JP2014121665A - Roller mill device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce a vibration load while ensuring turning-down of 30%.SOLUTION: A spring-type energizing device 100 applies a load on a roller unit 50 provided on a roller mill device 10. The energizing device 100 is equipped with a cylinder 112; a piston 114 capable of sliding in an axial direction of the cylinder; a spring member 116 abutting on the piston on a tip end side, becoming independent from the load and regulating a position on a base end side, and expanding/contracting by the movement of the piston when applying the load on the roller unit; a piston rod 110 provided so as to penetrate a substantially center portion of the piston, and capable of moving in the axial direction of the piston; a plunger 102 coupled to the roller unit on a tip end side, coupled to the piston rod on a base end side, and capable of moving the axial direction; and a shock absorber 118 provided on a base end side of the spring member, and generating attenuating force to the expanding/contracting action of the spring member.

Description

  The present invention relates to a roller mill device for pulverizing a lump such as coal, and more particularly to an urging device that adjusts a desired load to act on a roller unit provided in the roller mill device.

  A roller mill device is used to pulverize fuel coal into pulverized coal. The roller mill device has a housing, and a table in which coal is charged and rotated and the roller unit for pulverizing the coal is disposed. The roller unit includes a roller for crushing coal in cooperation with the table, and is supported by the housing in a swingable manner. In order to pulverize coal using a swingable roller unit, a hydraulic cylinder is attached to the housing as a biasing device that adjusts a desired load to act on the roller unit.

  However, the hydraulic urging device can adjust the fluctuation of the load applied to the roller unit, but requires a cost for a control system for adjusting the fluctuation. In recent years, in order to reduce the cost of the roller mill device in order to receive orders for emerging countries, the roller unit urging device is not expensive and does not require a complicated control system. There is a need for a roller mill device using a spring-type urging device that can suppress this.

  That is, in the base load plant required in the emerging countries, since the load adjustment frequency is relatively low, a base load type spring-type biasing device that applies a constant load is allowed. As the conventional spring-type technology, Patent Document 1 discloses that the pulverization roll is biased by a spring force so that the pulverization roll can be engaged with and separated from the coal on the pulverization table, and the spring force applied to the pulverization roll is electronically controlled. Disclosed is a mill device to be added by a type journal loading system.

Special table 2011-524251 gazette

  However, since the spring type roller unit urging device is a base load type that constantly applies a constant load to the roller unit, there is a demand for low load operation in which the amount of coal supply is reduced. It was difficult to perform stable pulverization even during operation. In other words, the load must be kept low during low-load operation with a turn-down of 30% in which the operation is continued with the amount of coal supply lowered to about 30%, for coexistence with the maximum load load during maximum capacity operation. Requires a large spring coefficient of the biasing device. However, in this case, vibration load caused by minute vibrations during coal pulverization becomes large. In order to reduce the vibration load, it is necessary to make the spring coefficient small, but in this case, the load at the time of low load operation becomes large, which causes a problem that hinders smooth operation of the mill device. In other words, if the load during a low load operation is large, the coal layer put on the table becomes thin, and as a result, a phenomenon that the protrusion provided on the roller unit hits the gap bolt occurs, and stable operation cannot be performed. Even with a base load type spring-type biasing device, there is a demand for 30% turn-down, but with conventional spring-type biasing devices, it is difficult to ensure both 30% turn-down and reduce vibration load. It was.

  The present invention has been made in view of the above-described problems of a spring-type biasing device provided in a conventional roller mill device. Even if the biasing device is a spring-type, a low load is ensured by ensuring 30% of turndown. It is an object of the present invention to provide a new and improved roller mill device capable of smooth device operation even during operation.

  In one embodiment of the present invention, a raw material is pulverized in cooperation with a substantially cylindrical housing, a table provided in the housing and driven to rotate about a rotating shaft extending in a vertical direction, and a pulverizing surface of the table. A plurality of roller units each including a roller and swingably supported by an arm extending inward from the housing; and the roller unit so as to urge each of the rollers toward the crushing surface of the table An urging device for applying a load to the cylinder, wherein the urging device has a cylinder, a piston slidable in the axial direction of the cylinder, a distal end abutting the piston, and a proximal end independent of the load. A spring member that is expanded and contracted by movement of the piston when a load is applied to the roller unit, and a substantially central portion of the piston is provided, A piston rod movable in the axial direction of the piston, a distal end side connected to an arm supporting the roller unit, a proximal end side connected to the piston rod, a plunger movable in the axial direction, and a spring member The present invention relates to a roller mill device comprising a shock absorber provided on the base end side and generating a damping force with respect to the expansion and contraction operation of the spring member.

  According to one aspect of the present invention, even if the spring coefficient is increased in order to secure 30% turndown, the vibration load is reduced by the shock absorber, so that smooth device operation can be performed even during low load operation.

  At this time, in one aspect of the present invention, the shock absorber includes a damping cylinder filled with viscous oil, the damping cylinder divided into a first chamber and a second chamber, and the damping cylinder. A damping piston slidable in the axial direction, a distal end side connected to the piston rod, a proximal end side connected to a substantially central portion of the damping piston, and a damping piston rod movable in the axial direction; An oil flow path formed in the axial direction of the damping piston so that the oil flows when the first chamber and the second chamber are connected and moved in the axial direction of the piston. It is good also as providing these.

  In this way, when the damping piston slides in conjunction with the expansion / contraction operation of the spring member, the viscous oil generates a damping force while flowing in the oil flow path. Can be attenuated.

  In one aspect of the present invention, the shock absorber includes a damping cylinder filled with viscous oil, the damping cylinder divided into a first chamber and a second chamber, and the damping cylinder A damping piston slidable in the axial direction, a distal end side connected to the piston rod, a proximal end side connected to a substantially central portion of the damping piston, and the damping piston rod movable in the axial direction; A bypass pipe connecting the first chamber and the second chamber, and bypassing the outside of the damping cylinder so that the oil flows when the piston moves in the axial direction; It is good also as providing.

  In this way, when the damping piston slides in conjunction with the expansion / contraction operation of the spring member, the viscous oil generates a damping force while flowing into the bypass pipe, so the expansion / contraction operation of the spring member is prevented. Can be attenuated.

  In one embodiment of the present invention, the bypass conduit may be provided with a cooling means for cooling the oil flowing in the bypass conduit.

  In this way, even when the oil in the shock absorber generates heat due to the expansion and contraction action of the spring member, the temperature can be reduced by the cooling means.

  In one embodiment of the present invention, the bypass pipe may be provided with a valve for adjusting the flow rate of the oil.

  In this way, a suitable damping force can be ensured by adjusting the oil flow rate with the valve.

  As described above, according to the present invention, since the shock absorber is provided on the base end side of the spring, even if a predetermined spring coefficient is ensured, the vibration load can be reduced and the initial compression force can be reduced. it can. For this reason, even if the urging device for applying a load to the roller unit is a base load type spring type, it is possible to achieve both a 30% turndown and a reduced vibration load. Can ensure structural soundness.

It is a figure which shows roughly the structure of the roller mill apparatus which concerns on the 1st Embodiment of this invention. It is a figure which expands and shows the area | region A in FIG. It is a figure which expands and shows the area | region B in FIG. It is a figure which shows schematically the structure of the shock absorber with which the urging | biasing apparatus of the roller mill apparatus which concerns on this embodiment is equipped. It is a figure which shows schematically the structure of the shock absorber with which the urging | biasing apparatus of the roller mill apparatus which concerns on the 2nd Embodiment of this invention is equipped.

  Hereinafter, preferred embodiments of the present invention will be described in detail. The present embodiment described below does not unduly limit the contents of the present invention described in the claims, and all the configurations described in the present embodiment are essential as means for solving the present invention. Not necessarily.

(First embodiment)
First, the configuration of the roller mill device according to the first embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a diagram schematically showing a configuration of a roller mill device according to a first embodiment of the present invention, and FIG. 2 is an enlarged view of a region A in FIG.

  The roller mill device 10 pulverizes raw material coal into pulverized coal, for example, for a coal gasification combined power generation system. The roller mill device 10 includes a roller mill main body 12 shown in cross section in FIG. 1 and a control device 14 shown as a block.

  The roller mill body 12 is installed on the foundation 18. The roller mill main body 12 has a metal housing 20, and the housing 20 has a substantially cylindrical shape. The upper lid 22 of the housing 20 is penetrated by a coal input pipe 24, and raw material coal to be pulverized is supplied into the housing 20 from above through the coal input pipe 24. The upper lid 22 is provided with a delivery hole 26, and pulverized coal pulverized from the delivery hole 26 is sent out.

  Further, a propeller-shaped rotary classifier 28 is concentrically attached to the coal input pipe 24, and a motor 30 is installed on the upper lid 22. For example, the motor 30 rotates the rotary classifier 28 via the belt 32, and the rotary classifier 28 rotates to exert a classification function of adjusting the particle size distribution of the pulverized coal.

  The foundation 18 is provided with a recess 34, and the recess 34 is located below the central portion of the housing 20. A body 38 of a speed reducer (rotating device) 36 is installed in the recess 34, and an output shaft (rotating shaft) 40 of the speed reducer 36 projects upward in the vertical direction from the recess 34. The output shaft 40 passes through the bottom wall of the housing 20 and protrudes into the housing 20, and a metal table 42 is fixed to the output shaft 40 so as to be concentric and relatively non-rotatable.

  The table 42 is disposed coaxially with the coal input pipe 24 in the housing 20. The table 42 has an annular crushing surface 43 disposed concentrically with the output shaft 40 on the upper side. When a rotational force is supplied to the reduction gear 36 from the outside, the output shaft 40 rotates integrally with the table 42. A gap between the table 42 and the bottom wall of the housing 20 is covered with a skirt 44 fixed to the table 42.

  A duct 48 is attached to the lower part of the peripheral wall 46 of the housing 20. A carrier gas such as air or nitrogen gas is fed into the housing 20 through the duct 48. The carrier gas flows out from the delivery hole 26 together with the pulverized pulverized coal. That is, a carrier gas flow path extending from the duct 48 to the delivery hole 26 is defined inside the housing 20.

  Further, for example, three roller units 50 are provided in the housing 20. In FIG. 1, two roller units 50 are arranged at 180 ° symmetrical positions for convenience of drawing, but in reality, the roller units 50 are concentrically centered on the output shaft 40 at 120 ° intervals. Is arranged.

  As shown in FIG. 2, the roller unit 50 includes a cylindrical rod holder 52, and the base end side of the rod 54 is fixed to the rod holder 52 so as not to be relatively rotatable. The rod holder 52 is arranged outside the table 42 in the radial direction and above the table 42. The rod 54 extends toward the axis of the output shaft 40 and extends obliquely with respect to the horizontal direction so that the tip of the rod 54 is closer to the table 42 than the base end.

  A rotary cylinder 58 is fitted to the distal end side of the rod 54 via a radial bearing 56 so as to be relatively rotatable, and an annular sliding member 60 is fitted to the rotary cylinder 58 so as not to be relatively rotatable. The roller 61 includes a rotating cylinder 58 and a sliding member 60. The outer peripheral surface of the sliding member 60 is configured by a curved surface that is convex outward in the radial direction.

  Coal falls onto the table 42 when it is introduced from the coal input pipe 24. Then, as the table 42 rotates, the coal enters the gap between the sliding member 60 and the table 42 and is pulverized to become pulverized coal. When coal is pulverized, the roller 61 rotates around the rod 54.

  The roller unit 50 is configured to be swingable so that the gap between the table 42 and the sliding member 60 can be adjusted. Specifically, the rod holder 52 is integrally provided with a pin 62 extending in the tangential direction of the outer periphery of the table 42.

  As shown in FIG. 2, the rod holder 52 is integrally provided with a protrusion 64 extending downward in order to define a minimum gap for avoiding contact between the table 42 and the sliding member 60. A screw 66 serving as a gap bolt is screwed into the screw hole 46. When the roller unit 50 is tilted in the direction in which the gap between the table 42 and the sliding member 60 is reduced, the gap is prevented from further reducing when the protrusion 64 comes into contact with the tip of the screw 66. That is, it is possible to prevent the crushing load from being reduced due to the decrease in the roller lift when the roller 61 is worn. The screw 66 can be rotated by a motor 68, and the control device 14 can variably control the minimum gap by controlling the rotation of the motor 68. An electric cylinder can be used instead of the screw 66 and the motor 68.

  On the other hand, an appropriate load is applied to the roller unit 50 to pulverize the coal using the swingable roller unit 50. Specifically, the rod holder 52 is integrally provided with an arm 70 extending upward, and the biasing device 100 applies a load to the tip of the arm 70. The biasing device 100 includes a plunger 102 and a spring-type pressurizing device 104, and the plunger 102 is disposed inside a port portion 106 provided on the peripheral wall 46 via a slide bearing 108. The piston rod 110 extending from the pressurizing device 100 is disposed coaxially with the plunger 102. When the piston rod 110 extends toward the inside of the peripheral wall 46, the plunger 102 is pressed against the arm 70 while moving in the axial direction. As described above, the pressure device 100 applies a load to the roller unit 50 by the plunger 102 pressing the arm 70.

  Next, the configuration of the urging device provided in the roller mill device of the present embodiment will be described with reference to the drawings. FIG. 3 is an enlarged view of a region B in FIG. 2, and is a view showing in detail the configuration of the urging device provided in the roller mill device of the present embodiment. FIG. 3 is a partial cross-sectional view for explaining the configuration of the pressure device.

  The urging device 100 applies a load to the roller unit 50 so as to urge each of the rollers 61 toward the grinding surface 43 of the table 42. In the present embodiment, the urging device 100 includes a plunger 102 and a pressurizing device 104 as shown in FIG. 3, and the pressurizing device 104 includes a cylinder 112, a piston 114, a spring member 116, and a piston rod. 110 and a shock absorber 118.

  The cylinder 112 is a substantially cylindrical hollow container. In the present embodiment, the piston 114 is reciprocated in the axial direction, and a shock absorber 118 is provided on the proximal end side. As shown in FIG. 3, the flange portion 112 a on the tip end side of the cylinder 112 includes a flange 108 a of a slide bearing 108 that can move in the axial direction with respect to the port portion 106, an adjustment bolt 113, and two lock nuts 115. Stopped. For this reason, the cylinder 112 is movable in the axial direction with respect to the port portion 106 by adjusting the position of the gap portion 117 by the position adjustment by the adjustment bolt 113 and the two lock nuts 115. As described above, in this embodiment, the adjustment bolt 113 has a function of applying extra compression to the spring member 116 while adjusting the position of the cylinder 112 by tightening.

  The piston 114 is slidable in the axial direction of the cylinder 112 in accordance with the expansion / contraction operation of the spring member 116. The spring member 116 is configured by a compression coil spring or the like whose distal end abuts on the piston 114, whose proximal end is positioned independently of the load, and expands and contracts by the movement of the piston 114 when a load is applied to the roller unit 50. . In the present specification, the “front end side” indicates a direction side (left side in FIG. 3) in which a load is applied to the roller unit 50, and the “base end side” is a side opposite to the front end side. The direction (right side in FIG. 3) is indicated.

  The piston rod 110 is provided so as to penetrate substantially the center of the piston 114 and is movable in the axial direction of the piston 114. In this embodiment, since the tip end side of the piston rod is connected to the plunger 102, the plunger 102 can be moved in the axial direction in conjunction with the movement of the piston. The plunger 102 is connected to the arm 70 supporting the roller unit 50 on the distal end side and connected to the piston rod 110 on the proximal end side, and moves in the axial direction in conjunction with the piston rod 110 as the piston 114 moves in the axial direction. .

  The shock absorber 118 is provided on the proximal end side of the spring member 116, and generates a damping force with respect to the expansion / contraction operation of the spring member 116. The shock absorber 118 is provided with a damping piston 122 that generates a damping force inside a damping cylinder 120 filled with viscous oil. A damping piston rod 124 connected to the substantial center of the damping piston 122 is connected to the piston rod 110. For this reason, when the piston 114 moves in the axial direction by the expansion and contraction operation of the spring member 116, the damping piston 122 generates a damping force in a direction against the moving direction via the piston rod 110 and the damping piston rod 124. .

  In the present embodiment, an adjustment nut 126 for adjusting the damping force of the shock absorber 118 is provided on the base end side of the shock absorber 118. By turning the adjustment nut 126, the damping piston 122, the piston rod 110, and the plunger 102 are moved to the base end side of the cylinder 112 via the damping piston rod 124, so that the damping force of the shock absorber 118 is adjusted. The At this time, if the plunger 102 is moved to the base end side of the cylinder 112 via the piston rod 110 and the damping piston rod 124, a gap is formed between the arm 70 and the plunger 102. Adjust the position. Further, during operation of the roller mill device 10, roller lift is generated by the coal layer on the table. Move to. At this time, a clearance is generated between the damping cylinder 120 and the adjustment nut 126 by the amount corresponding to the roller lift. Therefore, when further increasing the damping force of the shock absorber 118, the damping nut 126 is tightened to tighten the damping force. Can be adjusted.

  Thus, in this embodiment, since the shock absorber 118 is provided on the base end side of the spring member 116 that generates a load by the pressurizing device 10 of the biasing device 100, even if the elastic coefficient of the spring member 116 is increased. The vibration load can be reduced by the shock absorber. For this reason, even if the biasing device 100 of the roller unit 50 is a spring type, even if the spring coefficient is increased and the turndown is secured 30%, the vibration load due to the initial compressive force is reduced. Smooth device operation is possible.

  Next, the structure of the shock absorber provided in the urging device of the roller mill device according to the present embodiment will be described with reference to the drawings. FIG. 4 is a diagram schematically showing the configuration of the shock absorber provided in the urging device of the roller mill device according to the present embodiment. In FIG. 4, a part of the damping piston 122 is shown in a sectional view.

  In the shock absorber 118 of this embodiment, a damping cylinder 120 filled with viscous oil is divided into a first chamber 128 and a second chamber 130 by a damping piston 122. An oil passage 132 that connects the first chamber 128 and the second chamber 130 is formed in the damping piston 122 in the axial direction of the damping piston 122.

  For this reason, when the piston 114 moves in the axial direction by the expansion / contraction operation of the spring member 116, the damping piston 122 slides in conjunction with the expansion / contraction operation of the spring member 116. At this time, since the oil filled in the damping cylinder 120 flows through the oil flow path 132, a viscous resistance is generated, so that a damping force is generated in a direction that resists the movement of the piston 114. Thereby, the expansion and contraction operation of the spring member 116 can be attenuated.

  For example, when the amount of coal on the pulverizing surface 43 is small and the position of the roller 61 is lowered, when the spring member 116 provided in the biasing device 100 is extended, a damping force is generated in a direction against the extending direction. The spring member 116 extends slowly. On the contrary, when the amount of coal on the grinding surface 43 is large and the position of the roller 61 is raised and the spring member 116 provided in the biasing device 100 is contracted, a damping force is generated in a direction against the contracting direction. The spring member 116 gradually contracts. Thus, by providing the shock absorber 118, the frequency and amplitude of vibration of the spring member 116 can be reduced. That is, even if the rigidity of the spring member 116 is increased, the vibration load caused by minute vibrations during coal pulverization can be reduced by the shock absorber 118 to reduce the initial compression force.

  By attaching the shock absorber 118 in this way, even when the elastic coefficient of the spring member 116 is increased and a large load can be applied to the roller unit 50, the shock absorber 118 can suppress the vibration load due to the minute vibration of the roller lift. . That is, in order to ensure 30% turndown during the operation of the roller mill device 10, the spring load of the spring member 116 can be increased to ensure an increase in load due to an increase in base lift, and a vibration load due to minute vibrations can be reduced. . For this reason, even if the urging device 100 is a base load type spring type, it is possible to achieve both a 30% turndown and a reduced vibration load. Therefore, the cost of the roller mill device 10 can be reduced and the structural soundness of the device can be achieved. Can be secured.

(Second Embodiment)
Next, a roller mill device according to a second embodiment of the present invention will be described. In this embodiment, since the schematic structure of the roller mill apparatus 10 is the same as that of 1st Embodiment, description is abbreviate | omitted. In the present embodiment, the configuration of the shock absorber provided in the biasing device is different from that in the first embodiment. Regarding the present embodiment, the configuration of the shock absorber will be described with reference to the drawings.

  FIG. 5 is a diagram schematically showing a configuration of a shock absorber provided in the urging device of the roller mill device according to the second embodiment of the present invention. The shock absorber 218 of the present embodiment connects the first embodiment, the first chamber 228 and the second chamber 230, and the flow path through which oil flows is different. That is, in the present embodiment, as shown in FIG. 5, the damping cylinder 220 filled with viscous oil is divided into the first chamber 228 and the second chamber 230 by the damping piston 222. . An oil passage that connects the first chamber 228 and the second chamber 230 serves as a bypass conduit 232 that is provided around the damping cylinder 220 so as to be bypassed.

  For this reason, when the piston 114 moves in the axial direction by the expansion / contraction operation of the spring member 116, the damping piston 222 slides in conjunction with the expansion / contraction operation of the spring member 116. At this time, since the oil filled in the damping cylinder 220 flows through the bypass pipe 232 that bypasses the outside of the damping cylinder 220, a viscous resistance is generated, so that a damping force is generated in a direction that resists the movement of the piston 114. To do. Thereby, the expansion and contraction operation of the spring member 116 can be attenuated.

  Further, in the present embodiment, as a countermeasure against heat generation of oil in the shock absorber 218 by the expansion and contraction action of the spring member 116, the bypass conduit 232 includes a cooling means for cooling the oil flowing in the bypass conduit 232. A cooling device 234 is provided. As the cooling device 234, an air-cooled fan, a water-cooled cooler, or the like is applied, and if the bypass pipe 232 is formed of a metal such as copper having a high thermal conductivity, a cooling device serving as a cooling means is not provided. Can also be a cooling means for cooling the oil.

  Further, in the present embodiment, in order to adjust the oil flow rate and ensure a suitable damping force, the bypass conduit 232 is provided with a valve 236 such as a check valve for adjusting the oil flow rate. In this embodiment, the valve 236 is provided at the front stage of the cooling device 234, but the valve 236 may be provided at the rear stage of the cooling device 234.

  In the present embodiment, the case where there is one bypass conduit 232 is described, but the installation mode of the bypass conduit is not limited to the example of FIG. For example, two bypass conduits are provided to bypass the oil flow from the first chamber 228 to the second chamber 230 and the oil flow from the second chamber 230 to the first chamber 228. A separate bypass line may be provided. Then, a valve that adjusts the oil flow rate may be provided in each bypass pipe to generate a more suitable damping force.

  Thus, also in this embodiment, by attaching the shock absorber 218, even if the elastic coefficient of the spring member 116 is increased, the shock absorber 118 can suppress the vibration load due to the minute vibration of the roller lift. That is, in order to ensure 30% turndown during operation of the roller mill device 10, the spring load of the spring member 116 provided in the biasing device 100 is increased to ensure an increase in load due to an increase in base lift, and vibration load due to minute vibrations. Can be reduced. For this reason, even if the urging device 100 is a base load type spring type, it is possible to achieve both a 30% turndown and a reduced vibration load. Therefore, the cost of the roller mill device 10 can be reduced and the structural soundness of the device can be achieved. Can be secured.

  As described above, each embodiment of the present invention has been described in detail. However, it is easily understood by those skilled in the art that many modifications that do not substantially depart from the novel matters and effects of the present invention are possible. You can understand. Therefore, all such modifications are included in the scope of the present invention.

  For example, a term described with a different term having a broader meaning or the same meaning at least once in the specification or the drawings can be replaced with the different term in any part of the specification or the drawings. Further, the configuration and operation of the roller mill device and the urging device included in the roller mill device are not limited to those described in the present embodiment, and various modifications can be made.

DESCRIPTION OF SYMBOLS 10 Roller mill apparatus 12 Roller mill main body 14 Control apparatus 18 Base 20 Housing 22 Upper cover 24 Coal input pipe 36 Reduction gear 40 Output shaft 42 Table 43 Grinding surface 50 Roller unit 61 Roller 70 Arm 100 Energizing apparatus 102 Plunger 104 Pressurizing apparatus 110 Piston rod 112 Cylinder 114 Piston 116 Spring member 118, 218 Shock absorber 120, 220 Damping cylinder 122, 222 Damping piston 124, 224 Damping piston rod 128, 226 First chamber 130, 230 Second chamber 132 Oil flow path 232 Bypass pipe line 234 Cooling device (cooling means)
236 Valve

Claims (5)

A substantially cylindrical housing;
A table provided in the housing and driven to rotate about a rotation axis extending in a vertical direction;
A plurality of roller units each including a roller for crushing the raw material in cooperation with a crushing surface of the table, and supported by an arm extending inward from the housing so as to be swingable;
A biasing device that applies a load to the roller unit so as to bias each of the rollers toward the grinding surface of the table,
The biasing device is
A cylinder,
A piston slidable in the axial direction of the cylinder;
A spring member that is in contact with the piston on the distal end side, the position of the proximal end side is defined independently of the load, and that expands and contracts by movement of the piston when a load is applied to the roller unit;
A piston rod provided through substantially the center of the piston and movable in the axial direction of the piston;
A distal end side connected to the arm supporting the roller unit, a proximal end side connected to the piston rod, and a plunger movable in the axial direction;
A roller mill device comprising: a shock absorber provided on the base end side of the spring member and generating a damping force with respect to the expansion and contraction of the spring member. The shock absorber is
A damping cylinder filled with viscous oil;
A damping piston that divides the damping cylinder into a first chamber and a second chamber and is slidable in an axial direction of the damping cylinder;
A tip end side is connected to the piston rod, a base end side is connected to a substantially central portion of the damping piston, and a damping piston rod movable in the axial direction;
An oil flow path formed in the axial direction of the damping piston so that the oil flows when the first chamber and the second chamber are connected and moved in the axial direction of the piston. The roller mill device according to claim 1, further comprising: The shock absorber is
A damping cylinder filled with viscous oil;
A damping piston that divides the damping cylinder into a first chamber and a second chamber and is slidable in an axial direction of the damping cylinder;
A tip end side is connected to the piston rod, a base end side is connected to a substantially central portion of the damping piston, and a damping piston rod movable in the axial direction;
A bypass pipe that connects the first chamber and the second chamber, and is bypassed outside the damping cylinder so that the oil flows when the piston moves in the axial direction. The roller mill device according to claim 1, further comprising:   The roller mill device according to claim 3, wherein the bypass pipe is provided with cooling means for cooling the oil flowing in the bypass pipe.   The roller mill device according to claim 3 or 4, wherein a valve for adjusting the flow rate of the oil is provided in the bypass pipeline.

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