JP5920573B2 - Vertical crusher - Google Patents

Description

  The present invention mainly relates to a vertical crusher that uses coal, oil coke, limestone, slag, clinker, cement raw materials, chemicals, or the like as raw materials, and crushes them with a crushing roller driven on a rotary table. The present invention relates to a vertical crusher that prevents vibration and wear.

Conventionally, vertical crushers have been widely used as crushers for crushing coal and the like.
FIG. 7 is a schematic diagram of a conventional vertical crusher. As shown in the figure, a conventional vertical crusher 1 includes a casing 1B that forms an outline of the vertical crusher 1, a rotary table 2, and an outer surface of the upper surface of the rotary table 2 (hereinafter referred to as the upper surface 2A of the rotary table). A plurality of conical crushing rollers 3 are provided at positions equally divided in the circumferential direction.

  The crushing roller 3 is connected to the piston rod 9 of the hydraulic cylinder 8 via an upper arm 6 pivotally attached to the lower casing 1A by a shaft 7 and a lower arm 6A formed integrally with the upper arm 6. Yes. The hydraulic cylinder 8 is laterally pressed in the rotational direction of the rotary table upper surface 2A by the operation of the hydraulic cylinder 8, and is rotated by being driven by the raw material through the rotary table upper surface 2A.

  The vertical crusher disclosed in Patent Document 1 detects the tension hydraulic pressure of a hydraulic cylinder that presses a crushing roller against a rotary table. When the tension oil pressure becomes smaller than a preset value by a preset value, the tension oil pressure is increased to the set value after the rotational speed of the rotary table is reduced. Then, after the tension oil pressure rises to the set value, the rotational speed of the rotary table is increased until the speed before deceleration is reached. As a result, it is possible to prevent abnormal vibration of the vertical grinder that is likely to occur when the tension hydraulic pressure that deviates from the set value by more than the specified value to the original set value.

JP 2008-178837 A

  During operation, the crushing roller constantly vibrates up and down on the upper surface of the rotary table by crushing motion. At this time, the piston rod of the hydraulic cylinder directly connected to the crushing roller via the upper arm and the lower arm moves up and down in the same place in the hydraulic cylinder during the reciprocating motion depending on the layer thickness of the pulverized material to be crushed by the crushing roller. become. As the piston rod moves up and down, the hydraulic pressure in the hydraulic cylinder changes.

  The layer thickness of the pulverized product and the hydraulic pressure inside the cylinder are proportional to each other. For example, a force applied to the pulverized material is generated between the pulverizing roller and the rotary table. This crushing force is proportional to the size of the pulverized product, and can be efficiently crushed when the size of the pulverized product is within a certain range. However, the crushing force cannot provide a compressive force having a crushing effect when the size of the crushed material exceeds a certain range.

Further, it is effective for crushing to transmit the point load given by the crushing roller to the table in a straight line. However, when the size of the object to be crushed becomes larger, the rigidity of the object to be crushed increases, and the pressing force of the roller applied intensively by the point load is dispersed in the object to be crushed, and the crushing efficiency is lowered.
In addition to the above, the roller draws a trajectory approaching or leaving an arc instead of being perpendicular to the table surface. As a result, a horizontal component acts on the pressing force of the roller against the object to be crushed, the object to be crushed is removed from the load action line, and the roller cannot be crushed. This becomes more remarkable as the hardness of the object to be crushed increases.

FIG. 8 is an explanatory view of a conventional crushing roller. FIG. 8A shows a crushing roller when a material to be crushed having a large particle diameter is introduced, and FIG. 8B shows a crushing roller that is a rotary table. Shows the case of contact with.
As shown in (A), when the object to be crushed having a large particle size is supplied onto the turntable 2, the crushing roller 3 rides on the object to be crushed on the turntable 2 and lifts upward together with the arm 6B. Then, the piston rod 9 is lowered via the fulcrum, and the pressure in the hydraulic cylinder 8 is increased. In the hydraulic cylinder 8, since a predetermined hydraulic pressure is applied, an excessive load is applied when the pressure is applied, noise and vibration of the pulverizer are generated, and the pulverization roller 3 is loaded and uneven wear occurs. . Further, a load is applied to the oil seal of the hydraulic cylinder 8, which causes oil leakage.

  The vertical crusher is crushing while being pushed up in the direction in which the crushing roller is separated from the upper surface of the rotary table (upward of the rotary table) due to the thickness of the raw material having a large particle size immediately after the raw materials are charged. As the pulverization of the raw material proceeds, the distance between the upper surface of the rotary table and the pulverization roller gradually decreases. For this reason, the wear of the roller small-diameter portion of the crushing roller, in other words, the roller surface on the supply side of the object to be crushed easily proceeds.

  The crushing roller moves up and down by the change in the thickness of the raw material layer on the upper surface of the rotary table (arrow B in FIG. 7 is a pulling direction force). Therefore, in addition to the force (cylinder reaction force) for pulling the piston rod 9 in the axial direction (arrow A in FIG. 7), the link mechanism between the grinding roller and the hydraulic cylinder 8 is used in a direction orthogonal to the axial direction of the hydraulic cylinder 8. A horizontal force (external force) acts (arrow C in FIG. 7). The piston rod 9 normally reciprocates in the axial direction at the center of the packing of the hydraulic cylinder 8. However, when the horizontal force is applied, the gap between the hydraulic cylinder 8 and the piston rod 9 becomes non-uniform, and the piston rod 9 and the inner surface of the hydraulic cylinder 8 where the packing is locally strongly contacted may cause uneven wear. there were.

Further, when the object to be crushed is not supplied or when the gap between the pulverizing roller and the rotary table is small, the pulverizing roller 3 comes into contact with the rotary table 2 as shown in FIG. And the grinding roller 3 is worn.
Therefore, an object of the present invention is to provide a vertical crusher that can prevent vibration and wear of a crushing roller. It is another object of the present invention to provide a vertical crusher capable of preventing oil leakage of a hydraulic cylinder that applies a pressing force to a crushing roller.

  The vertical crusher of the present invention comprises a rotary table, a grinding roller rotatable on the rotary table, and a hydraulic structure that presses the grinding roller against an upper surface of the rotary table, and supplies the raw material supplied to the rotary table. In the vertical crusher for crushing, the hydraulic structure includes a hydraulic cylinder, a piston rod connected through a fulcrum to a shaft of the crushing roller, and a reciprocating motion inside the hydraulic cylinder, and a first connected to the hydraulic cylinder. A hydraulic pressure source that supplies hydraulic pressure to an oil passage and a second oil passage that branches off from the first oil passage and connects to the pressure release means, and maintains a separation distance between the grinding roller and the rotary table within a set range; The pressure release means relieves to a drain close to the hydraulic cylinder when excessive hydraulic pressure is applied to the hydraulic cylinder beyond the set range. It is characterized in.

  The pressure release means includes a through hole through which the piston rod penetrates, a relief valve having a relief hole connected to the through hole on the outer periphery, an end face hole of the piston rod connected to the second oil passage, An oil passage connected to the outer peripheral hole formed on the outer peripheral surface and formed along the axial center of the piston rod, and when the piston rod moves forward and backward, the relief hole and the outer peripheral hole overlap. Further, the hydraulic pressure of the second oil passage is relieved to the drain.

  The pressurizing release means includes a rotation shaft of the fulcrum and a bearing that supports rotation around the axis of the rotation shaft, and the rotation shaft is formed on an end surface hole connected to the second oil passage, and on an outer peripheral surface. Relief connected with the formed outer peripheral hole, forming an oil passage formed along the shaft core, the bearing forming a through hole through which the shaft passes along the axial center, and connecting with the through hole A hole is formed on the outer periphery, and the hydraulic pressure of the second oil passage is relieved to the drain when the rotary shaft rotates and the relief hole and the outer peripheral hole overlap.

  According to the vertical crusher of the present invention configured as described above, oil in the hydraulic cylinder does not leak within the operating range of the roller, and the inside of the cylinder can be maintained at a predetermined pressure. When the crushing roller moves out of the operating range of the roller, excessive pressure acting on the hydraulic cylinder can be released by leaking the oil connected to the hydraulic cylinder to the drain close to the hydraulic cylinder by the pressure release means. . That is, when the grinding roller is lifted beyond the operating range, the cylinder hydraulic pressure (roller pressing force) for pressing the grinding roller is relieved to the drain. Further, the roller pressing force is relieved to the drain before the roller contacts the table beyond the operating range. And after relief, the predetermined oil pressure which returns a grinding | pulverization roller to an operation range with a hydraulic pressure source acts.

Conventionally, in a pulverizer configured to absorb a pressure change by an accumulator separated from a hydraulic cylinder, a pipe to the accumulator becomes long and cannot cope with a sudden pressure change in the hydraulic cylinder. However, according to the pulverizer of the present invention, when a sudden pressure change occurs, the pressure is effectively reduced by relief to the drain of the pressure release means formed near the hydraulic cylinder, that is, the piston rod or the arm. Can be absorbed. Therefore, it is possible to prevent wear and cracks due to abnormal noise of the grinding roller, abnormal vibration of the grinding machine, and strong contact between the metal of the grinding roller and the rotary table.
Further, the oil seal load of the cylinder oil of the hydraulic cylinder can be reduced, and there is no possibility of oil leakage from the hydraulic cylinder.
In addition, since excessive pressure is applied to the hydraulic cylinder and no abnormal pressure is applied to the cylinder or the hydraulic piping, the load on the equipment can be reduced.

Further, the maximum lifting of the pulverizing roller can prevent the pressure in the cylinder and the hydraulic equipment from changing suddenly due to the size and hardness of the pulverized material.
Further, when the pulverizing roller is lifted (in a state where the pulverizing roller is separated from the rotary table), there is a possibility that the local portion of the large-diameter portion of the tapered pulverizing roller comes into contact with the rotary table. In this case, the local part of the crushing roller is worn out early. Therefore, when the grinding roller is lifted beyond the operating range, the pressing force of the grinding roller can be lowered to prevent local wear.

It is explanatory drawing which represented notionally the hydraulic structure of the vertical crusher of 1st Embodiment. It is sectional drawing to which the pressurization cancellation | release means of 1st Embodiment was expanded. It is explanatory drawing of the hydraulic structure of 1st Embodiment when a grinding | pulverization roller and a rotary table have left | separated. It is explanatory drawing of the hydraulic structure of 1st Embodiment when a crushing roller and a rotary table approach. It is explanatory drawing of the pressurization cancellation | release means of 2nd Embodiment, (A) is a perspective view of a rotating shaft, (B) is a perspective view of a rotating shaft and a bearing, (C) is sectional drawing of a rotating shaft. It is a lineblock diagram of the vertical crusher of a 1st embodiment. It is the structure schematic of the conventional vertical crusher. It is explanatory drawing of the conventional crushing roller.

Embodiments of a vertical crusher of the present invention will be described below in detail with reference to the accompanying drawings.
FIG. 6 is a schematic configuration diagram of the vertical crusher of the first embodiment. As shown in the figure, the vertical crusher 10 includes a casing 12, a rotary table 14, and a plurality of conical crushing rollers 16 disposed at positions at which the outer peripheral portion of the upper surface of the rotary table 14 is equally divided in the circumferential direction. It has.

  The crushing roller 16 is connected to a piston rod 26 of a hydraulic cylinder 24 via an upper arm 20 pivotally attached to a lower casing 12B serving as a fulcrum and a lower arm 22 formed integrally with the upper arm 20. Yes. The crushing roller 16 operates in the direction of the upper surface 14A of the rotary table by the operation of the hydraulic cylinder 24 (operating in the direction of supplying oil to the oil chamber on the rod side of the hydraulic cylinder 24 in FIG. 6 and pulling the piston rod 26 in the axial direction). Then, the rotary table 14 is rotated by being driven via the raw material.

  A separator 30 and a raw material charging port 32 are provided at the central portion of the rotary table upper surface 14A of the casing 12, and a raw material charging chute 34 is arranged so as to penetrate the central axis of the separator 30 up and down. The raw material can be charged from the raw material charging port 32 to the upper surface 14A of the rotary table via the raw material charging chute 34.

  In addition, the separator 30 includes a plurality of blades 36 arranged in a reverse truncated cone shape having a diameter increasing upward with the rotation axis of the separator 30 as a center, and is freely rotated by a driving device (not shown). It can be configured.

  The raw material charged from the raw material charging chute 34 is moved to the outer peripheral portion of the rotary table upper surface 14A while drawing a spiral trajectory on the rotary table upper surface 14A, and is caught and pulverized by the rotary table upper surface 14A and the grinding roller 16. Then, a part of the raw material caught by the rotary table upper surface 14A and the grinding roller 16 gets over the dam ring 38 provided around the outer edge of the rotary table upper surface 14A, and the rotary table upper surface 14A and the outer peripheral part It goes to the annular passage 40 which is a gap with the casing 12. Here, a gas inlet 42 for introducing gas is provided below the rotary table 14 of the lower casing 12B, and an upper outlet for taking out the raw material pulverized together with the gas is further provided above the rotary table 14. 44 is provided.

  During operation of the vertical crusher 10, by introducing gas (air in the present embodiment) from the gas inlet 42, the casing 12 passes through the separator 30 from below the rotary table 14 and passes through the upper outlet. There is an air flow of gas flowing to 44.

  The raw material charged into the vertical crusher 10 and part of the raw material crushed by the rotary table 14 and the crushing roller 16 and over the dam ring 38 are blown up by the gas and moved up in the casing 12 to reach the separator 30. To reach.

  Here, the raw material having a large diameter and weight cannot pass through the blades 36 of the separator 30 and falls below the separator 30 and is re-engaged by the grinding roller 16 to be pulverized. It passes through the separator 30 through the blades 36 arranged with a gap, and is taken out from the upper outlet 44.

  Further, a part of the raw material having a maximum particle size that has reached the annular passage without being bitten by the grinding roller 16 falls below the rotary table 14 from the annular passage 40 and is dropped from the lower outlet 46 to the vertical grinder. 10 is taken out.

  The vertical pulverizer may be a tire-type vertical pulverizer in which the shape of the pulverizing roller is a spherical shape. Further, the separator 30 may be a fixed type according to the required particle size of the product. Or the type which is not equipped with the separator may be sufficient.

  FIG. 1 is an explanatory view conceptually showing the hydraulic structure of the vertical crusher of the first embodiment. As shown in the figure, the hydraulic structure 50 of the first embodiment includes a hydraulic cylinder 24, a piston 28 that reciprocates in the cylinder, a piston rod 26 that is connected to the piston 28 and protrudes from the hydraulic cylinder 24, and pressure release means. 60, a hydraulic pump 70, and an accumulator 80 are the main basic components.

  The hydraulic cylinder 24 is attached to the base 13 of the lower casing 12B (FIG. 6). The piston rod 26 is provided with a pressure release means 60 at the end opposite to the end to which the piston 28 is connected. And between the piston 28 of the piston rod 26 and the pressure release means 60, it connects with the arm 23 rotatably via the link. A crushing roller 16 is formed at the end of the arm 23. A shaft 18 serving as a fulcrum is formed between the link at one end of the arm 23 and the crushing roller 16 at the other end. Such an arm 23 is formed to be rotatable through a fulcrum.

  The hydraulic structure 50 that presses the crushing roller 16 against the rotary table 14 includes an accumulator 80 as a pressure accumulator that generates tension hydraulic pressure, and a hydraulic pump 70 that supplies pressure oil to the accumulator 80. A first oil passage 72 is formed between the hydraulic pump 70 and the hydraulic cylinder 24. The second oil passage 74 branched from the first oil passage 72 is connected to the pressure release means 60.

  FIG. 2 is an enlarged cross-sectional view of the pressure release means of the first embodiment. As shown in the figure, the pressure release means 60 of the first embodiment includes a through hole 63 through which the piston rod 26 penetrates, a relief valve 62 formed on the outer periphery with a relief hole 64 connected to the through hole 63, and a second oil. An end surface hole 77 of the piston rod 26 connected to the path 74 and a third oil path 76 connected to the outer peripheral hole 78 formed on the outer peripheral surface and formed along the axial center of the piston rod 26 are configured. Yes.

  The relief valve 62 is a cylinder that covers the outer periphery of the end of the piston rod 26. The relief valve 62 is formed with a through hole 63 through which the end of the piston rod 26 opposite to the end where the piston 28 is formed penetrates. The relief valve 62 is formed with a plurality of relief holes 64 formed on the outer periphery of the cylinder. The relief hole 64 is connected to the through hole 63. A plurality of relief holes 64 are formed along the longitudinal direction of the cylindrical body. In the relief valve 62 of the embodiment, an upper relief hole 64a is formed on the end portion side (end surface hole side of the piston rod 26) of the piston rod 26, and a lower relief hole 64b is formed on the piston side. Both the upper relief hole 64a and the lower relief hole 64b are connected to an external drain. The operation range of the crushing roller 16 is between the upper relief hole 64a and the lower relief hole 64b.

The third oil passage 76 is connected to an end surface hole 77 formed in the end surface of the end portion of the piston rod 26 and an outer peripheral hole 78 formed in the outer periphery of the piston rod 26, and is formed along the axis of the piston rod 26. Has been. Further, the end surface hole 77 is connected to the second oil passage 74.
In the pressure release means 60 of the first embodiment having such a configuration, the outer peripheral hole 78 of the piston rod 26 is located between the upper relief hole 64a and the lower relief hole 64b of the relief valve 62 during normal operation of the pulverizer. It is arranged in the operating range. When the outer peripheral hole 78 is disposed within this operating range, the crushing roller 16 is disposed at a position spaced apart from the rotary table 14 by a predetermined distance. At this time, pressure oil is supplied from the hydraulic pump 70 to the accumulator 80, and tension hydraulic pressure is generated in the first oil path 72 and the second oil path 74 from the accumulator 80. Tension oil pressure is also generated in the third oil passage 76 connected to the second oil passage. Since the outer peripheral hole 78 is blocked by the inner wall of the relief valve 62, the pressure oil in the third oil passage 76 does not leak to the outside. If excessive pressure acts on the hydraulic cylinder 24 and the outer peripheral hole 78 exceeds the operating range, the upper relief hole 64a or the lower relief hole 64b overlaps with the upper relief hole 64b in plan view, and the pressure oil in the third oil passage 76 is relieved by the relief hole 64. To the external drain. After the relief, the outer peripheral hole 78 is returned to the working range by the tension hydraulic pressure by the accumulator 80.

Next, the operation of the vertical crusher of the present invention having the above configuration will be described below.
FIG. 3 is an explanatory diagram of the hydraulic structure of the first embodiment when the grinding roller and the rotary table are separated from each other. As shown in the figure, when a massive crushed object is supplied onto the rotary table 14, the pulverizing roller within the operating range indicated by the dotted line rides on the pulverized object on the rotary table 14, and the pulverizing roller indicated by the solid line. In this way, it is lifted in the direction away from the rotary table (upward) (arrow A). Then, the piston rod 26 linked to the arm 23 via the shaft 18 moves downward as indicated by an arrow B. When the piston 28 in the hydraulic cylinder 24 moves to the cylinder-side oil chamber, excessive pressure is applied to the cylinder-side oil chamber. This excessive pressure acts on the first to third oil passages 72, 74, 76 connected to the hydraulic cylinder 24. In the relief valve 62, the outer peripheral hole 78 of the piston rod 26 disposed within the operating range moves downward (in the hydraulic cylinder 24 side) as indicated by an arrow C. When the outer peripheral hole 78 moves beyond the operating range to a position overlapping the lower lower relief hole 64b in plan view, the pressure oil in the third oil passage 76 is relieved to the external drain via the lower relief hole 64b ( Arrow D). Accordingly, excessive pressure acting on the first to third oil passages 72, 74, and 76 is released, so that the movement of the crushing roller 16 in the direction of arrow A is stopped. After the relief, the outer peripheral hole 78 is returned to the operating range by the tension hydraulic pressure by the accumulator 80, and the grinding roller 16 is rearranged in the operating range.

  FIG. 4 is an explanatory diagram of the hydraulic structure of the first embodiment when the crushing roller and the rotary table approach each other. As shown in the drawing, when the object to be crushed is not supplied to the pulverizer and the gap between the pulverizing roller 16 and the rotary table 14 is reduced, the pulverizing roller 16 within the operating range indicated by the dotted line is replaced by the pulverizing roller 16 indicated by the solid line. In this way, it is pushed down in the direction approaching the rotary table 14 (downward) (arrow E). The piston rod 26 linked to the arm 23 via the shaft 18 moves upward as indicated by an arrow F. In the relief valve 62, the outer peripheral hole 78 of the piston rod 26 disposed within the operating range moves upward (in the second oil passage 74 side) indicated by the arrow G. When the outer peripheral hole 78 moves beyond the operating range to a position overlapping the upper upper relief hole 64a in plan view, the pressure oil in the third oil passage 76 is relieved to the external drain via the upper relief hole 64a ( Arrow H). Thereby, the movement of the crushing roller 16 in the direction of arrow E is stopped. After the relief, the outer peripheral hole 78 is returned to the operating range by the tension hydraulic pressure by the accumulator 80, and the grinding roller 16 is rearranged in the operating range.

  According to such a vertical crusher of the present invention, the oil in the hydraulic cylinder is not leaked within the operating range of the roller, and the inside of the cylinder can be maintained at a predetermined pressure. On the other hand, when the crushing roller is lifted beyond the operating range, the cylinder hydraulic pressure (roller pressing force) for pressing the crushing roller can be relieved to the drain. Moreover, the roller pressing force is relieved to the drain before the grinding roller contacts the rotary table beyond the operating range.

As a result, it is possible to prevent wear and cracks due to abnormal noise of the grinding roller, abnormal vibration of the grinding machine, and strong contact between the metals of the grinding roller and the rotary table.
Further, the oil seal load of the cylinder oil of the hydraulic cylinder can be reduced, and there is no possibility of oil leakage from the hydraulic cylinder.
In addition, since excessive pressure is applied to the hydraulic cylinder and no abnormal pressure is applied to the cylinder or the hydraulic piping, the load on the equipment can be reduced.

  5A and 5B are explanatory views of the pressure release means of the second embodiment, wherein FIG. 5A is a perspective view of the rotating shaft, FIG. 5B is a perspective view of the rotating shaft and a bearing, and FIG. 5C is a sectional view of the rotating shaft. It is. As shown in the figure, the pressure release means 60A of the second embodiment is composed of a rotating shaft 90 serving as a fulcrum and a bearing 100 that rotates around the axis of the rotating shaft 90.

The rotation shaft 90 is formed with a hole through which the arm 23 of the crushing roller 16 passes in a central portion of the shaft center and at a location intersecting the shaft center. The rotating shaft 90 has an end surface hole 92 connected to the second oil passage 74 on either end surface. An outer peripheral hole 94 is formed on the outer peripheral surface of the rotary shaft 90. The third oil passage 96 is connected to the end face hole 92 and the outer peripheral hole 94 and is formed along the axis. The end surface hole 92 is connected to the second oil passage 74. The rotating shaft 90 and the arm 23 may be formed integrally.
The bearing 100 forms a through-hole 102 through which the rotary shaft 90 passes along the axis, and supports the rotary shaft 90 so as to be rotatable about its axis. The bearing 100 has a relief hole connected to the through hole 102 on the outer periphery. A plurality of relief holes are formed along the axis of the rotary shaft 90. In the bearing 100 of the embodiment, a first relief hole 104 a and a second relief hole 104 b are formed along the axis of the rotary shaft 90. Both the first relief hole 104a and the second relief hole 104b are connected to an external drain (not shown). The operating range of the crushing roller 16 is between the first relief hole 104a and the second relief hole 104b.

  In the pressure release means 60A of the second embodiment having such a configuration, the outer peripheral hole 94 of the rotary shaft 90 is formed between the first relief hole 104a and the second relief hole 104b of the bearing 100 during normal operation of the pulverizer. It is arranged in the operating range between. When the outer peripheral hole 94 is disposed within this operating range, the crushing roller 16 is disposed at a position spaced apart from the rotary table 14 by a predetermined distance. At this time, pressure oil is supplied from the hydraulic pump 70 to the accumulator 80, and tension hydraulic pressure is generated in the first oil path 72 and the second oil path 74 from the accumulator 80. Tension hydraulic pressure is also generated in the third oil passage 96 connected to the second oil passage. Since the outer peripheral hole 94 is blocked by the inner wall of the bearing 100, the pressure oil in the third oil passage 96 does not leak to the outside. When excessive pressure acts on the hydraulic cylinder 24 and the outer peripheral hole 94 exceeds the operating range, it overlaps with the first relief hole 104a or the second relief hole 104b in plan view, and the pressure oil in the third oil passage 96 becomes the first relief. Relief is performed from the hole 104a or the second relief hole 104b to the external drain. After the relief, the outer peripheral hole 94 is returned to the working range by the tension hydraulic pressure by the accumulator 80.

  Even with the vertical crusher using the pressure release means of the second embodiment, the oil in the hydraulic cylinder does not leak within the operating range of the roller, and the inside of the cylinder can be maintained at a predetermined pressure. . On the other hand, when the grinding roller is lifted beyond the operating range, the cylinder hydraulic pressure (roller pressing force) for pressing the grinding roller can be relieved to the drain close to the hydraulic cylinder. Further, the roller pressing force can be relieved to the drain before the grinding roller contacts the rotary table beyond the operating range.

  The vertical crusher of the present invention that can prevent vibration and wear of the crushing roller and oil leakage of the hydraulic cylinder is very useful.

DESCRIPTION OF SYMBOLS 1 ......... Shape type pulverizer, 1A ......... Lower casing, 1B ......... casing, 2 ......... Rotary table, 3 ......... Crushing roller, 7 ......... Shaft, 6 ......... Upper arm, 6A ......... Lower arm, 8 ......... Hydraulic cylinder, 9 ......... Piston rod, 10 ......... Vertical crusher, 12 ......... Case, 12B ......... Lower casing, 13 ......... Base, 14 ... ...... Turntable, 14A ......... Top of rotary table, 16 ......... Crushing roller, 18 ......... Shaft, 20 ......... Upper arm, 22 ......... Lower arm, 24 ......... Hydraulic cylinder, 26 ... ... piston rod, 28 ... piston, 30 ... separator, 32 ... raw material inlet, 34 ... raw material chute, 36 ... blade, 38 ... dam ring, 40 ... annular Passage, 42 ... Gas inlet, 44 ...... Upper outlet, 50 ......... Hydraulic structure, 60, 60A ......... Pressure release means, 62 ......... Relief valve, 63 ......... Through hole, 64 ......... Relief hole, 70 ......... Hydraulic Pump, 72 ......... First oil passage, 74 ......... Second oil passage, 76 ......... Third oil passage, 77 ...... End face hole, 78 ......... Outer peripheral hole, 80 ...... Accumulator, 90 ......... Rotating shaft, 92 ......... End face hole, 94 ......... Outer peripheral hole, 96 ......... Third oil passage, 100 ......... Bearing, 102 ......... Through hole, 104a ......... First relief hole , 104b ......... second relief hole.

Claims (2)

In a vertical crusher for crushing a raw material supplied to the rotary table, comprising: a rotary table; a crushing roller rotatable on the rotary table; and a hydraulic structure that presses the crushing roller against an upper surface of the rotary table.
The hydraulic structure is
A hydraulic cylinder;
A piston rod connected to the arm of the crushing roller via a fulcrum and reciprocating inside the hydraulic cylinder;
The hydraulic pressure is supplied to the first oil passage connected to the hydraulic cylinder and the second oil passage branched from the first oil passage and connected to the pressure release means, and the separation distance between the grinding roller and the rotary table is increased. And a hydraulic pressure source that is maintained within the set range.
The pressure release means is
A relief valve having a through hole through which the piston rod penetrates and a relief hole connected to the through hole formed on the outer periphery;
An end face hole of the piston rod connected to the second oil path, an outer peripheral hole formed on the outer peripheral surface, and a third oil path formed along the axial center of the piston rod,
Excess hydraulic pressure acts on the hydraulic cylinder beyond the set range, and the piston rod moves forward and backward, and the oil in the third oil passage is relieved to the drain when the relief hole and the outer peripheral hole overlap. A vertical crusher characterized by being made. In a vertical crusher for crushing a raw material supplied to the rotary table, comprising: a rotary table; a crushing roller rotatable on the rotary table; and a hydraulic structure that presses the crushing roller against an upper surface of the rotary table.
The hydraulic structure is
A hydraulic cylinder;
A piston rod connected to the arm of the crushing roller via a fulcrum and reciprocating inside the hydraulic cylinder;
The hydraulic pressure is supplied to the first oil passage connected to the hydraulic cylinder and the second oil passage branched from the first oil passage and connected to the pressure release means, and the separation distance between the grinding roller and the rotary table is increased. And a hydraulic pressure source that is maintained within the set range.
The pressure release means is
The rotation shaft of the fulcrum, and a bearing that supports rotation around the axis of the rotation shaft,
The rotating shaft forms an end surface hole connected to the second oil passage, an outer peripheral hole formed on the outer peripheral surface, and a third oil passage connected along the axis.
The bearing forms a through hole through which the shaft passes along an axis, and forms a relief hole on the outer periphery to connect to the through hole,
When the excessive hydraulic pressure acts on the hydraulic cylinder beyond the set range and the rotating shaft rotates and the relief hole and the outer peripheral hole overlap in plan view, the oil in the third oil passage drains. A vertical crusher characterized by being relief.

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