projection surface, wherein the surfaces normal to these first projection surface and third projection surface extend in a direction opposite to the opening movement (from left to right in fig. 7) direction of the piston 60.

The projection of the second pressure surface 68 in a plane perpendicular to the preload direction of the spring 90 forms a second projection plane. The surface normal to the second plane of projection extends in the direction of opening movement of the piston 60.

Now, the design of the piston 60 is such that when the piston 60 is closed, as shown in fig. 7, the area of the first plane of projection is larger than the area of the second plane of projection. During operation of the high-pressure valve 40, the pressure of the pressure chamber 24 of the hydraulic cylinder 20 is present in the pressure line 43. This pressure exists at the first pressure surface 66. Due to the presence of the openings 61, this pressure is also present in the fluid region 72, which is formed above the second pressure surface 68 (upstream). In this manner, the pressure also pressurizes the second pressure surface 68. The first projection surface is now larger than the second projection surface, so that the piston 60 will be lifted from the valve seat 47.6 due to the existing pressure conditions. The spring 90 counteracts this action. The preload force of the spring 90 is therefore selected to compensate for the force in the opening direction of the piston 60 due to the surface differences and additionally exerts a residual preload force which presses the piston 60 firmly against the valve seat 47.6.

If a severe overload situation now occurs, the pressure in the pressure chamber 24 of the hydraulic cylinder 20 suddenly increases. The pressure is also present at the first pressure surface 66 and the second pressure surface 68. If the pressure exceeds a critical threshold, the high pressure valve 40 is triggered.

Depending on the design of the rotary impact crusher, the critical pressure may be selected in the range of more than 150bar, more than 200bar, more than 250bar or more than 300bar or more than 350 bar.

When this threshold pressure is applied, the resulting force acting in the opening direction of the piston 60 may increase under the influence of the forces acting on the first and second pressure areas 66, 68. This force then becomes greater than the preload force of the spring 90. The piston 60 is then lifted off the valve seat 47.6. Hydraulic fluid may flow from the pressure line 43. Hydraulic fluid flows through the open valve seat 47.6 and into the area upstream of the third pressure surface 67. There, the pressure in the hydraulic fluid causes the force acting on the piston 60 in the opening direction of the piston 60 to increase further. This additional force causes the high pressure valve 40 to open rapidly.

Hydraulic fluid may flow across the third pressure surface 67. In this way, it enters the low pressure range. The hydraulic fluid then enters the decompression chamber 48 through the line section 47.3 and can flow out through the discharge opening 48.1.

Preferably, the outflowing hydraulic fluid is collected and returned to the hydraulic system, for example using a tank and a pump.

When the high-pressure valve 40 is activated in this way, the piston 23 of the high-pressure cylinder 20 is pushed into the cylinder 25, thereby reducing the size of the pressure chamber 24. In doing so, a large amount of hydraulic fluid is discharged from the cylinder 25 in a short time. This results in a rapid and extensive enlargement of the crushing gap 15. This situation is shown in fig. 3. The uncrushable object 19.3 causes an overload situation. The high pressure valve 40 has been triggered and the crusher body 14 has been adjusted to create the maximum crushing gap width. The uncrushable objects 19.3 can now fall out of the crushing gap 15.

As soon as uncrushable objects 19.3 fall out of the crushing gap 15, the overload situation no longer exists. The piston 23 in the high-pressure cylinder 20 is no longer loaded by the uncrushable object 19.3. The pressure in the pressure chamber 24 decreases. This results in both the high-pressure valve 40 and the possibly triggered pressure valve 31 being closed. When the two valves are closed, the machine control system can refill the pressure chamber 24 of the hydraulic cylinder 20 until it reaches its initial position in the operating position (fig. 2).

Fig. 6 shows a design variant in which the support element displacement sensor 50 is mounted at the high-pressure valve 40. The displacement sensor 50 may be, for example, an inductive sensor. The displacement sensor 50 may determine or detect the position of the piston 60. This information may be evaluated in the machine control system. Additionally or alternatively, a measurement port 49 for further parameters may also be provided, such as a pressure gauge or a thermometer. The pressure gauge measures the pressure in the decompression chamber 48.

As shown in fig. 7, a chamber is formed between the guide body 47 and the piston 60, in which chamber a spring 90 is arranged. The chamber is further delimited by a guide section 64, which guide section 64 can extend in a sealing manner along the inner wall 47.2. If no seal is provided here, or the requirement for a seal is not high, hydraulic fluid may enter the chamber when the high pressure valve 40 is activated. This will hinder the free adjustability of the piston 60. For this reason, a drain 69 is provided, which drain 69 is led out of the chamber and into the low-pressure region. Any accumulated hydraulic fluid may then be drained.