JP2000126632A - Roller supporting structure of roller mill - Google Patents

Abstract

PROBLEM TO BE SOLVED: To minimize torque of a rotary driving motor for pulverizing rollers and to make vibration acceleration due to vibration of the pulverizing rollers an allowable level or less. SOLUTION: In a roller mill provided with a freely rotatable pulverizing ring 1, a plurality of pulverizing rollers 2, a roller bracket 3 for holding each vibrating roller 2, a pressurizing frame 71 for holding the roller bracket every roller bracket, and a pressurizing mechanism 71 which is disposed at one end of the pressurizing frame 71 and on which a load is put in the vertical direction at the other end of the pressurizing frame 71, a tension rod 13-1 is stood, and moving mechanisms 507, 508, 509 for vertically moving the tension rod 13-1 are equipped. Vibration acceleration 501 due to vibration of the pulverizing rollers and torque 502 of a rotary driving motor of the pulverizing ring 1 are measured. Based on the vibration acceleration and the torque, inclination of the pressurizing frame 71 is calculated. The moving mechanism is subjected to vertical movement control so that the calculated inclination coincides with the optimum inclination.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pulverizer for finely pulverizing raw materials of coal, cement clinker or chemical products, and more particularly to a roller mill excellent in vibration proof.

[0002]

2. Description of the Related Art In a coal-fired boiler, low-pollution combustion and rapid load fluctuation operation are carried out, and accordingly, a coal pulverizer is also required to respond to a more flexible operation such as a fluctuation in the amount of supplied coal. Now required.

[0003] As one type of a pulverizer for finely pulverizing lump such as coal, cement raw material or new raw material, a rigid type having a pulverizing table performing low-speed rotation and a plurality of pulverizing rollers rotating on the pulverizing table. Roller mills have recently been strengthening its position as one of the representative models of fine pulverizers.

FIGS. 5 and 6 show an outline of a roller mill. FIG. 5 is a sectional view of a plane passing through the center axis of the mill, and FIG.
It is the top view seen in the direction. This type of mill includes a rotary table 52 that rotates at low speed in a horizontal plane in cylindrical housings 59 and 60, and a crushing ring 1 on the table 52.
A plurality of crushing rollers 2 which rotate while being pressed against
It has. The force pressing the crushing roller 2 is hereinafter referred to as crushing load 53. The turntable 52 is driven by a motor (not shown) fixed to a vertical axis that rotates at a low speed via a speed reducer.

FIG. 7 shows details of the pulverizing section of the mill. As shown in FIG. 5, the rotating shaft 60 of the crushing roller 2 is supported by a roller bracket 3 provided to cover the crushing roller 2. The roller bracket 3 is supported via a roller pivot 4 by a pressure frame 9 provided on the upper part thereof. Since the roller pivot 4 has a pin structure,
The roller bracket 3 is capable of pendulum movement of the rotary table 52 in the radial direction. The crushing load, which is the main factor controlling the crushing performance, is the combined force of the weight of the crushing unit such as the crushing roller 2 and the pressing frame 9 and the load 53 transmitted from the pressing device to the pressing frame 9 via the tension rod 19. Given as This resultant force is hereinafter referred to as a total crushing load. The load value of the pressurizing device is controlled according to the mill operating conditions represented by the amount of coal supplied.

A method of pulverizing coal by a roller mill will be described with reference to FIG. In FIG. 5, the raw material 51 supplied from the supply pipe 50 to the center of the rotary table 52 is rotated by the centrifugal force generated by the rotation of the rotary table 52.
It moves to the outer periphery along a spiral path on the top, and is caught between the crushing ring 1 and the crushing roller 2 and crushed.
Hot air 55 is guided to the base of the housing 59 by a duct, and the hot air 55 is blown up from an air throat 54 between the outer peripheral portion of the turntable 1 and the inner peripheral portion of the housing 59. The crushed powder is dried while rising inside the housing 59 by the flow of the hot air 55.

[0007] Of the particles transported to the housing 59, coarse particles fall by gravity, and pass through there, and the finer particles further rise. Classified again by the classifier 56, and the powder having a predetermined particle size or less is further heated with hot air 5.
5 transported. And in the case of a boiler, it is sent to a pulverized coal burner or a pulverized storage bin. The sieved powder having a predetermined particle size or more falls onto the rotary table 52 and is pulverized again with the raw material newly supplied into the mill. Pulverization and classification are repeated in this manner.

[0008] When the roller mill is operated with a low load or when the number of stops / starts is large, vibrations occur in the mill. This vibration phenomenon is a kind of friction vibration caused by slippage between the coal seam and the roller, and belongs to self-excited vibration as a vibration type. In ordinary coal, as shown in FIG. 8, this self-excited vibration often occurs during low-load operation (conditions with little coal hold-up in the mill).

When such self-excited vibration occurs,
As shown in FIGS. 9 and 10, the pressure frame is inclined. This inclination is such that any one of the three crushing rollers supporting the pressure frame moves to the outside of the rotary table by pendulum movement, and the heights of the three fulcrums of the pressure frame are different. Arises. Then, as shown in FIGS. 9 and 10, the contact point 65 between one crushing roller 2 and the crushing ring 1 is shifted from the neutral position in the direction of rotation of the rotary table 52 or in the opposite direction (see FIGS. 10 of 65
−a → 65-b), and as a result, the rotation direction of the rotary table at the contact point is different from the rotation direction of the crushing roller (the relationship between 66-a and 67-a is the relationship between 66-b and 67-b). To change).

Of these, vibration occurs in the state shown in FIG. 9, that is, when the contact point is at the neutral position (65-a in FIGS. 9 and 10).
(Indicated by ()) in the table rotation direction. Conversely, it is known that the vibration is suppressed when the contact point shifts to the downstream side as shown in FIG.

The difference between the two states is a component orthogonal to the rotating direction of the crushing roller (hereinafter referred to as a component perpendicular to the rotating direction of the crushing roller) of the two components of the rotary table speed vector in “Description of Contact Point 65-b” in FIGS. , "Side skid component"). In other words, in the state of FIG. 9, the sideslip component is directed outward in the radial direction when viewed from the center of the turntable.
This excites the vertical vibration of the grinding roller 2 as shown in FIG.

One crushing roller 2 is in a skidding state,
That is, when the vibration state is reached, this movement is transmitted to the other crushing rollers 2 gradually through the integrated pressurizing frame 9 which presses and supports the three crushing rollers 2 shown in FIG. Induces self-excited oscillation. Therefore, in the integrated pressure frame system, the vibration of one crushing roller is transmitted to another crushing roller.

In order to solve the above-mentioned problems of the prior art, a roller supporting structure has been proposed by the same applicant as the present application. The proposed roller support structure will be described with reference to FIGS. FIG. 13 is a plan view seen from the AA direction in FIG. The three grinding rollers 2 are supported by a pressure frame 70 via a roller pivot 4. The pressure frame 70 is divided for each crushing roller as shown in FIG. The pressure frame 70 is restrained at both ends by a pressure frame support box 75 provided in the housing 59. Hereinafter, the constraint conditions will be described.

Among the horizontal degrees of freedom, the pressing frame 70
Is restrained by a stopper 73, and its degree of freedom in the perpendicular direction is restrained by wear ring plates 74-1 and 74-2. In the vertical direction, the end on the downstream side of the turntable 52 is fixed and restrained to the foundation 79 via the tension rod 13-1. In the middle of the tension rod 13-1, the length of the tension rod 13-1 is adjusted to adjust the vertical level of the downstream end of the pressure frame 70.
A turnbuckle type level adjusting device 72 is incorporated. The other end is also a tension rod 13-2
The tension rod 13-2 incorporates a pressure device 71, which applies a vertically downward load but does not restrict the displacement.

The anti-vibration effect of the proposed roller support structure will be described. First, the behavior of the contact point between the grinding roller and the grinding ring, which is closely related to the generation of vibration, will be described. The cause of the deviation of the contact point from the neutral position 65-a is the inclination of the pressing frame 70 as shown in FIGS. Here, the inclination α of the pressure frame 70 is defined as positive when the upstream end of the pressure frame 70 is higher than the downstream end as shown in FIG. Corresponding to the sign of α, the contact point 65 between the crushing roller 2 and the crushing ring 1 is shifted from the neutral position in the rotation direction of the rotary table 52 or in the opposite direction (65-a in FIGS. 9 and 10). → 65-b) As a result, the velocity vector in the rotation direction of the rotary table at the contact point is different from the vector in the rotation direction of the crushing roller (the relationship between 66-a and 67-a is 66-b and 67-b).
b).

The difference between the directions of the two vectors is represented by an angle θ.
It is defined that when α is positive, θ is also positive. Of these, vibration occurs in FIG. 9, that is, when θ is positive. In this case, the contact point is in the neutral position (65- in FIGS. 9 and 10).
(indicated by "a") in the table rotation direction. Conversely, it is known that in the case of FIG. 10 where α and θ are negative, that is, when the contact point shifts to the downstream side, it is suppressed.

The difference between the two states is again shown in FIGS.
This will be described with reference to FIG. This difference between the states is due to the component (side slip component) orthogonal to the rotation direction of the crushing roller, out of the two components of the rotary table speed vector in “Description of Contact Point 65-b” shown in FIGS. Equivalent to the difference.
That is, when θ is positive (the state shown in FIG. 9), the sideslip component faces outward when viewed from the center of the rotary table, and excites the vertical vibration of the grinding roller.

Conversely, when θ is negative (the state shown in FIG. 10), the sideslip component is directed inward when viewed from the center of the turntable, and vibration is suppressed. However, if the absolute value of θ is too large, the motor torque for driving the turntable increases.

FIG. 14 shows the relationship between the vibration or motor torque and the angles α and θ described above. In this figure, when two horizontal axes are set, geometrically θ = between two angles.
The fact that 0.7α holds is used. From FIG. 14, the upper limit of the two angles determined from the vibration acceleration is θ _MAX =
0.7 °, α _MAX = 1.0 °, and the lower limits determined by the motor torque are θ _MIN = −3.0 ° and α _MIN = −, respectively.
4.3 ゜. Further, the allowable range of the angles α and θ is determined from the upper limit value and the lower limit value.

As shown in FIG. 12, in the middle of the tension rod 13-1 of the proposed roller support structure, the length of the tension rod 13-1 is adjusted to adjust the vertical level at the downstream end of the pressure frame 70. 14, a turnbuckle level adjusting device 72 is incorporated, and by using this adjusting device 72, the inclination α of the pressurizing frame is set freely within an allowable range in FIG. Suppress.

[0021]

There is an optimum value for α (or θ) shown in FIG. The optimum value is a point where the vibration acceleration is equal to or lower than the allowable level and the motor torque is the minimum, that is, a point where α = 0 ° (θ = 0 °). In contrast, the proposed roller support structure has the following problems.

(1) The value of α differs between when the roller is new and when it is worn. Α changes with the change in load. That is, with the proposed roller support structure, it is impossible to always make α equal to the optimum value.

(2) When an unexpected load condition occurs,
α exceeds the allowable range, and the vibration acceleration or the motor torque becomes larger than the allowable level.

An object of the present invention is to provide a roller mill which can be operated under a wide load without causing such a problem.

[0025]

In order to solve the above problems, the present invention employs the following configuration.

A rotatable crushing ring, a plurality of crushing rollers opposed to the crushing ring, a roller bracket for holding a rotating shaft of each crushing roller, and a split pressure frame for holding a roller bracket for each roller bracket When,
A pressurizing mechanism provided at one end of the pressurizing frame to apply a load in a vertical direction, comprising: a roller mill configured to pulverize the object to be pulverized by the pulverizing ring and the pulverizing roller.
A tension rod is provided at the other end of the pressurizing frame and a movable mechanism for vertically moving the tension rod is provided. The torque of the rotation driving motor of the crushing ring is minimized, and the vibration acceleration caused by the vibration of the crushing roller is provided. A roller support structure of a roller mill for controlling the movable mechanism to move up and down so that the value is below an allowable level.

Also, a rotatable crushing ring, a plurality of crushing rollers facing the crushing ring, a roller bracket for holding a rotating shaft of each crushing roller, and a split type holder for holding a roller bracket for each roller bracket. A pressure frame, comprising a pressure mechanism provided at one end of the pressure frame and applying a load in the vertical direction, a roller mill for crushing the object to be crushed by the crushing ring and the crushing roller, A tension rod is provided at the other end of the pressurizing frame and a movable mechanism for vertically moving the tension rod is provided, and a vibration acceleration due to the vibration of the crushing roller and a torque of a rotation driving motor of the crushing ring are measured. Calculating a tilt of the pressurizing frame based on the vibration acceleration and the torque; and calculating the calculated tilt with the optimum tilt. Roller support structure roller mill for controlling vertical movement of the movable mechanism.

Also, a rotatable crushing ring, a plurality of crushing rollers opposed to the crushing ring, a roller bracket for holding a rotating shaft of each crushing roller, and a split type holder for holding a roller bracket for each roller bracket. A pressure frame, comprising a pressure mechanism provided at one end of the pressure frame and applying a load in the vertical direction, a roller mill for crushing the object to be crushed by the crushing ring and the crushing roller, A first tension rod is interposed at one end of the pressurizing frame, a second tension rod is provided at the other end of the pressurizing frame, and a movable mechanism for vertically moving the second tension rod is provided. Displacement gauges for measuring the vertical displacement of the second tension rod are provided, and the pressurized frame is measured based on the amount of displacement from each of the displacement gauges. Roller support structure roller mill said movable mechanism for controlling vertical movement so that the inclination of the calculated and the calculated slope of the matches the optimal tilt.

[0029]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A roller support structure of a roller mill according to an embodiment of the present invention will be described below with reference to FIGS. FIG. 1 shows a control device for always optimally controlling the inclination of a pressure frame in a roller support structure of a roller mill according to a first embodiment of the present invention, and FIG. 2 shows a connecting portion between a motor and a tension rod. . FIG. 3 shows a control device for measuring the inclination itself of the pressure frame and controlling the inclination according to the second embodiment of the present invention, and FIG. 4 shows an enlarged configuration of the displacement meter of FIG. is there.

The features of the roller support structure according to the first embodiment of the present invention are, roughly speaking, the measurement of the vibration acceleration of the mill and the motor torque, and the inclination of the pressure frame is always equal to the optimum value. Is provided with a control device for performing such adjustment. The control device includes sensors 501 and 502, a control unit 506, a motor 507 for moving the tension rod 13-1 up and down, and the like.

As sensors, a sensor 501 for measuring the vibration acceleration of the mill and a sensor 502 for measuring the motor torque are used. The control unit 506 includes an amplifier 503 that amplifies the signal measured by the acceleration sensor 501, and a torque sensor 502
And a calculator 505 for calculating the amount by which the tension rod 13-1 is moved up and down so that the motor torque is minimized and the vibration acceleration of the mill is at or below an allowable level. Calculator 505
Is input to the motor 507 to move the tension rod 13-1 up and down.

Focusing on the motor 507, an enlarged view of the connection between the motor 507 and the tension rod 13-1 is shown in FIG.
It is. As shown in FIG. 2B, a jig 509 (hereinafter, referred to as a tension rod receiver) that supports the tension rod 13-1 so as to be vertically movable is provided on the motor 507 via a shaft 508. . The tension rod receiver 509 has a screw hole as shown in FIG. 2 (2).

FIG. 2A shows a state in which the tip of the tension rod 13-1 is machined so as to correspond to the screw hole. If the tip of the tension rod 13-1 is machined and inserted into the threaded hole of the tension rod receiver 509 by rotating it, the tension rod 13-1 can be moved up and down by rotating the motor 507.

With the structure described above, the inclination α (see the definition of α shown in FIG. 9) of the split-type pressurizing frame 70 can always be made equal to the optimum value, thereby minimizing the motor torque. And the vibration acceleration of the mill can be reduced to an allowable level or less. In the above description, the case where the vibration acceleration of the mill and the motor torque are measured has been described as a method of controlling the inclination of the pressurizing frame to be always equal to the optimum value.

Next, a roller support structure according to a second embodiment of the present invention will be described. This embodiment is characterized in that the inclination itself of the pressurizing frame is measured and the tension load is moved up and down based on the measured value, which will be described below with reference to FIGS. FIG.
A control device that measures a gradient α of 0, determines whether the gradient is equal to an optimum value, and controls the gradient α of the pressure frame. The control device includes displacement meters 514 and 51
5, a control unit 510, a motor 507 for raising and lowering the tension rod 13-1, and the like.

FIG. 4A is an enlarged view of the periphery including the displacement meter 514. (2) of FIG. 4 shows a BB cross section of (1) of FIG. The displacement gauge 514 is fixed to the tension rod 13-2 by fastening the displacement gauge fixing jigs 519, 520, 521 with bolts 518. On the other hand, a plate 5 is attached to the housing 19 via a jig 517.
16 is attached, and a displacement meter 514 is attached to this plate 516.
Has a structure where the tips of the contacts come in contact. With such a structure, the vertical displacement of the tension rod 13-2 with respect to the housing 19 can be measured.

The displacement meter 515 shown in FIG. 3 has the same mechanism as the displacement meter 514 shown in FIG. 4, and measures the vertical displacement of the tension rod 13-1 with respect to the housing 19.

The control unit 510 includes a calculator 5 for moving the amplifiers 511 and 512 and the tension rod 13-1 up and down.
05. The calculator 505 includes a displacement meter (514).
And 515) and the displacement of the tension rods (13-2 and 13-1) measured using the amplifiers (511 and 512) are used to calculate the inclination α of the pressure frame. When the calculated inclination α deviates from the optimum value, the vertical amount of the tension rod 13-1 is calculated, and the motor 507 is rotated to move the tension rod 113-1 up and down.

Next, the operation and functions of the first and second embodiments of the present invention will be described below. In FIG.
The allowable range and the optimum value of the inclination α of the pressurizing frame are shown so that the vibration acceleration of the mill and the motor torque are below the allowable levels.

In the case of the first embodiment, first, when coal is not pulverized, that is, when the roller and the table are in metal touch, the inclination α of the pressure frame becomes equal to the optimum value. As shown in FIG.
Set the vertical position of -1.

After the operation of the mill is started and the comminution of the coal is started, the vibration acceleration is measured by the acceleration sensor 501 in FIG. 1 and the motor torque is measured by the torque sensor 502 in real time. If the vibration acceleration measured in this way is equal to or higher than the allowable level or the motor torque deviates from the minimum value, the motor 507 in FIG.
The tension rod 13-1 is moved up and down so that the inclination α of the pressure frame is adjusted to be always equal to the optimum value.

Further, in the case of the second embodiment, the inclination α of the pressurizing frame can be detected by measuring the vertical displacement of both ends of the split-type pressurizing frame, and this inclination is determined in advance. The tension rod motor 507 is moved up and down so as not to deviate from the optimum value (as shown in FIG. 14, the optimum value of the inclination is determined in advance from the viewpoint of vibration acceleration and motor torque).

As described above, the embodiments of the present invention include those having the following structures, functions, and actions.

According to the present embodiment, the basic configuration is to control the vertical movement of the tension rod that presses the pressurizing frame, and the control device includes the vibration acceleration of the mill and the motor torque for driving the grinding ring. Or a measuring device for measuring the inclination of the pressure frame, and a control unit for calculating the vertical amount of the tension rod so that the inclination of the pressure frame matches the optimum value using the signal measured by the measuring device, And a motor for giving a vertical amount to the tension rod.

When the vibration of the mill occurs, the vibration acceleration of the mill and the motor torque measured by the measuring instrument are inputted to the control unit, and the vertical movement of the tension rod is calculated so that the inclination of the pressurizing frame is made to coincide with the optimum value. Then, the vertical amount is given to the tension rod by the motor, and the inclination of the pressurizing frame is controlled so as to always coincide with the optimum value.

As a result, the motor torque can always be minimized, and the vibration acceleration of the mill can be kept below an allowable level.

[0047]

The effects obtained by applying the tension rod vertical control device according to the present invention to a roller mill are summarized as follows.

[0048] Since the self-excited vibration of the mill can be suppressed under any load condition, the mill can be operated over a wide area without impairing the crushability of the mill.

Also, since the vibration of the mill can be suppressed,
The level of vibration and noise that causes discomfort to the employees in the plant is reduced, and the working environment is improved.

Furthermore, the vibration suppression improves the reliability and durability of the mill itself and plant equipment around the mill.

Further, in a normal mill, even if a coal type or a solid fuel, which is liable to cause self-excited vibration, is used, the vibration is suppressed, so that an inexpensive fuel which has not been used conventionally can be used. The operation cost of the plant can be reduced.

[Brief description of the drawings]

FIG. 1 is a diagram showing a control device for always optimally controlling the inclination of a pressure frame in a roller support structure of a roller mill according to a first embodiment of the present invention.

FIG. 2 is a diagram showing a connecting portion between a motor and a tension rod.

FIG. 3 is a diagram showing a control device that measures the inclination itself of a pressure frame and controls the inclination according to a second embodiment of the present invention.

FIG. 4 is an enlarged view of the displacement meter shown in FIG.

FIG. 5 is a view showing a roller supporting structure of a roller mill according to the related art.

FIG. 6 is a sectional view of FIG. 5;

FIG. 7 is a detailed view of a pulverizing unit of a conventional mill.

FIG. 8 is a diagram for explaining how self-excited vibration is generated in a mill crushing unit.

FIG. 9 is a diagram for explaining generation of self-excited vibration due to tilting of the pressing frame.

FIG. 10 is a diagram illustrating generation of self-excited vibration due to tilting of a pressure frame.

FIG. 11 is a detailed view of a crushing unit where vibration occurs.

FIG. 12 is a configuration diagram that achieves vibration suppression by using a split-type pressure frame structure for the pressure frame.

FIG. 13 is a sectional view of FIG.

FIG. 14 is a diagram showing a relationship between the inclination of the pressing frame and the vibration acceleration of the crushing unit or the motor torque of the crushing ring driving motor.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Crush ring 2 Crush roller 3 Roller bracket 4 Pivot pin 13-1, 13-2 Tension rod 19 Housing 70 Split type press frame 71 Press device 79 Foundation 501 Acceleration sensor 502 Torque sensor 503, 504, 511, 512 Amplifier 505 Level calculator 506, 510 Control unit 507 Motor 508 Shaft 509 Tension rod receiver 514, 515 Displacement gauge 519, 520, 521 Jig for fixing displacement gauge

 ──────────────────────────────────────────────────続 き Continuing from the front page (72) Eiji Murakami, Inventor 3-36 Takaracho, Kure-shi, Hiroshima Pref. Inside the Kure Research Laboratories (72) Inventor Nobuyasu No. 3-36 Takaracho, Kure-shi, Hiroshima Pref. Babcock Hitachi, Ltd. Inside the Kure Research Laboratory (72) Inventor Tadashi Hasegawa 6-9 Takaracho, Kure City, Hiroshima Prefecture Babcock Hitachi Kure Factory F-term (reference) 4D063 EE03 EE12 EE24 GA06 GA08 GA10 GC21 GC25 GC29 GD01 GD12 GD13

Claims (3)

[Claims] 1. A rotatable crushing ring, a plurality of crushing rollers opposed to the crushing ring, a roller bracket for holding a rotating shaft of each crushing roller, and a split type holder for holding a roller bracket for each roller bracket. A pressure frame, comprising a pressure mechanism provided at one end of the pressure frame and applying a load in the vertical direction, a roller mill for crushing the object to be crushed by the crushing ring and the crushing roller, A tension rod is provided at the other end of the pressurizing frame and a movable mechanism for vertically moving the tension rod is provided. The torque of the rotation driving motor of the grinding ring is minimized, and the vibration acceleration due to the vibration of the grinding roller is reduced. A roller support structure for a roller mill, wherein the movable mechanism is controlled to move up and down so as to be below an allowable level. 2. A rotatable crushing ring, a plurality of crushing rollers opposed to the crushing ring, a roller bracket for holding a rotating shaft of each crushing roller, and a split type holder for holding a roller bracket for each roller bracket. A pressure frame, comprising a pressure mechanism provided at one end of the pressure frame and applying a load in the vertical direction, a roller mill for crushing the object to be crushed by the crushing ring and the crushing roller, A tension rod is provided at the other end of the pressurizing frame and a movable mechanism for vertically moving the tension rod is provided, and a vibration acceleration due to the vibration of the crushing roller and a torque of a rotation driving motor of the crushing ring are measured. Calculate the inclination of the pressurizing frame based on the vibration acceleration and the torque so that the calculated inclination matches the optimal inclination. A roller support structure for a roller mill, wherein the movable mechanism is controlled to move up and down. 3. A rotatable crushing ring, a plurality of crushing rollers facing the crushing ring, a roller bracket for holding a rotating shaft of each crushing roller, and a split mold for holding a roller bracket for each roller bracket. A pressure frame, comprising a pressure mechanism provided at one end of the pressure frame and applying a load in the vertical direction, a roller mill for crushing the object to be crushed by the crushing ring and the crushing roller, A first tension rod interposed at one end of the pressure frame, a second tension rod provided at the other end of the pressure frame, and a movable mechanism for vertically moving the second tension rod; A displacement gauge for measuring a displacement of the second tension rod in the vertical direction; Roller support structure roller mill, characterized by vertical movement controls the moving mechanism so that the inclination that is to calculate the slope and the calculation is consistent with the optimal tilt.