JP3569195B2 - Vertical mill - Google Patents

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a vertical mill in which a rotary table moves up and down.
[0002]
[Prior art]
A vertical mill will be described with reference to FIGS. 1 and 9 showing an embodiment of the present invention. A table 8 is rotatably provided in a mill casing (upper and lower frames 2, 3), and a roller tire is mounted on the table 8. 9, the crushed objects a and a 'are fed between the table 8 and the roller tire 9 to perform crushing crushing or crushing crushing.
[0003]
In the pulverization by the vertical mill, when the supply amount of the crushed material a ′ fluctuates, the rolling force of the roller tire 9 and the gap between the roller tire 9 and the table 8 are adjusted so that the particle size of the crushed material b ′ is in an appropriate range. δ ₁ Need to be adjusted. This adjustment is performed by adjusting the pressing force of the roller tire 9 or moving the table 8 up and down. At this time, in the type in which the roller tire 9 is pressed by the pressing spring 45, the pressing force of the roller tire 9 is determined by the spring pressure, and it is difficult to adjust the rolling force or the like. It corresponds by raising and lowering.
[0004]
Examples of vertical mills capable of moving the table 8 up and down include those described in JP-A-2-144160 and JP-A-9-276726. The technique described in the former publication is such that a table 8 and an elevator equipped with a drive motor thereof can be moved up and down by a screw-driven pantogram-type elevator. The technique described in the latter publication uses various types of elevators. The elevator can be moved up and down.
[0005]
In addition, crushing, for example, sand making, is performed by this vertical mill, and an example thereof is described in Japanese Utility Model Publication No. 3-17945. The technique described in this publication adjusts the pressing force of the roller tire 9 with a compression spring and an adjustment bolt to reduce the rolling force and the gap δ. ₁ Adjust
[0006]
[Problems to be solved by the invention]
The technology described in both publications related to the above-mentioned pulverization, since the table 8, the motor and the reduction gear are mounted on the elevating table, their weight becomes heavy, and thus, a large elevating means is required, Since the lifting platform is not fixed to the ground G, the lifting platform vibrates greatly due to the crushing action, hinders a smooth crushing action, and generates noise. In addition, it is necessary to provide a means for resisting the rotational force of the table 8 on the elevating table.
[0007]
Further, also in the crushing of sand making or the like, it is preferable to adjust the rolling force by moving the table 8 up and down, and in this case, it is preferable to avoid the same problem as the crushing.
[0008]
By the way, the roller tire 9 is swung up and down so that the gap δ ₁ Means must be adjusted for each roller tire 9, the operation is complicated, and the adjustment control is not easy. In addition, if the pressing means of the roller tire 9 protrudes from the mill casing, the size of the mill itself is increased, and the pressing means is generally expensive (see Japanese Utility Model Publication No. 3-17945).
[0009]
SUMMARY OF THE INVENTION It is an object of the present invention to solve the above-mentioned problems, to reduce the size of a table elevating means, to suppress an eccentric load when the table rotates, and to reduce vibration.
[0010]
Another object of the present invention is to provide a vertical mill capable of miniaturizing a table elevating means, suppressing an eccentric load at the time of rotating the table, reducing vibration, and setting a large number of rotations of the table. Is to get.
[0011]
[Means for Solving the Problems]
In order to solve the above problems, the present invention provides a table rotating means and an elevating means which are respectively installed on the ground, and absorbs the elevating of the rotating shaft from the rotating means to a rotating shaft of the table to transmit a rotating force. It was.
[0012]
In this way, if the lifting means is separated from the rotating means, the lifting means does not need to raise and lower the rotating means, and can be downsized accordingly.
[0013]
BEST MODE FOR CARRYING OUT THE INVENTION
As an embodiment of the present invention, in a vertical mill for crushing, in a vertical mill in which a crushed object is fed between a rotating table and a roller tire close to the table to crush and crush, the table is hydraulically driven. It is supported by a cylinder or the like so as to be able to ascend and descend, and its elevating means and rotating means such as the motor of the table are installed on the ground, respectively, and the rotating means absorbs the elevating movement of the rotating shaft to the rotating shaft of the table, thereby reducing the rotational force. A configuration adapted to transmit may be employed.
[0014]
As a specific means for absorbing the elevation of the rotating shaft, a configuration in which a pulley that is movable in the axial direction of the rotating shaft of the table and is integrated in the rotating direction can be adopted. In this configuration, the pulley is rotated by the rotating means, and the rotational force can be transmitted to the rotary shaft by absorbing the elevation of the pulley by moving the pulley in the axial direction with respect to the rotary shaft.
[0015]
Further, as another specific means, a configuration in which a spur gear is fitted on a rotation shaft of the table, and a pinion rotated by the rotation means is meshed with the spur gear may be employed. In this configuration, the spur gear meshing Move As a result, the up-and-down movement of the rotating shaft is absorbed, and the rotating force is transmitted to the rotating shaft.
[0016]
Further, as another specific means, a hydraulic cylinder serving as the elevating means is rotatably provided on the ground around its axis, the piston rod of the hydraulic cylinder is used as the rotation axis of the table, and the piston rod is used as a cylinder. It is possible to adopt a configuration in which the cylinder casing cannot be rotated with respect to the casing and the cylinder casing can be rotated by the rotating means. In this configuration, the vertical movement is absorbed by the space between the cylinder casing and the piston rod.
[0017]
Further, in any of the vertical mills of pulverization and crushing, as another specific means of the absorbing means, a casing of a hydraulic cylinder serving as the elevating means is fixed to the ground, and the rotation of the table is rotated by the piston. The shaft may be integrated in the elevating direction, and the table rotating shaft may be rotatable to the casing so that the rotational force of the motor absorbs the elevating of the piston and is transmitted. The rotation of the table rotating shaft with respect to the casing may be obtained by making the table rotatable with respect to the piston (see the embodiment), or may be obtained by making the piston rotatable with respect to the casing.
[0018]
In the configuration using these hydraulic cylinders, the motor, the hydraulic cylinder, and the table are arranged on the same straight line if the table rotation shaft penetrates the casing and is coaxial with the output shaft of the motor. Since it is located, the installation space for the motor and the hydraulic cylinder on the ground is reduced, and the size of the mill itself can be reduced.
[0019]
Means for absorbing the vertical movement of the piston (rotary shaft) is that if a flexible joint movable in the axial direction, such as Oldham's joint, is adopted, it is possible to absorb the misalignment of the shaft center, etc. The manufacturing cost can be reduced. At this time, the Oldham coupling transmits the torque of the motor to the table rotating shaft directly or via a piston. That is, the table rotation shaft is directly rotatable with respect to the piston, and the table rotation shaft is integrated with the piston in the rotation direction via the piston. Even in the case of this integral structure, it can be directly transmitted to the table rotating shaft.
[0020]
Also, if the opening of the chute for inputting the crushed object is made to face the upper surface of the table, and the gap between the opening of the chute and the upper surface of the table can be adjusted by raising and lowering the input chute, the input amount of the crushed object can be adjusted by adjusting the gap. Can be adjusted. As a specific configuration, the charging chute is formed of a telescopic double tube, and the tube facing the upper surface of the table can be moved in the axial direction with respect to another tube by a cylinder so that the gap can be moved to the table. A mechanism in which the gap is detected by a feeder opening detection mechanism and input to the control unit, and the gap is adjusted and controlled through the control unit may be employed.
[0021]
Further, in any of the above vertical mills, the roller tire is fixed to the casing so as not to swing, and the table is raised and lowered with respect to the roller tire so that the gap between them is constant, and the table rotation is performed. A configuration can be adopted such that the number can be rotated at high speed. With such a configuration, the number of table rotations can be set to be significantly large. In the conventional type, in which the roller tires are pressed by pressure springs, the rolling force is adjusted independently for each of the roller tires, so if you try to increase the table rotation speed, the rolling force from the roller tires varies, so 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 can be increased several times An appropriate particle size can be ensured even if the size is increased.
[0022]
【Example】
One embodiment is shown in FIGS. 1 to 4. In the vertical mill of this embodiment, upper and lower frames (casings) 2 and 3 are fixed on a machine base 1 and divided into four equal parts around the inner surface of the lower frame 2. An arm 2a is provided, and a hydraulic cylinder 10 is supported on the arm 2a via a support ring 4. A lid 5 is attached to the upper frame 3, and a charging cylinder (charging chute) 6 for crushed material a is provided at the center of the lid 5. The input chute 6 is an input chute with a hopper in which the upper hopper 6a of the lid 5 is integrally formed. An adjustment cylinder (adjustment chute) 7 is fitted to the input chute 6 via a cylinder 7a so as to be able to move up and down. The adjustment chute 7 is moved up and down by the expansion and contraction of a piston rod of the cylinder 7a (the pipe 7 moves with respect to the pipe 6). (Moving in the axial direction) the level of the lower end inlet, that is, the gap δ between the chute 7 and the table 8 described below. ₂ Is adjusted.
[0023]
By this adjustment, the amount of injection from the opening of the chute 7 is controlled, and the layer thickness of the crushed material a on the table 8 is kept constant. The gap δ ₂ Is detected by a table / feeder opening detecting mechanism 7c, for example, a linear scale provided between the flange 7b of the adjusting chute 7 and the input chute 6, and the detection result is input to a control unit of the vertical mill (not shown). . Gap δ ₂ When the setting is changed, when the change set value is input to the control unit, the cylinder 7a operates via the control unit to move the adjustment chute 7 up and down, and the gap δ ₂ Is adjusted to a predetermined value. That is, the gap δ is determined by the table feeder opening degree detection mechanism 7c. ₂ Is detected on the control panel, and the gap δ is determined by operating a switch on the control panel. ₂ Is adjusted to control the supply amount of the crushed material a from the chute 7. This stabilizes the load during crushing / crushing and reduces pulverization.
[0024]
A rotary table 8 is provided at the axis of the hydraulic cylinder 10, and roller tires 9 are provided at three equal parts around the table 8. The roller tire 9 is rotatably supported by the upper frame 3 but is not swingable via a tire shaft 9a. When the table 8 is rotating, the crushed material a is loaded from the loading cylinder 6. Then, the crushed material a is pinched and crushed between the roller tire 9 and the table 8.
[0025]
The hydraulic cylinder 10 is an annular type described in Japanese Patent Publication No. 5-29508, in which a casing 11 is fixed to the support ring 4, and a cylindrical piston 12 is provided in the casing 11 so as to be able to move up and down. Hydraulic chambers 13a and 13b are formed above and below the piston 12 in the casing 11, and oil pipes 14a and 14b are connected to the two chambers 13a and 13b, respectively. Oil is supplied to the upper hydraulic chamber 13a, and the lower hydraulic chamber 13b is drained. The piston 12 is lowered by being oiled, the oil is supplied to the lower hydraulic chamber 13b, and the piston 12 is raised by being drained from the upper hydraulic chamber 13a. The rotary shaft 8a of the table 8 is rotatably inserted into the piston 12 via a bearing 15 so as to be integrated in the vertical direction. Further, a linear scale 16 is attached to the piston 12, and the vertical movement of the piston 12 is detected by the scale 16.
[0026]
The above-mentioned hydraulic circuit 30 for raising and lowering the piston is configured as shown in FIG. 4, and the upper and lower hydraulic chambers 13a in the cylinder 11 are controlled by a motor / pump 31 from a tank T via a 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. 2B), the piston 12 descends, and conversely, when the lower hydraulic chamber 13b is refueled (see FIG. In the state shown in FIG. 1A, the piston 12 moves up. The elevation of the piston 12 is the elevation of the table 8, and the elevation (the gap δ between the table 8 and the roller tire 9) ₁ ) Is detected by the linear scale 16, and when the required position is reached, refueling is stopped.
[0027]
That is, the gap δ ₁ When the setting is changed in a narrowing direction, for example, when the gap is increased due to abrasion, the switching valve 32 is switched so that the hydraulic pressure is applied to the hydraulic cylinder 10 from the hydraulic pump 31 as shown in FIG. When voltage is applied to the hydraulic chamber 13b via the oil pipe 14b, the piston 12 rises with the rise of the oil pressure, and the table 8 also rises in synchronization. As the piston 12 rises, the hydraulic pressure in the upper hydraulic chamber 13a also increases, and the rise in the hydraulic pressure causes the spring of the check valve 34 to open, so that the oil in the upper hydraulic chamber 13a flows into the tank T. I do. When the piston 12 rises by the set amount, the hydraulic pump 31 is stopped.
[0028]
On the other hand, the gap δ ₁ When the setting is changed in the expanding direction, for example, by increasing the size of the crushed material to slightly increase the particle size, the switching valve 32 is switched as shown in FIG. Is applied to the upper hydraulic chamber 13a of the hydraulic cylinder 10 via the oil pipe 14a, the piston 12 descends, and the table 8 descends synchronously. At this time, the oil in the lower hydraulic chamber 13b flows into the tank T via the oil pipe 14b because the oil pressure in the oil pipe 14b applies a pilot pressure to the check valve 33 and opens. When the piston 12 descends by the set amount, the switching valve 32 is switched from FIG. 4B to FIG. 4A to stop the motor pump.
[0029]
The gap δ during this adjustment ₁ Is detected by the gap detecting mechanism of the table 8, that is, the linear scale 16 and the like, and the detection result is input to a control unit of the vertical mill (not shown). Gap δ ₁ When the setting is changed, when the change setting value is input to the control unit, the hydraulic circuit 30 is operated by the control unit to have a predetermined value.
[0030]
By this action, the required gap δ ₁ In this state, the hydraulic cylinder 10 is in a state where the upper and lower hydraulic chambers 13a and 13b are filled with a constant pressure. That is, since the backflow of the lower hydraulic chamber 13 b is prevented by the check valve 33, only the pressure due to its own weight of the table 8 and the like is generated, while the upper hydraulic chamber 13 a is controlled by the spring of the check valve 34. Backflow is prevented, and thus 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 do not necessarily have to be balanced, and the upper hydraulic chamber 13a may be open. Therefore, the check valve 34 need not be provided. Incidentally, the check valve 34 performs an operation of adjusting the return amount of the oil in the upper hydraulic chamber 13a when the piston 12 is lifted at the time of setting the gap. If the upper hydraulic chamber 13a is open, the piston 12 will rise quickly when oil is poured into the lower hydraulic chamber 13b. Therefore, a throttle valve or an orifice can be used instead of the check valve 34. Thus the gap δ ₁ Is easy because the table 8 only needs to be moved up and down by one hydraulic cylinder 10 and the hydraulic circuit 30.
[0031]
Further, during the crushing operation, if a large crushed object a enters between the roller tire 9 and the table 8 or if the layer thickness increases and a high load (impact force) is generated, pressure is generated in the lower hydraulic chamber 13a. The 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, oil having a capacity equal to the amount of movement of the piston 12 moves to absorb the impact force. This relief valve 35 is preferably of 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, 39 is a relief valve, and this relief valve 39 is provided for some reason by the oil pressure in the oil pipe 14b from the pump 31. Release the pressure when it becomes abnormally high.
[0032]
A support frame 17 is fixed to a lower portion of the support ring 4, and an inverter motor M is provided on the frame 17. The inverter motor M does not require a reduction gear, can be reduced in size, and has a variable rotation speed. A motor other than an inverter motor can be used as the motor M. The rotating shaft (output shaft) 20 of the motor M and the table rotating shaft 8a have the same axis and are connected by an Oldham joint 21 which is a flexible joint movable in the axial direction. As shown in FIG. 3, the Oldham coupling 21 includes a member 21a fixed to the motor rotation shaft 20, a member 21b fixed to the table rotation shaft 8a, and a floating cam fitted to both members 21a and 21b. And a member 21c. The method of transmitting the rotational force to the output shaft 20 can also be performed via a motor, a speed reducer, or the like that is not installed on various types of rotating shafts described later and known.
[0033]
The member 21b of the Oldham's joint 21 is integrated with the rotating shaft 8a by screwing a retaining ring 21d to both of them 21c and 8a, and the member 21a is integrated with the rotating shaft 20 by a key. The cam 21c is movably supported in one direction by a guide 21e fixed to the member 21a via a stopper plate 21f and a packing 21g. The Oldham coupling 21 is capable of transmitting a rotational force even when the axes of the two rotating shafts 8a and 20 are displaced, and is easy to assemble them. This joint portion is protected from dust by the covers 22a and 22b provided on the member 21a and the member 21b, respectively. As the flexible coupling, a slide (sliding type) coupling capable of moving the table 8 up and down with respect to the fixing of the motor M in place of the Oldham coupling 21, for example, a gear coupling and a spline coupling described later may be used.
[0034]
In this embodiment, the table 8 is moved up and down by supplying and discharging oil to the upper and lower hydraulic chambers 13a and 13b of the hydraulic cylinder 10 so that the gap .delta. ₁ To the required value. Then, when the table 8 is rotated by the motor M and the crushed material a is thrown in, the gap δ between the table 8 and the roller tire 9 is obtained. ₁ Crushing while maintaining the pressure, the particle size becomes uniform without powdering, and the crushed material b falls downward from around the table 8. At this time, the fall is smoothly guided by the guide plate 2b on the arm 2a. The fallen object b is conveyed to a required position by various conveyors.
[0035]
In the vertical mill having the above-described configuration, the roller tire 9 is fixedly installed on the upper frame 3 and cannot be swung. ₁ Is adjusted in advance so that is a required value. Therefore, the number of rotations of the table 8 by the motor M can be set to be significantly large. Roller tire 9 is equally spaced δ from table 8 ₁ Is set, the crushed particle size can be made uniform even when the rotation speed of the table 8 is increased.
[0036]
For example, in the illustrated example, the number of rotations of the table 8 can be set to 60 to 120 rpm, which is 2 to 3 times higher than that of 30 to 40 rpm in the conventional example. As a result, the crushing (crushing) capacity (production capacity) can be greatly increased.
[0037]
FIGS. 5 to 8 show another embodiment. In the embodiment shown in FIGS. 5 and 6, the roller tire 9 is supported by a trunnion joint 9 b and pressed in the direction of the table 8 by a pressing spring 45. It has become. The rotating shaft 8a of the table 8 is surrounded by an elevating cylinder 47, and is rotatably supported by a radial bearing 48 above the elevating cylinder 47. A thrust self-aligning roller bearing 52 is provided between the table 8 and the elevating cylinder 47.
[0038]
A pulley 49 is externally fitted on the rotating shaft 8a, and the pulley 49 is rotatably supported on its upper and lower sides by bearings 50 and 51. The two bearings 50 and 51 are formed by a supporting member (not shown) by a casing member. (Frame) 2. As shown in FIG. 6A, the rotating shaft 8a and the pulley 49 have a vertical ridge 53 provided on the outer peripheral surface of the rotating shaft 8a and a vertical groove 56 formed on the inner peripheral surface of the pulley 49. Are engaged, and the rotating shaft 8a and the pulley 49 are slidable in the vertical direction and integrated with each other in the rotating direction. That is, it is a spline bearing. Note that the rotating shaft 8a and the pulley 49 may slide in the vertical direction and engage (integrally) in the rotating direction. For example, as shown in FIG. A well-known configuration may be adopted in which the cross section of the shaft 8a is square and the inner peripheral surface of the pulley 49 is engaged with the square corresponding to 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, a known transmission means such as a timing belt may be employed.
[0039]
A bottom plate 58 is fixed to a lower portion of the elevating cylinder 47, and a hydraulic cylinder 59 as elevating 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 rotating shaft 8a, the table 8 and the like are moved up and down integrally, and the gap δ between the table 8 and the roller tire 9 is increased. ₁ To adjust. At this time, the gap δ ₁ Is detected by measuring the amount of expansion and contraction 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 due to the bearings 50 and 51 fixed to the casing 2, but when the ridge 53 slides in the groove 56, the rotary shaft 8 a moves up and down with respect to the pulley 49, Absorption is made.
[0041]
Required gap δ ₁ Then, when the table 8 is rotated by driving the motor M, the rotation of the pulley 49 is reliably transmitted to the rotating shaft 8a by the engagement of the ridge 53 and the groove 56, and the table 8 is rotated. The material to be crushed a is supplied onto the rotating table 8 and crushed by being caught between the roller tire 9 and the table 8 urged by the pressure spring 45.
[0042]
In the embodiment of FIG. 7, a spur gear 62 is externally fitted and fixed to the rotating shaft 8a, and a pinion 63 is meshed 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 vertical mill, the rotating shaft 8 a can be moved up and down by a hydraulic cylinder 59 and receives a rotating force via a pinion 63 and a spur gear 62. At this time, the width (height) of the spur gear 62 is made larger than that of the pinion 63, so that even if the rotating shaft 8a moves up and the position of the spur gear 62 changes, the meshing between the spur gear 62 and the pinion 63 is ensured. As a result, the rotating shaft 8a can be rotated.
[0044]
In the embodiment of FIG. 8, the rotating shaft 8a is composed of a rotating shaft portion (piston rod) 59a having a rectangular cross section and a piston portion 68b having a circular cross section. 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 a casing 59b of the hydraulic cylinder 59. The upper surface of the cylinder casing 59b is formed in an opening having a rectangular cross section, and a rotation shaft portion 59a having a rectangular cross section penetrates the opening, so that rotation with respect to the cylinder casing 59b is prohibited, and only vertical movement is allowed. You.
[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 a lower end of the hydraulic cylinder 59. Is provided. Oil is supplied to and discharged from the hydraulic cylinder 59 by a hydraulic pump (not shown) through the rotary joint 65, so that 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 of the above-described embodiments is for the case of crushing sand or the like, each of these embodiments can be adopted also in the case of crushing. At this time, for example, as shown in FIG. 9, the crushed material a is put on the table 8 from the screw feeder 60, and the crushed material b 'is conveyed by the air introduced from the lower part of the casing 2 and rises. Through which a vertical mill for grinding is guided to a collector such as a bag filter.
[0048]
In the embodiments after FIG. 5, the hydraulic cylinder 59 is controlled by the hydraulic circuit 30 shown in FIG. Further, the roller tire 9 does not apply the pressing force by the pressing spring 45, and may not swing as shown in FIG.
[0049]
【The invention's effect】
As described above, according to the present invention, the rotating means and the elevating means of the table can be respectively installed on the ground, so that the elevating means can be reduced in size and cost can be reduced. In addition, it is easy to minimize the unbalanced load during the rotation of the table, the vibration is small, and the rotation of the table can be smooth.
[Brief description of the drawings]
FIG. 1 is a schematic sectional view of one embodiment.
FIG. 2 is a sectional view of a main part of the same embodiment in a state where the piston is raised.
FIG. 3 is an exploded perspective view of the Oldham coupling of the embodiment.
FIG. 4 is a hydraulic circuit diagram of the embodiment.
FIG. 5 is a schematic sectional view of a main part of another embodiment.
FIG. 6 is a sectional view showing each example of fitting of the table rotation shaft and the pulley according to the embodiment.
FIG. 7 is a schematic sectional view of a main part of another embodiment.
FIG. 8 is a schematic sectional view of a main part of another embodiment.
FIG. 9 is a schematic cross-sectional view of a main part of another embodiment.
[Explanation of symbols]
a, a 'crushed material
b crushed material
b 'ground
G ground
M Table rotation motor
2, 3 mill casing (upper and lower frames)
6, 7 throwing chute
7a Cylinder for throwing chute
7c Table / feeder opening detection mechanism (linear scale)
8 tables
9 Roller tire
10 Hydraulic cylinder
11 Cylinder casing
12 piston
13a, 13b Hydraulic chamber
20 Motor rotation shaft (output shaft)
21 Oldham couplings
30 hydraulic circuit
45 Pressure spring
47 lifting cylinder
49, 49 'Pulley for rotary shaft
55 pulley
59 Hydraulic cylinder
59b cylinder casing
60 support tube
62 spur gear
63 pinion

Claims (4)

A vertical mill for feeding a crushed object a between a rotating table 8 and a roller tire 9 close to the table 8 to crush and crush it;
Fixed disable swinging the roller tires 9 to vertical mill casing 3, to the table 8 by vertically movable supported by lifting means, the lifting of the table 8, a gap [delta] ₁ of table 8 and the roller tire 9 The lifting means and the rotating means of the table 8 are installed on the ground G, respectively, and the rotating means transmits the rotational force by absorbing the lifting of the rotating shaft 8a to the rotating shaft 8a of the table 8 from the rotating means. A vertical mill characterized by the above. The rotating table 8 is supported so as to be able to ascend and descend, and the elevating means and the rotating means of the table 8 are respectively installed on the ground G, and the ascending and descending of the rotating shaft 8a is absorbed by the rotating shaft 8a of the table 8 from the rotating means. A vertical mill that transmits the rotational force to feed the crushed material a ′ between the table 8 and the roller tire 9 adjacent to the table 8 to crush and compress the same.
The roller tire 9 is fixed to the vertical mill casing 3 so as not to swing, and the table 8 is moved up and down to adjust the gap δ ₁ between the table 8 and the roller tire 9. The casing 11 is fixed to the ground G, and the rotating shaft 8a of the table 8 is integrated with the piston 12 in the ascending and descending directions. The rotating shaft 8a of the table 8 is rotatable with the casing 11 so that the rotational force of the motor M is reduced. A vertical mill, which absorbs and moves up and down the piston 12 and transmits the same. Is faced to the opening of the input chute 7 of the grind to the table 8 top, according to claim 1 or 2, characterized in that the adjustable gap [delta] ₂ of the opening and the table top of the chute 7 by the lifting of the chute 7 The vertical mill according to 1. The charging chute 7 is composed of telescopic double tubes 6, 7, and the tube 7 facing the upper surface of the table 8 can be moved in the axial direction with respect to the other tubes 6 by a cylinder 7a, so that the gap δ ₂ detects and by a table feeder opening detection mechanism 7c is inputted to the control unit, vertical according to claim 3, characterized in that so as to adjust control the gap [delta] ₂ via the control unit mill.

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