JP3723089B2 - Vertical mill - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a vertical mill that feeds crushed material between a rotary table and a roller tire to crush and crush.
[0002]
[Prior art and problems]
A vertical mill will be described with reference to FIGS. 1 and 11 showing an embodiment of the present invention. A table 8 is rotatably provided in a mill casing (upper and lower frames 2 and 3), and a roller tire is provided on the table 8. 9, the crushed material a is fed between the table 8 and the roller tire 9 to be crushed under pressure or crushed under pressure.
[0003]
In crushing (crushing) with this vertical mill, if the rotation speed of the table 8 is increased in order to increase crushing efficiency or obtain a crushed product b (pulverized product b ′) having a particle size in a required range, The crushed material a easily moves to the outside by centrifugal force, and is discharged without being sufficiently crushed. For this reason, conventionally, the table rotation speed cannot be increased so much, and there are many problems.
[0004]
An object of the present invention is to prevent the crushed material a from being discharged without being crushed outside the table even when the number of rotations of the table is increased.
[0005]
[Means for Solving the Problems]
In order to achieve the above object, the present invention is configured to drop the crushed material in the center of the table. The crushed material in the center of the table has a long distance to the outer periphery of the table, and the centrifugal force is also small, so the time for crushing and crushing between the table and the roller tires increases, resulting in crushed material that is discharged without being crushed. Will be less.
[0006]
DETAILED DESCRIPTION OF THE INVENTION
As an embodiment of the present invention, in a vertical mill that crushes and crushes crushed material between a rotating table and a roller tire adjacent to the table, the table has a predetermined gap above the table. Then, a cylindrical charging chute for crushed material is provided, and the charging chute is gradually reduced in diameter downward. In this way, when the diameter is gradually reduced, the crushed material to be introduced gradually gathers in the center and falls (guided) to the center of the table.
[0007]
In this configuration, the inclination angle of the roller tire with respect to a perpendicular (vertical line) passing through the center of the table is 20 ° to 40 °, preferably 25 ° to 40 °, and the inclination angle that is the horizontal line of the horizontal surface of the concave curved surface of the table is the same. It is good to do. Moreover, each curvature of the concave curved surface of a table and a roller tire outer peripheral surface can be made the same.
[0008]
If it does in this way, a table outer periphery will become a place comparatively higher than the position where a crushed material is pinched and crushed between a table concave curved surface and a roller tire, and jumping out by centrifugal force will decrease compared with the past. Therefore, the crushed material in the concave curved surface of the table is sufficiently crushed without being discharged (suppressed) by centrifugal force until a predetermined particle size is obtained. Thereby, a product having a good particle size distribution can be obtained. The reason why the inclination angle is set to 20 ° or more is that when the angle is less than 20 °, a dam ring for preventing the crushed material from jumping out from the table is necessary as in the conventional case. On the other hand, the reason why the angle is set to 40 ° or less is that when the angle exceeds 40 °, the lateral protrusion of the roller tire increases and the width of the machine increases.
[0009]
In order to prevent the machine width from increasing, it is only necessary to bring the roller tire closer to the center, but at that time the throwing chute gets in the way. For this reason, it is a preferable aspect to make the charging chute taper downward and avoid the roller tire approaching its center.
[0010]
In this saddle type mill, the table rotating means and the lifting means can be installed on the ground, respectively, and the rotating force can be transmitted from the rotating means to the rotating shaft of the table by absorbing the lifting and lowering of the rotating shaft. Thus, if the lifting means and the rotating means are separated from each other, the lifting means does not need to move the rotating means up and down, and can be reduced in size accordingly.
[0011]
Specifically, in a vertical mill that sends crushed material between a rotating table and a roller tire adjacent to the table and crushes and crushes the table, the table is supported by a hydraulic cylinder or the like so as to be lifted and lowered. Rotating means such as a motor for the table is installed on the ground, and the rotational force is transmitted from the rotating means to the rotating shaft of the table by absorbing the elevation of the rotating shaft.
[0012]
As a specific means for absorbing the raising and lowering of the rotating shaft, a configuration in which the table can be moved in the axial direction and an integral pulley is fitted in the rotating direction can be adopted. In this configuration, the pulley can be rotated by the rotating means, and the rotational force can be absorbed and transmitted to the rotating shaft by the movement of the pulley in the axial direction with respect to the rotating shaft.
[0013]
As another specific means, a structure in which a spur gear is fitted on the rotation shaft of the table and a pinion rotated by the rotation means is engaged with the spur gear can be adopted. In this configuration, the elevation of the rotating shaft is absorbed by the latitudinal latitude of the meshing spur gear, and the rotational force is transmitted to the rotating shaft.
[0014]
Furthermore, as another specific means, a hydraulic cylinder serving as the lifting means is provided on the ground so as to be rotatable about its axis, and the piston rod of the hydraulic cylinder is used as the rotating shaft of the table, and the piston rod is used as the cylinder. A configuration in which the casing cannot be rotated and the cylinder casing can be rotated by the rotating means may be employed. In this configuration, the elevation is absorbed between the cylinder casing and the piston rod.
[0015]
In addition, in any of the crushing and crushing vertical mills, as another specific means of the absorbing means, a casing of a hydraulic cylinder serving as the lifting means is fixed to the ground, and the table rotates on the piston. The shaft may be integrated in the up-and-down direction, and the table rotation shaft may be configured to be rotatable to the casing and to transmit the rotational force of the motor by absorbing the lifting and lowering of the piston. The rotation of the table rotation shaft with respect to the casing may be obtained by being rotatable with respect to the piston (see the embodiment), but may be obtained by making the piston rotatable with respect to the casing.
[0016]
In the configuration using these hydraulic cylinders, the motor, the hydraulic cylinder, and the table are aligned on the same straight line if the table rotating shaft passes through the casing and has the same axis as the output shaft of the motor. Therefore, the installation space for the motor and hydraulic cylinder on the ground is reduced, and the mill itself can be reduced in size.
[0017]
As for the means for absorbing the elevation of the piston (rotating shaft), if a flexible joint that is movable in the axial direction, for example, an Oldham joint, is adopted, it is possible to absorb axial misalignment, etc., and high manufacturing accuracy is not required. Production costs can be reduced. At this time, the rotational force of the motor is transmitted to the table rotation shaft directly or via the piston by the Oldham coupling. That is, the table rotation shaft is directly rotatable about the piston, and when the piston is interposed, the table rotation shaft is integrated with the piston in the rotation direction. Even in this integrated case, it can be directly transmitted to the table rotation shaft.
[0018]
Moreover, if the opening of the crushed material charging chute is exposed on the upper surface of the table and the gap between the chute opening and the table upper surface can be adjusted by raising and lowering the charging chute, the amount of crushed material charged can be adjusted by adjusting the gap. Can be adjusted. Specifically, the charging chute is formed by a telescopic double pipe, the pipe facing the upper surface of the table is movable in the axial direction with respect to another pipe by a cylinder, and the gap is set in the table. -It is possible to adopt one that is detected by a feeder opening detection mechanism and input to the control unit, and the gap is adjusted and controlled via the control unit.
[0019]
Furthermore, in any of the above vertical mills, the roller tire is fixed to the casing so as not to swing, and the table is set up and down so that the gap between the roller tire and the roller tire is constant. A configuration can be adopted in which the number can be rotated at high speed. In such a configuration, the table rotation speed can be set to be significantly large. In the conventional type in which the roller tires are pressed by a pressure spring, the rolling force is adjusted independently for each roller tire, so when trying to increase the table rotation speed, the rolling force from the roller tires varies and the particle size is appropriate. However, if the roller tire is fixed as in the above configuration and the table is raised and lowered so that the gap is always constant, the number of rotations of the table is several times that of the conventional system. Even if it is increased to an appropriate level, it is possible to ensure an appropriate particle size.
[0020]
【Example】
One embodiment is shown in FIGS. 1 to 6, and in the vertical mill of this embodiment, upper and lower frames (casings) 2 and 3 are fixed on a machine base frame 1, and the quartile around the inner surface of the lower frame 2 is shown. The arm 2 a is provided to the hydraulic cylinder 10 via the support ring 4. A lid 5 is attached to the upper frame 3, and a cylindrical charging chute 6 for the crushed material a is provided at the center of the lid 5. The charging chute 6 is gradually reduced in diameter toward the lower side, and the reduced-diameter shape line has an arc shape protruding inward.
[0021]
A rotary table 8 is provided at the axial center of the hydraulic cylinder 10, and a roller tire 9 is provided around the table 8 in three equal parts. When the roller tire 9 is freely rotatable on the upper frame 3 and the table 8 is rotating, if the crushed material a is introduced from the charging chute 6, the crushed material a is transferred to the roller tire 9 and the table 8. Crushing between them. The angle θ between the center line O of the rotary table 8 and the roller tire 9 is 20 ° to 40 °, preferably 25 ° to 40 °. The inclination angle θ ₁ formed with the horizontal surface of the concave curved surface of the table 8 is also the same as the angle θ, and preferably θ = θ ₁ . Further, the curvature of the concave curved surface of the rotary table 8 and the outer peripheral surface of the roller tire 9 are the same.
[0022]
An annular dam ring 71 is provided on the outer periphery of the rotary table 8, and this dam ring 71 is supported by a holding material 72. The holding material 72 is supported by a cylinder 73 via an inclined surface 72a. On the inclined surface 74a. The cylinder 73 is swingably supported by a frame 75 fixed to the lower surface of the table 8, and moves up and down the lifting member 74 according to an instruction from the control unit 80. By this raising / lowering, the dam ring 71 moves up and down via the inclined surfaces 72a and 74a, and finely adjusts the discharge amount of the crushed material a from the table 8. Although three cylinders 73 are provided at equal intervals around the cylinder 73, the number thereof is arbitrary. As shown in FIG. 5, the control unit 80 includes an oil tank 81, a pump 82, a motor 83, a solenoid valve 84, and a distribution valve 85, and hydraulic pressure is applied to each cylinder 73 via a hydraulic pipe 86.
[0023]
As shown in FIG. 4, the power supply to the control unit 80 and the transmission of the control signal are conducted from the outside into the annular container 87 concentric with the rotating shaft 8a by the electric wire 86a, and to the sol-like conductive liquid 87a in the container 87. It is connected. On the other hand, the ring-shaped conductor piece 89 is inserted into the conductive liquid 87 a from the support base 80 a of the control unit 80 via the insulating plate 88, and the electric wire 86 b is led from the conductor piece 87 to the control unit 80. The number of power supply and signal transmission configurations of the container 87 and the like is determined as appropriate depending on the number of power supply and signal transmission, and regardless of the rotation of the table 8, the wires from the external wire 86a through those members (conductive liquid 87a and the like) Via 86b, power is supplied to the control unit 80 and a control signal is transmitted. The control signal can be wireless. In this case, only the power supply is configured. Even when the dam ring 71 moves up and down, the conductor piece 89 does not come out of the conductive liquid 87a. The lifting mechanism of the dam ring 71 can be omitted. At this time, the dam ring 71 may be fixed to the table 8.
[0024]
A conical pointed member 90 is provided at the center of the table 8, and the crushed material a is guided around the table 8 by the pointed member 90. A hardened layer 90 a is formed on the surface of the pointed member 90. Further, the charging chute 6 has a funnel shape that is squeezed downward. Due to this shape, the crushed material a hits the pointed member 90 and is reliably guided around the table 8. The pointed member 90 may be screwed to the table 8, but can be formed integrally with the table 8.
[0025]
The hydraulic cylinder 10 is an annular type described in Japanese Patent Publication No. 5-29508. As shown in FIG. 2, the casing 11 is fixed to the support ring 4, and the cylindrical piston 12 is moved up and down in the casing 11. It is provided freely. In the casing 11, hydraulic chambers 13a and 13b are formed above and below the piston 12, and oil pipes 14a and 14b are connected to both chambers 13a and 13b, respectively, and the upper hydraulic chamber 13a is supplied with oil and the lower hydraulic chamber 13b is discharged. The piston 12 is lowered by being oiled, and the piston 12 is raised by being supplied to the lower hydraulic chamber 13b and discharged from the upper hydraulic chamber 13a. A rotating shaft 8a of the table 8 is inserted into the piston 12 through a bearing 15 so as to be rotatable, and is integrated in the ascending / descending direction. In addition, a linear scale 16 is attached to the piston 12, and the lifting amount of the piston 12 is detected by the scale 16.
[0026]
The hydraulic circuit 30 for raising and lowering the piston is configured as shown in FIG. 6, and the upper and lower hydraulic chambers 13a in the cylinder 11 are connected from the tank T to the motor / pump 31 via the switching valve 32 and check valves 33 and 34. Oil pressure is applied to 13b. Therefore, as described above, when the upper hydraulic chamber 13a is refueled by the switching valve 32 (the state shown in FIG. 5B), the piston 12 is lowered, and conversely, the lower hydraulic chamber 13b is refueled (same as above). The state of the figure (a)), the piston 12 rises. The raising / lowering of this piston 12 is the raising / lowering of the table 8, and the raising / lowering amount (gap (delta) _{1 of the} table 8 and the roller tire 9) is detected by the linear scale 16, and if it becomes a required position, oil supply will be stopped.
[0027]
That is, when the gap δ ₁ is changed in the narrowing direction, for example, when the gap δ ₁ is narrowed because the gap is widened due to wear, the hydraulic pressure is supplied from the hydraulic pump 31 by switching the switching valve 32 as shown in FIG. When applied to the lower hydraulic chamber 13b of the hydraulic cylinder 10 via the oil pipe 14b, the piston 12 rises as the hydraulic pressure rises, and the table 8 also rises synchronously. As the piston 12 rises, the hydraulic pressure in the upper hydraulic chamber 13a also rises, and the spring in the check valve 34 is released by this increase in hydraulic pressure, and the oil in the upper hydraulic chamber 13a flows into the tank T. To do. When the piston 12 rises by a set amount, the hydraulic pump 31 is stopped.
[0028]
On the other hand, when the setting of the gap δ ₁ is increased in a widening direction, for example, to widen the particle size of the crushed material slightly, the switching valve 32 is switched as shown in FIG. When the hydraulic pressure is applied to the upper hydraulic chamber 13a of the hydraulic cylinder 10 via the oil pipe 14a by the pump 31, the piston 12 descends and the table 8 also descends in synchronization. At this time, the oil in the lower hydraulic chamber 13b flows into the tank T through the oil pipe 14b because the oil pressure in the oil pipe 14b is released by applying a pilot pressure to the check valve 33. When the piston 12 is lowered by the set amount, the switching valve 32 is switched from FIG. 6B to FIG. 6A to stop the motor / pump.
[0029]
The gap δ ₁ at the time of adjustment is detected by a gap detection mechanism of the table 8, that is, a linear scale 16 and the like, and the detection result is input to a control unit of this vertical mill not shown. In the case of changing the setting of the gap δ ₁ , when the changed setting value is input to the control unit, the hydraulic circuit 30 is operated by the control unit and becomes a predetermined value.
[0030]
This action, in the condition that the required gap [delta] _1, the hydraulic cylinder 10 is vertically hydraulic chambers 13a, 13b are both state constant pressure is enclosed. That is, because the lower hydraulic chamber 13b is prevented from backflow by the check valve 33, only pressure due to its own weight such as the table 8 is generated, while the upper hydraulic chamber 13a is driven by the spring of the check valve 34. Backflow is prevented, and therefore, the upper and lower hydraulic chambers 13a and 13b are in a state of being balanced by the pressure. The upper and lower hydraulic chambers 13a and 13b are not necessarily balanced, and the upper hydraulic chamber 13a may be open. For this reason, the check valve 34 may not be provided. Incidentally, the check valve 34 adjusts the return amount of the oil in the upper hydraulic chamber 13a when the piston 12 is raised when the clearance is set. If the upper hydraulic chamber 13a is opened, the piston 12 will rise quickly when oil is introduced into the lower hydraulic chamber 13b. For this reason, a throttle valve or an orifice can be used in place of the check valve 34. Thus, the setting of the gap δ ₁ is easy because it is only necessary to move the table 8 up and down by one hydraulic cylinder 10 and the hydraulic circuit 30.
[0031]
Further, when a large crushed material a enters between the roller tire 9 and the table 8 during the crushing action, or when the layer thickness increases and a high load (impact force) is generated, pressure is generated in the lower hydraulic chamber 13a. Oil is supplied to the upper hydraulic chamber 13b through the relief valve 35. In this oil supply, since the upper and lower hydraulic chambers 13a and 13b have the same cross-sectional area, the oil having a capacity equal to the moving amount of the piston 12 moves and absorbs the impact force. The relief valve 35 is preferably a high flow type. In the figure, 36 is a strainer, 37 is a pressure gauge, 37a is an oil level gauge, 38 is an air freezer, and 39 is a relief valve. The relief valve 39 has a hydraulic pressure in the oil pipe 14b from the pump 31 for some reason. Relieve the pressure when it becomes abnormally high.
[0032]
A support frame 17 is fixed to the lower portion of the support ring 4, a reduction gear N is provided on the frame 17, and a motor M is connected to the reduction gear N. The rotating shaft (output shaft) 20 of the speed reducer N and the table rotating shaft 8a are connected to each other by an Oldham joint 21, which is a flexible joint movable in the axial direction with the same axis. As shown in FIG. 3, the Oldham coupling 21 includes a member 21a fixed to the motor rotating shaft 20, a member 21b fixed to the table rotating shaft 8a, and a floating cam fitted to both the members 21a and 21b. And the member 21c. The transmission method of the rotational force to the output shaft 20 can also be performed through a motor, a speed reducer, etc. that are not installed on various rotational shafts described later and well-known.
[0033]
The member 21b of the Oldham coupling 21 is integrated with the rotating shaft 8a by screwing a retaining ring 21d to both the shafts 21c and 8a, and the member 21a is integrated with the rotating shaft 20 by a key. The cam 21c is supported by a guide 21e fixed to the member 21a so as to be movable only in one direction via a stop plate 21f and a packing 21g. This Oldham joint 21 can transmit rotational force even if the shaft centers of both rotary shafts 8a and 20 are misaligned, and the assembly thereof is easy. The joint portion is prevented from entering dust by covers 22a and 22b provided on the member 21a and member 21b sides, respectively. As the flexible joint, a slide (sliding type) shaft joint that can move the table 8 up and down with respect to the fixing of the motor M, for example, a gear shaft joint, a spline shaft joint, and the like described later can be used instead of the Oldham joint 21.
[0034]
This embodiment is the above construction, the upper and lower hydraulic chamber 13a of the hydraulic cylinder 10, by supplying and discharging oil to 13b, by elevating the table 8, the gap [delta] ₁ of the roller tire 9 to a required value . After that, when the table 8 is rotated by the motor M and the crushed material a is introduced, the crushing crushing is performed while maintaining the gap δ ₁ between the table 8 and the roller tire 9, so that the uniform particle size without causing pulverization. The crushed material b falls downward from the table 8 periphery. At this time, the crushed material a fed from the feeding chute 6 contacts the pointed member 90 and diffuses around it to be crushed smoothly. Further, the dam ring 71 is appropriately moved up and down to discharge the crushed material b having a required particle size width from the table 8.
[0035]
In the vertical mill configured as described above, the roller tire 9 is fixedly installed on the upper frame 3 and cannot be swung, and the above adjustment is performed in advance so that the clearance δ ₁ becomes a required value with respect to the roller tire 9. Is called. For this reason, the number of rotations of the table 8 by the motor M can be set to be significantly large. This is because the roller tire 9 is set at an equal interval δ _{1 with} respect to the table 8, so that the crushing particle size can be made uniform even if the rotational speed of the table 8 is increased.
[0036]
For example, in the illustrated example, the rotational speed of the table 8 can be set to 60 to 120 rpm, which is 2 to 3 times faster than the conventional example of 30 to 40 rpm, As a result, the crushing (crushing) capacity (production capacity) can be greatly increased.
[0037]
FIGS. 7 to 11 show other embodiments, and in each case, the dam ring 71 and its elevating mechanism are attached as in the above embodiment, but may be omitted. At that time, the dam ring 71 can be fixed to the table 8. 7 and 8, the roller tire 9 is supported by a trunnion joint 9 b and pressed against the table 8 by a pressure spring 45. The rotating shaft 8 a of the table 8 is surrounded by an elevating cylinder 47, and is supported rotatably by a radial bearing 48 at the upper part of the elevating cylinder 47. A thrust self-aligning roller bearing 52 is provided between the table 8 and the lifting cylinder 47.
[0038]
A pulley 49 is fitted on the rotary shaft 8a, and the pulley 49 is supported by bearings 50 and 51 so that the upper and lower sides of the pulley 49 can rotate freely. (Frame) 2 is fixed. As shown in FIG. 8A, the rotating shaft 8 a and the pulley 49 include a vertical protrusion 53 provided on the outer peripheral surface of the rotating shaft 8 a and a vertical groove 56 formed on the inner peripheral surface of the pulley 49. Are engaged, and the rotation shaft 8a and the pulley 49 are slidable in the vertical direction and are integrated in the rotation direction. That is, it is a spline bearing. The rotating shaft 8a and the pulley 49 need only slide in the vertical direction and engage (integrally) in the rotating direction. For example, as shown in FIG. A well-known configuration may be employed such that the shaft 8a has a quadrangular cross section and the inner peripheral surface of the pulley 49 is engaged with the square. The pulley 49 is connected to a pulley 55 of a motor M with a speed reducer fixed on the ground G outside the casing 2 by a V belt 57. Instead of the V-belt 57, known transmission means such as a timing belt may be employed.
[0039]
A bottom plate 58 is fixed to the lower part of the lifting cylinder 47, and a hydraulic cylinder 59 as a lifting means is provided on the ground G below the bottom plate 58. The bottom plate 58 is fixed so that the piston rod 59a of the hydraulic cylinder 59 cannot rotate.
[0040]
In this embodiment, the hydraulic cylinder 59 is moved up and down, so that the lifting cylinder 47, the rotary shaft 8a, the table 8 and the like are integrally moved up and down, so that the gap δ ₁ between the table 8 and the roller tire 9 is increased. adjust. At this time, the gap δ ₁ is detected by measuring the expansion / contraction amount of the hydraulic cylinder 59 (actually a piston) with a displacement meter such as the linear scale 16. Further, the pulley 49 cannot move in the vertical direction by the bearings 50 and 51 fixed to the casing 2, but when the protrusion 53 slides in the groove 56, the rotary shaft 8 a moves up and down with respect to the pulley 49. Absorption is done.
[0041]
When the required gap δ ₁ is reached, the motor M is driven to rotate the table 8, and the rotation of the pulley 49 is reliably transmitted to the rotary shaft 8 a by the engagement of the protrusion 53 and the groove 56. 8 rotates. The crushed material a is supplied onto the rotating table 8 and is crushed between the roller tire 9 urged by the pressure spring 45 and the table 8.
[0042]
In the embodiment of FIG. 9, a spur gear 62 is fitted and fixed to the rotating shaft 8 a, and a pinion 63 is engaged with the spur gear 62. The pinion 63 is rotated by a motor M with a reduction gear via a bevel gear box 64.
[0043]
In this saddle type mill, the rotary shaft 8 a can be moved up and down by a hydraulic cylinder 59 and receives a rotational force via a pinion 63 and a spur gear 62. At this time, the width (height) of the spur gear 62 is set larger than that of the pinion 63, and even when the rotary shaft 8a is moved up and the position of the spur gear 62 is changed, the engagement between the spur gear 62 and the pinion 63 is ensured. The rotation shaft 8a can be rotated.
[0044]
In the embodiment of FIG. 10, the rotating shaft 8a is composed of a rotating shaft portion (piston rod) 59a having a square cross section and a piston portion 68b having a circular cross section, and the piston portion 59c has a sectional area larger than that of the rotating shaft portion 59a. It is designed to be large and is housed in the casing 59b of the hydraulic cylinder 59. The upper surface of the cylinder casing 59b is formed as an opening having a square cross section, and the rotation shaft portion 59a having a square cross section passes through the opening, so that rotation with respect to the cylinder casing 59b is prohibited, and only vertical movement is allowed. The
[0045]
The hydraulic cylinder 59 is rotatably supported by a support cylinder 60 fixed to the ground G via a bearing 51 and is installed on the ground G. A rotary joint 65 for supplying and discharging oil is provided at the lower end of the hydraulic cylinder 59. Is provided. Through this rotary joint 65, oil is supplied to and discharged from the hydraulic cylinder 59 by a hydraulic pump (not shown), the piston portion 59c moves up and down, and the table 8 and the rotary shaft 8a move up and down integrally.
[0046]
A pulley 49 ′ is fixed to the cylinder casing 59b. When the pulley 49 ′ is rotated by a motor M (not shown), the cylinder casing 59b rotates and the table 8 also rotates.
[0047]
Although each said Example was the case of crushing sand manufacture etc., these each Example is employable also in the case of crushing. At this time, for example, as shown in FIG. 11, the crushed material a is introduced from the screw feeder 60 onto the table 8, and the pulverized material b ′ is conveyed to the air introduced from the lower part of the casing 2 and rises. It can be set as the vertical mill for grinding | pulverization led to collectors, such as a bag filter, through.
[0048]
7 and the subsequent embodiments, the hydraulic cylinder 59 is controlled by the hydraulic circuit 30 shown in FIG. Further, the roller tire 9 does not apply a pressing force by the pressure spring 45, and may not be able to swing as shown in FIG.
[0049]
Further, the present invention can also be adopted in the case of FIG. Further, the present invention can be applied to a table in which the rotary table 8 does not move up and down. When the dam ring 71 can be raised and lowered, θ and θ ₁ can be set to 20 degrees or less, for example, 10 ° to 15 ° or even 20 °.
[0050]
【The invention's effect】
According to the present invention, the crushed material can be supplied to the center of the table as described above. Therefore, efficient crushing can be performed and a crushed material having a required particle size range can be easily obtained.
[Brief description of the drawings]
FIG. 1 is a schematic cross-sectional view of an embodiment. FIG. 2 is a cross-sectional view of a main part in a state where a piston of the embodiment is raised. FIG. 3 is an exploded perspective view of an Oldham joint of the embodiment. FIG. 5 is a layout diagram of hydraulic equipment for raising and lowering the dam ring of the same embodiment. FIG. 6 is a hydraulic circuit diagram of the same embodiment. FIG. 7 is a schematic sectional view of the main portion of another embodiment. 8] Cross-sectional view showing examples of fitting of table rotation shaft and pulley in the same embodiment. [FIG. 9] Cross-sectional view of main part of other embodiment. [FIG. 10] Cross-sectional view of main part of other embodiment. 11 is a schematic sectional view of an essential part of another embodiment.
a crushed material b crushed material b 'crushed material G ground M Table rotation motor 2, 3 Mil casing (upper and lower frames)
6 Input chute 7a Input chute cylinder 7c Table feeder opening detection mechanism (linear scale)
8 Table 9 Roller tire 10 Hydraulic cylinder 11 Cylinder casing 12 Pistons 13a, 13b Hydraulic chamber 20 Motor rotating shaft (output shaft)
21 Oldham coupling 30 Hydraulic circuit 45 Pressure spring 47 Lifting cylinder 49, 49 'Rotary shaft pulley 55 Pulley 59 Hydraulic cylinder 59b Cylinder casing 60 Support cylinder 62 Spur gear 63 Pinion 71 Dam ring 72 Dam ring holding material 73 Lifting cylinder 72a, 74a Inclined surface 74 Elevating member 90 Pointed member

Claims (1)

A vertical mill that crushes and crushes the crushed material a between a rotating table 8 and a roller tire 9 adjacent to the table 8,
A crushed material cylindrical charging chute 6 having a predetermined gap with the table 8 is provided at the upper center of the table 8, and the charging chute 6 is gradually reduced in diameter toward the lower side. A vertical mill characterized by a convex arc shape on the inside .

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