JP7080970B2 - Crushing device and control method of crushing device - Google Patents

Description

The present invention relates to a crushing device and a control method for the crushing device.

Mills (crushing devices) for crushing solid fuels used in thermal power generation facilities and objects to be crushed such as cement raw materials used in cement manufacturing plants are known. The mill grinds the object to be crushed by being put into the crushing rotary table from the material supply pipe to be crushed by sandwiching it between the crushing rotary table and the crushing roller. Then, the object to be crushed into fine powder is blown up by the transport gas supplied from the outer periphery of the crushing rotary table, and is sifted by a classifier according to the particle size. The object to be crushed having a small particle size is discharged to the outside of the mill and transported to a predetermined device as a transport destination provided.

The crushing roller provided in the mill in this way wears by crushing the object to be crushed. Since the wear of the crushing roller may affect the operating condition and performance of the mill in various ways, when the mill is provided with a device for diagnosing the wear condition of the crushing roller in order to grasp the wear condition of the crushing roller. (For example, Patent Document 1).

Patent Document 1 describes the appropriate value of the mill differential pressure or the mill power by simulation from the detection value from various detectors provided in the mill, the mill structure (ring diameter, roller diameter, etc.), the classifier structure, and the coal type. Disclosed is a roller wear state diagnostic device that diagnoses the wear state of a roller or the like from the deviation between this and the measured value from the mill differential pressure detector or the power detector. In this device, when there is an abnormality from the comparison result between the appropriate value and the measured value, measures such as generation of an alarm, stop of the mill, start of another mill, or load distribution are performed.

Special Fair 8-206 Gazette

It was found that the influence of the wear of the crushing roller on the performance of the mill differs depending on the installation mode of the crushing roller in the crushing device.
For example, when the crushing roller is provided so that the degree of freedom for the crushing table is relatively low, the crushing roller is worn and the crushing performance is deteriorated. On the other hand, when the crushing roller is provided so that the degree of freedom for the crushing table is relatively high, the roller portion moves to a position where the load is relatively small when the object to be crushed is crushed. As a result, the shape of the roller portion is worn so as to have a shape suitable for the crushing mode in the crushing device. Therefore, in such a crushing device, the crushing performance is improved by the wear of the crushing roller.
As described above, it was found that depending on the crushing device, the performance of the mill may be deteriorated or improved as the crushing roller is worn.

In Patent Document 1, only the situation where the mill differential pressure increases with the wear of the rollers is considered. An increase in the differential pressure of the mill indicates an increase in pressure loss in the mill, that is, a decrease in grinding performance. Therefore, in Patent Document 1, only a situation in which the crushing performance is deteriorated is assumed. Further, in the apparatus of Patent Document 1, proper operation is not considered from the diagnosis result of roller wear.
Therefore, there is a possibility that the mill cannot be operated properly according to the secular variation of the crushed portion.

The present invention has been made in view of such circumstances, and provides a crushing device and a control method for the crushing device, which can appropriately operate the crushing device even if the crushing unit changes over time. The purpose.

In order to solve the above problems, the following means are adopted as the crushing device and the control method of the crushing device of the present invention.

The crushing device according to one aspect of the present invention is a crushing device that crushes an object to be crushed, and has a table portion that is rotationally driven about an axis in the vertical direction and a roller that is arranged so as to face the upper surface of the table portion. A crushing section that has a section and crushes the object to be crushed by sandwiching the object to be crushed between the upper surface of the table section and the roller section, and a load derivation that derives the load of the current crushing device. A unit, a performance value measuring unit that measures the current performance value of the crushing device, and a crushing device when the crushing device is operated with a load derived by the load deriving unit at a predetermined reference time. Based on the performance value derivation unit for deriving the performance value, the current performance value of the crushing device measured by the performance value measuring unit, and the performance value of the crushing device at the reference time derived by the performance value deriving unit. , The current performance value of the crushing device measured by the performance value measuring unit affects the performance value of the crushing device so as to approach the performance value of the crushing device at the reference time derived by the performance value deriving unit. It is provided with a control unit for changing a parameter that gives.

With the operation of the crushing device, the shape of the crushing portion for crushing the object to be crushed changes over time. The secular variation of the crushed portion includes deformation due to wear of the roller portion and the table portion. As the crushed portion changes over time, the performance value of the crusher fluctuates.
In the above configuration, the parameters that affect the performance value of the crusher are changed so that the current performance value of the crusher approaches the performance value of the crusher at the reference time. As a result, even if the crushing portion changes over time due to the operation of the crushing device, the performance value of the crushing device can be set to the performance value at a predetermined reference time. Since the performance value can be controlled in this way, even if the crushed portion changes over time, the crushing device can be appropriately operated according to the performance value (aged change of the crushed portion).
The predetermined reference time includes, for example, a time before the crushing portion changes over time, such as during the initial operation of the crushing device or during the break-in operation of the crushing device.

Further, the crushing device according to one aspect of the present invention includes a load applying portion that applies a pressing load toward the upper surface of the table portion to the roller portion, and the parameter is applied to the roller portion. Having a pressing load applied, the control unit has the current performance value of the crushing device measured by the performance value measuring unit and the performance value of the crushing device at the reference time derived by the performance value deriving unit. Based on the above, the load applying unit so that the current performance value of the crushing device measured by the performance value measuring unit approaches the performance value of the crushing device at the reference time derived by the performance value deriving unit. It may have a load control unit for adjusting the applied pressing load.

As a parameter that affects the performance value of the crusher, there is a crushing capacity C of the crusher. The crushing capacity C of the crushing device is calculated by the following formula (1).
C = k × M × ω × D ... (1)
However, k: coefficient
M: Pressing load of roller part
ω: Number of rotations of the table
D: Diameter of the table portion As described above, as parameters for determining the crushing capacity C of the crusher, there are a pressing load, a rotation speed of the table portion, and a diameter of the table portion. The diameter of the table portion cannot be easily changed once the table portion is installed. Therefore, the inventors focused on the pressing load and the rotation speed of the table portion. The crushing capacity C can be increased or decreased by changing the pressing load and / or the rotation speed of the table portion. By increasing or decreasing the crushing capacity C, the performance value of the crusher can be adjusted. Hereinafter, the product of the pressing load, which is an element that determines the crushing capacity C, and the rotation speed of the table portion is also referred to as crushing energy.
In the above configuration, the pressing load applied by the load applying portion is adjusted so that the current performance value of the crushing device approaches the performance value of the crushing device at the reference time. As described above, the pressing load is one of the parameters that affect the performance value. As a result, even if the crushing part changes over time due to the operation of the crushing device, the performance value of the crushing device can be set as the performance value at a predetermined reference time by adjusting the pressing load applied by the load applying part. Can be done. Since the performance value can be controlled in this way, even if the crushed portion changes over time, the crushing device can be appropriately operated according to the performance value (aged change of the crushed portion).

Further, the crushing apparatus according to one aspect of the present invention includes a rotation drive unit that rotationally drives the table unit so as to have a predetermined rotation speed, and the parameter has the rotation speed of the table unit and is controlled. The unit is measured by the performance value measuring unit based on the current performance value of the crushing device measured by the performance value measuring unit and the performance value of the crushing device at the reference time derived by the performance value deriving unit. A table that adjusts the number of rotations of the table unit rotated by the drive unit so that the current performance value of the crushing device approaches the performance value of the crushing device at the reference time derived by the performance value derivation unit. It may have a rotation speed control unit.

In the above configuration, the rotation speed of the table portion is adjusted so that the current performance value of the crushing device approaches the performance value of the crushing device at the reference time. As described above, the rotation speed of the table unit is one of the parameters that affect the performance value. As a result, even if the crushing part changes over time due to the operation of the crushing device, the performance value of the crushing device can be set as the performance value at a predetermined reference time by adjusting the pressing load applied by the load applying part. Can be done. Since the performance value can be controlled in this way, even if the crushed portion changes over time, the crushing device can be appropriately operated according to the performance value (aged change of the crushed portion).
Further, by adjusting the rotation speed of the table portion, the vibration value of the crusher can be reduced as compared with the case where the pressing load is adjusted.

Further, the crushing device according to one aspect of the present invention is provided inside the housing of the crushing device and includes a frame portion that supports the roller portion, and the frame portion is swingable with respect to the table portion. The roller portion is swingably supported with respect to the frame portion, and the load control portion presses the load applying portion so that the pressing load applied by the load applying portion is reduced. The load may be adjusted.

In the above configuration, the frame portion is swingable with respect to the table portion, and the roller portion is swingably supported with respect to the frame portion, so that the roller portion can be moved in a plurality of directions. There is. That is, the roller portion is supported with a relatively high degree of freedom with respect to the table portion. As a result, the roller portion moves to the position where the load is the least among the movable positions when the object to be crushed is crushed. Generally, the mode of crushing by the crushing unit differs depending on the installation environment of the crushing device and the object to be crushed. When crushing, the roller portion having the above configuration moves to the position where the load is the least, so that the roller portion wears according to the crushing mode in the crushing device. Therefore, due to secular variation, the shape of the roller portion changes so as to be suitable for the crushing mode in the crushing device. Therefore, in the above configuration, the performance value of the crushing device changes so that the crushing performance (crushing efficiency) improves as the crushing portion changes over time.
In the above configuration, the pressing load of the load applying portion is adjusted so that the pressing load applied by the load applying portion is reduced. When the pressing load is reduced, the force for sandwiching the object to be crushed between the table portion and the roller portion is weakened, so that the crushing performance is suppressed. As a result, it is possible to suppress the improvement of the crushing performance due to the secular variation of the crushed portion and suppress the excessive crushing of the object to be crushed by the crushed portion. Therefore, the speed of wear and the like of the crushed portion due to excessive crushing can be reduced, and the product life of the crushed portion can be extended.
Further, in the above configuration, since the crushing portion changes over time, the crushing performance (crushing efficiency) is improved, so that the crushing amount of the object to be crushed increases and the driving force of the crushing portion increases, but the load-applied portion Since the applied pressing load is reduced and the improvement of the crushing performance is suppressed, the increase in the driving force of the crushing portion can also be suppressed. Therefore, it is possible to suppress an increase in the driving force of the crushed portion due to excessive crushing and to save energy in the crushing device.

Further, in the crushing device according to one aspect of the present invention, the performance value of the crushing device may include a driving force for driving the crushing portion.

When the crushed portion changes over time, the crushing performance of the crushed portion also changes according to the aging of the crushed portion. As a result, the driving force for driving the crushed portion also changes. The cause of the change in the driving force is that the crushing performance deteriorates due to the change in the shape of the crushed part, which requires more driving force, and the crushing performance improves due to the change in the shape of the crushed part. , The situation where the crushed amount of the object to be crushed increases can be mentioned. In the above configuration, the driving force of the crushed portion, which changes due to the secular variation of the crushed portion, is used as the performance value. Therefore, it is possible to accurately grasp the secular variation of the crushed portion.
Further, in the above configuration, since the driving force for driving the crushing section is used as the performance value of the crushing device, the driving force for driving the crushing section even if the crushing section changes over time due to the operation of the crushing device. Can be the driving force at a predetermined reference time. Since the driving force can be controlled in this way, the crushing device can be operated with an appropriate driving force even if the crushing portion changes over time. Therefore, it is possible to accurately suppress an increase in the driving force of the crushed portion due to excessive crushing, and to further save energy in the crushing device.

Further, the crushing apparatus according to one aspect of the present invention discharges a transport gas supply unit for supplying a transport gas for transporting the crushed object to the outside and a crushed object transported by the transport gas. A discharge unit is provided, and the performance value of the crusher may include a differential pressure between the pressure on the transport gas supply unit side and the pressure on the discharge unit side.

When the crushed portion changes over time, the crushing performance of the crushed portion also changes according to the aging of the crushed portion. As the crushing performance changes, the amount of crushed material in the crushing device also changes. Since the amount of crushed material becomes a pressure loss with respect to the transport gas flow, the differential pressure between the transport gas supply unit side and the discharge unit side also changes. That is, the differential pressure also changes according to the secular variation of the crushed portion. In the above configuration, the differential pressure that changes due to the secular variation of the crushed portion is used as the performance value. Therefore, it is possible to accurately grasp the secular variation of the crushed portion.

Further, the crushing device according to one aspect of the present invention has a learning unit that performs machine learning for deriving the degree of adjustment of the pressing load applied by the load applying unit, and the learning unit is based on the machine learning. The adjustment degree may be derived, and the load control unit may adjust the pressing load applied by the load applying unit so as to have the adjustment degree derived by the learning unit.

In the above configuration, the learning unit that has performed machine learning to derive the reduction degree for reducing the pressing load applied by the load applying unit adjusts the pressing load with the adjustment degree derived based on the machine learning. This makes it possible to accurately adjust the pressing load.

The control method of the crushing device according to one aspect of the present invention is the control method of the crushing device for crushing the object to be crushed, the upper surface of the table portion rotationally driven about the vertical axis, and the said table portion. A crushing step of crushing the object to be crushed by sandwiching the object to be crushed between the roller portion arranged facing the upper surface, a load derivation step of deriving the load of the crushing device at present, and the crushing at present. A performance value measuring step for measuring the performance value of the device and a performance value for deriving the performance value of the crushing device when the crushing device is operated with the load derived in the load derivation step at a predetermined reference time. In the performance value measurement step, based on the derivation step, the current performance value of the crusher measured in the performance value measurement step, and the performance value of the crusher at the reference time derived in the performance value derivation step. Control to change the parameters that affect the performance value of the crusher so that the measured current performance value of the crusher approaches the performance value of the crusher at the reference time derived in the performance value derivation step. It has steps and.

According to the present invention, the crushing apparatus can be appropriately operated even if the crushing portion changes over time.

It is a vertical sectional view which shows the mill which concerns on 1st Embodiment of this invention. It is a block diagram which shows the control device of the mill of FIG. It is a flowchart which shows the operation control processing performed by the control device of FIG. It is a flowchart which shows the performance value acquisition process performed by the control device of FIG. It is a flowchart which shows the modification of FIG. It is a graph which showed the relationship between the mill load factor and the pressure loss in the mill which concerns on 1st Embodiment of this invention. It is a graph which showed the relationship between the mill load factor and the crushing power in the mill which concerns on 1st Embodiment of this invention. It is a graph which showed the relationship between the hydraulic pressure and the driving force ratio in the mill which concerns on 1st Embodiment of this invention. It is a graph which showed the relationship between the hydraulic pressure and the circulating coal differential pressure ratio in the mill which concerns on 1st Embodiment of this invention. It is a graph which showed the relationship between time and hydraulic pressure in the mill which concerns on 1st Embodiment of this invention. It is a graph which showed the relationship between the time and the driving force in the mill which concerns on 1st Embodiment of this invention. It is a graph which showed the relationship between the time and the circulating coal differential pressure in the mill which concerns on 1st Embodiment of this invention. It is a graph which showed the relationship between time and crushing energy. It is a graph which showed the relationship between time and circulating coal differential pressure. It is a graph which showed the relationship between time and driving force. It is a block diagram which shows the control device of the mill which concerns on 2nd Embodiment of this invention. It is a flowchart which shows the operation control processing performed by the control device of FIG. It is a flowchart which shows the modification of FIG. It is a graph which showed the relationship between the rotation speed and the driving force ratio of the crushing rotary table in the mill which concerns on 2nd Embodiment of this invention. It is a graph which showed the relationship between the rotation speed of the crushing rotary table in the mill which concerns on 2nd Embodiment of this invention, and the circulation coal differential pressure ratio. It is a graph which showed the relationship between the time in the mill which concerns on 2nd Embodiment of this invention, and the rotation speed of a pulverization rotary table. It is a graph which showed the relationship between the time and the circulating coal differential pressure ratio in the mill which concerns on 2nd Embodiment of this invention. It is a graph which showed the relationship between time and driving force in the mill which concerns on 2nd Embodiment of this invention. It is a graph which showed the relationship between the time and the vibration value in the mill which concerns on 2nd Embodiment of this invention. It is a block diagram which shows the control device of the mill which concerns on 3rd Embodiment of this invention.

[First Embodiment]
Hereinafter, the first embodiment of the crushing device and the control method of the crushing device according to the present invention will be described with reference to the drawings. In this embodiment, an example in which the present invention is applied to a crushing device provided in a thermal power generation facility for crushing solid fuel will be described.

FIG. 1 shows the details of the mill 1. FIG. 1 shows a mill 1 for pulverizing coal as a raw material (fuel), and a mill facility including a raw material supply system and a pulverized material transport system of the mill 1.

The mill 1 is a vertical mill and crushes solid coal. The mill 1 may be in the form of crushing only coal, in the form of crushing biomass fuel together with coal, or in the form of crushing only biomass fuel. In this embodiment, a case where only coal is crushed will be described.

The housing 31 of the mill 1 has a vertical cylindrical hollow shape, and a center chute 33 is attached to the central portion of the ceiling portion 32. The upper end of the center chute 33 is connected to a coal supply pipe (not shown), and coal derived from a bunker (not shown) storing coal is supplied into the housing 31. The center chute 33 is arranged at the center position of the housing 31 along the vertical direction (vertical direction), and the lower end portion thereof extends into the housing 31.

At the lower part of the housing 31, a gantry 34 is installed on the ground, and a crushing rotary table 35 is rotatably arranged on the gantry 34. The lower end of the center chute 33 is arranged so as to face the center of the crushing rotary table 35. The center chute 33 supplies coal from above to below. Further, inside the housing 31, a hopper 11 having an inverted conical shape and a cylindrical shape is provided between the center chute 33 and the crushing rotary table 35.

A rotary feeder (not shown) is attached to the coal supply pipe, and the rotary feeder cuts out a fixed amount of coal, that is, supplies coal in predetermined amounts.

The coal is crushed by the crushing unit 30. The crushing section 30 has a crushing rotary table (table section) 35, a crushing roller (roller section) 36, and the like.
The crushing rotary table 35 is rotatable around the central axis in the vertical direction (vertical direction) and is driven by the drive device 20. The upper surface of the crushing rotary table 35 has an inclined shape in which the central portion is high and is lowered from the central portion to the outside, and the outer peripheral portion is curved upward from the inside to the outside. The drive device 20 has an inverter (not shown). The drive device 20 can adjust the rotation speed of the crushing rotary table 35 by an inverter.

Above the crushing rotary table 35, a plurality of, for example, three crushing rollers 36 are arranged facing the upper surface of the crushing rotary table 35. The crushing rollers 36 are arranged above the outer peripheral portion of the crushing rotary table 35 at equal intervals in the circumferential direction (120 ° intervals in the case of three crushing rollers 36). Although the two crushing rollers 36 are symmetrically shown in FIG. 1 for the sake of explanation, when the three crushing rollers 36 are arranged at intervals of 120 °, the arrangement of the crushing rollers 36 is shown in FIG. It is different from the figure.

The crushing roller 36 is swingably connected to the pressurizing arm (frame portion) 37 via the bracket 38. The bracket 38 is hinged to the pressurizing arm 37. The pressurizing arm 37 has a substantially hexagonal shape in a plan view, and is connected to a tension rod (load applying portion) 39 at three points between adjacent crushing rollers 36. The tension rod 39 has a hydraulic cylinder portion 49 provided at the lower portion, and the hydraulic cylinder portion 49 can change the pressing load of the crushing roller 36 by hydraulic pressure.

With the above configuration, the bracket 38 is supported by the pressurizing arm 37, and the crushing roller 36 can be swung with respect to the pressurizing arm 37 by the bracket 38. The pressurizing arm 37 is connected to a tension rod 39 housed in the tension rod box 40. Further, the pressurizing arm 37 is provided inside the housing 31, and the position in the vertical direction (vertical direction) is adjusted by the hydraulic pressure of the hydraulic cylinder portion 49. Thereby, the load (pressing load) acting on the solid matter on the crushing rotary table 35 can be changed by the crushing roller 36. Further, the pressure arm 37 is swingably supported by the tension rod 39 with respect to the crushing rotary table 35. The lower end of the tension rod 39 is fixed to the ground.

When the crushing rotary table 35 rotates, the crushing roller 36 is driven by the force received from the crushing rotary table 35 and the solid matter, and rolls around the rotation axis of the crushing roller 36. The coal is pressed and crushed between the crushing roller 36 and the crushing rotary table 35 by the meshing of the crushing roller 36 and the crushing rotary table 35. When coal is crushed, pulverized products on pulverized powder (hereinafter referred to as "pulverized coal") are produced.

A primary air duct (conveying gas supply unit) 13 is connected to the lower part of the housing 31. The primary air (transport gas) 60 supplied by the primary air duct 13 is guided into the housing 31 and supplied to the space located below the crushing rotary table 35.

A rotary classifier 41 is provided on the upper part of the housing 31. The rotary classifier 41 is arranged so as to surround the center chute 33 and rotates around the center chute 33. As the rotary classifier 41 rotates, a plurality of fins 42 attached to the outer peripheral side thereof travel in the circumferential direction. The pulverized coal crushed by the crushing rotary table 35 and the crushing roller 36 is wound upward by the air flow rising from below the crushing rotary table 35 through the outer peripheral side of the crushing rotary table 35. Of the pulverized coal that has been rolled up, the pulverized coal having a relatively large diameter is knocked down by the fins 42, returned to the pulverizing rotary table 35, and pulverized again. As a result, the pulverized coal is classified by the rotary classifier 41. The rotary classifier 41 is rotated by the driving force of the driving unit 50.

A plurality of coal feeding pipes (discharged parts) 9 are connected to the ceiling portion 32, and the coal feeding pipe 9 discharges the pulverized coal after being classified by the rotary classifier 41 and discharges the discharged pulverized coal. Lead to the boiler body. The plurality of coal feed pipes 9 are connected to the plurality of openings provided corresponding to the ceiling portion 32, respectively. The coal feed pipe 9 varies depending on the size of the mill 1 and the crushing capacity, but is in the range of 2 to 8 pipes, and is often 4 to 6 pipes.

The flow of coal in the mill 1 according to the present embodiment will be described below.

The coal stored in the bunker is sent to the coal supply pipe and the center chute 33. At this time, the rotary feeder attached to the coal supply pipe cuts out a certain amount of coal, and the biomass fuel falls toward the inside of the mill 1 (a).

The coal supplied into the mill 1 falls on the crushing rotary table 35 (b), moves to the outer peripheral side by centrifugal force, and is crushed between the plurality of crushing rollers 36 and the crushing rotary table 35. The pulverized pulverized coal rises in the mill 1 by the primary air 60 blown into the mill 1 through the primary air duct 13 and the throat vane 44 (c). During this ascent, some of the coarse particles having a large particle size of the pulverized coal fall due to gravity and are returned to the crushing rotary table 35.

At the upper part of the mill 1, a rotary classifier 41 composed of a plurality of fins (blades) 42 is rotating, and coarse and heavy pulverized coal is knocked down by the centrifugal force of the fins 42 so as to be repelled. Further, the pulverized coal that has been knocked down slides down the inner peripheral surface of the hopper 11 and is returned to the crushing rotary table 35 (d). The finely pulverized product is repeatedly pulverized until it becomes finer.
The finely divided pulverized coal passes through the rotary classifier 41 (e) and is air-transported to the outside through the coal feed pipe 9 (f). The air-transported pulverized coal is sent to a burner provided in a boiler (not shown) and burned.

Next, various measuring instruments provided in the mill 1 will be described. The mill 1 is provided with a measuring instrument for measuring the operating state of the mill 1. Specifically, the flow rate (primary air amount) of the primary air supplied from the coal supply amount measuring instrument 21 for measuring the amount of coal supplied to the mill 1 (the amount of coal supply) 21 and the primary air duct 13 is measured. The hydraulic pressure of the primary air amount measuring instrument 22, the classifying machine rotation speed measuring instrument 23 for measuring the rotation speed (classifying machine rotation speed) of the fins 42 of the rotary classifying machine 41, and the tension rod 39 (more specifically, the hydraulic cylinder portion 49). It is a hydraulic pressure measuring instrument 24 for measuring hydraulic pressure) and a table rotation number measuring instrument 25 for measuring the rotation speed of the crushing rotary table 35.
Further, the mill 1 is subjected to the difference pressure between the pressure measured by the pressure gauge (not shown) provided in the primary air duct 13 and the pressure measured by the pressure gauge (not shown) provided in the coal feed pipe 9. A differential pressure measuring instrument 26 for measuring and a driving force measuring instrument 27 for measuring the driving force of the crushing unit 30 are provided.
The driving force of the crushing unit 30 is, for example, electric power supplied from the driving device 20 for rotationally driving the crushing rotary table 35. When the crushing roller 36 is also driven by electric power in the crushing section 30, the driving force of the crushing rotary table 35 and the crushing roller 36 may be acquired as the driving force of the crushing section 30. Various results measured by these measuring instruments are output to the control device 15.

The control device 15 is composed of, for example, a CPU (Central Processing Unit), a RAM (Random Access Memory), a ROM (Read Only Memory), a computer-readable storage medium, and the like. As an example, a series of processes for realizing various functions are stored in a storage medium or the like in the form of a program, and the CPU reads this program into a RAM or the like to execute information processing / arithmetic processing. As a result, various functions are realized. The program is installed in a ROM or other storage medium in advance, is provided in a state of being stored in a computer-readable storage medium, or is distributed via a wired or wireless communication means. Etc. may be applied. The computer-readable storage medium is a magnetic disk, a magneto-optical disk, a CD-ROM, a DVD-ROM, a semiconductor memory, or the like.

As shown in FIG. 2, the control device 15 includes a load derivation unit 16, a performance value derivation unit 17, a determination unit 18, and a load control unit 19, and performs operation control processing of the mill 1.

The load derivation unit 16 derives the load factor of the mill 1. Specifically, as information relating to the current operating state of the mill 1, the measurement results of various measuring instruments provided in the mill 1 are acquired, and the load factor of the mill 1 is derived based on the acquired measurement results. In the present embodiment, the load derivation unit 16 measures the coal supply amount measured by the coal supply amount measuring instrument 21, the primary air amount measured by the primary air amount measuring instrument 22, and the classifier rotation speed as the measurement results of various measuring instruments. The rotation speed of the classifier measured by the instrument 23, the oil pressure measured by the hydraulic measuring instrument 24, and the rotation speed of the crushing rotary table 35 measured by the table rotation speed measuring instrument 25 are acquired.
Further, the load derivation unit 16 acquires information on the properties of coal. In detail, an index showing the difficulty of crushing coal is obtained. The index indicating the difficulty of crushing coal is, for example, a Hardgrove Grindability Index (HGI). The HGI is input to the control panel 28 or the like by the operator of the power plant (mill 1), for example, and the load derivation unit 16 acquires the HGI from the control panel 28. If the HGI can be measured (or estimated) by the measuring instrument in the mill 1, the mill 1 may acquire the HGI from the measuring instrument. Further, as long as it is an index showing the difficulty of crushing the solid fuel, it can be used not only as a hard glove crushability index, and for example, total water content or the like may be used.

The mill load factor ML is obtained from the measurement results of the above-mentioned measuring instrument. Hereinafter, an example of a method for deriving the mill load factor ML performed by the load deriving unit 16 according to the present embodiment will be described.
The mill load factor ML is calculated by, for example, the following equation (2).
ML = C / C1 ... (2)
However, C: coal supply amount C1: coal properties

Further, the coal property C1 is calculated by the following formula (3).
C1 = C0 x Fm x Ff x Fg x (other coefficients) ... (3)
However, C0: standard crushing capacity in mill 1
Fm: Mill capacity correction coefficient due to difference in water content
Ff: Mill capacity correction coefficient based on mill fineness (for example, outlet 200 # pass rate) Fg: Mill capacity correction coefficient based on coal grindability index (for example, HGI)

Further, the outlet 200 # pass rate is a table or the like that defines the correlation between the outlet 200 # pass rate created by using the data at the time of the trial run of the mill 1 and the theoretical classification diameter obtained from the classifier rotation speed and the amount of air. Demanded by. That is, the outlet 200 # pass rate can be estimated by applying the measured rotation speed of the classifier and the primary air amount to the table.

The performance value derivation unit 17 is a performance value of the mill 1 when the mill 1 is operated at a load factor derived by the load derivation unit 16 at a predetermined reference time based on the performance value measured by the performance value measurement unit. Is derived. In the present embodiment, the predetermined reference time is the test run of the mill 1 (that is, before the wear of the crushing roller 36). Further, in the present embodiment, the differential pressure measuring unit and the driving force measuring unit are used as the performance value measuring unit. Further, in the present embodiment, the circulating coal differential pressure between the pressure of the primary air duct 13 and the pressure of the coal feed pipe 9 and the driving force of the crushing unit 30 are used as the performance values.
Therefore, in the mill 1 according to the present embodiment, the mill 1 in the state at the time of trial run is the mill currently in operation based on the differential pressure measured by the differential pressure measuring instrument 26 and the driving force measured by the driving force measuring instrument 27. The performance value derivation unit 17 derives the circulating coal differential pressure and the driving force when operating at the same load factor as 1.

The circulating coal differential pressure is a differential pressure measured by the differential pressure measuring instrument 26 in a state where an object to be crushed such as coal is not supplied to the mill 1 (hereinafter referred to as “air differential pressure”). It is the differential pressure calculated by subtracting. That is, the circulating coal differential pressure is the differential pressure caused by the pressure loss caused by the pulverized coal filling the mill 1. The air differential pressure is the pressure of the primary air duct 13 and the coal feeding in the state where the air is supplied from the primary air duct 13 into the mill 1 before the object to be crushed is supplied into the mill 1. It is calculated by the pressure of the tube 9. The calculation for calculating the circulating coal differential pressure may be performed by the differential pressure measuring instrument 26 or the control device 15. In this embodiment, the case of calculation by the control device 15 will be described.

Therefore, in the mill 1 according to the present embodiment, the state at the time of trial run is based on the circulating coal differential pressure calculated based on the differential pressure measured by the differential pressure measuring instrument 26 and the driving force measured by the driving force measuring instrument 27. The performance value (circulating coal differential pressure and driving force) when the mill 1 is operated at the same load factor as the currently operating mill 1 is derived by the performance value derivation unit 17.

Specifically, the performance value derivation unit 17 uses a graph (see the solid line in FIG. 6) and a table showing the relationship between the driving force and the load factor during the trial run of the mill 1 to obtain the mill 1 currently in operation. The driving force at the reference time of the mill 1 according to the load factor is derived. Note that FIG. 6 is a graph showing the relationship between the mill load factor and the pressure loss. The solid line shows before the roller wear, and the broken line shows the roller wear time.
Further, the performance value derivation unit 17 uses a graph (see the solid line in FIG. 7) and a table showing the relationship between the circulating coal differential pressure and the load factor during the trial run of the mill 1 to load the mill 1 during the current operation. The circulating coal differential pressure at the reference time of the mill 1 according to the rate is derived. Note that FIG. 7 is a graph showing the relationship between the mill load factor and the driving force. The solid line shows the roller before wear, and the broken line shows the roller wear time.

The determination unit 18 compares the current performance value measured by the performance value measurement unit with the reference performance value derived by the performance value derivation unit 17, and is it necessary to adjust (correct) the pressing load by the tension rod 39? , Judge if it is unnecessary. Specifically, when the current driving force W measured by the driving force measuring instrument 27 is larger than the driving force Wi at the reference time derived by the performance value deriving unit 17 (Wi> W), and the difference. When the circulating coal differential pressure ΔPc measured by the pressure measuring instrument 26 is smaller than the circulating coal differential pressure ΔPci at the reference time derived by the performance value derivation unit 17 (ΔPc <ΔPci), it is determined that adjustment is necessary. .. If either condition is not met, it is determined that adjustment is not necessary.
The determination criteria of the determination unit 18 are an example, and the determination criteria are not limited to these. For example, when the current driving force W measured by the driving force measuring instrument 27 is larger than the driving force Wi at the reference time derived by the performance value deriving unit 17 by a predetermined threshold value α or more (Wi> W + α). When the circulating coal differential pressure ΔPc measured by the differential pressure measuring instrument 26 is β smaller than a predetermined threshold value by the reference time circulating coal differential pressure ΔPci derived by the performance value derivation unit 17 (ΔPc <ΔPci−β). May determine that adjustment is necessary.
Further, in the above description, an example of determining that adjustment is necessary when both of the two conditions are satisfied has been described, but when either of the two conditions is satisfied, adjustment is necessary. You may judge.

In the load control unit 19, the current performance value (driving force and circulating coal differential pressure) of the crushing device measured by the performance value measurement unit is the performance value (driving force) of the mill 1 at the reference time derived by the performance value derivation unit 17. And the hydraulic pressure (pressing load) applied to the tension rod 39 is adjusted so as to have the same value as the circulating coal differential pressure). Specifically, the oil pressure is adjusted using FIGS. 8 and 9, which are graphs showing the relationship between the oil pressure and the performance value.

FIG. 8 is a graph relating to the method of adjusting the pressing load, in which the horizontal axis represents the hydraulic pressure Op and the vertical axis represents the driving force ratio (W / Wi). The solid line indicates before the roller wear, and the broken line indicates the time when the roller wears. The data before the roller wear is acquired at the time of trial run of the mill 1.
As shown in FIG. 8, when the pressing load is applied to the crushing roller 36 by the hydraulic pressure of Opi before the roller is worn, the pressing load is applied by the hydraulic pressure of Op when the roller is worn. The driving force can be the same as that before wear (that is, the driving force ratio (W / Wi) is 1). Therefore, in this case, the load control unit 19 reduces the hydraulic pressure by the difference between Opi and Op.

Further, FIG. 9 is a graph relating to the method of adjusting the pressing load, in which the horizontal axis indicates the hydraulic pressure Op and the vertical axis indicates the circulating coal differential pressure ratio (ΔPc / ΔPci). The solid line indicates before the roller wear, and the broken line indicates the time when the roller wears. The data before the roller wear is acquired at the time of trial run of the mill 1.
As shown in FIG. 9, even when the pressing load is applied to the crushing roller 36 by the hydraulic pressure of Opi before the roller is worn, the pressing load is applied by the hydraulic pressure of Op when the roller is worn. Then, the same circulating coal differential pressure as before the roller wear (that is, the circulating coal differential pressure ratio (ΔPc / ΔPci) becomes 1) can be obtained. Therefore, in this case, the load control unit 19 reduces the hydraulic pressure by the difference between Opi and Op.

Next, the operation control process performed by the control device 15 according to the present embodiment will be described with reference to FIGS. 3 and 4.
The control device 15 acquires data necessary for deriving the load factor of the mill 1 (S1). Specifically, the load derivation unit 16 of the control device 15 measures the coal supply amount measured by the coal supply amount measuring instrument 21 which is the measurement result of various measuring instruments provided in the mill 1, and the primary air amount measuring instrument 22 measures. The primary air amount, the classifier rotation speed measured by the classifier rotation speed measuring instrument 23, the hydraulic pressure measured by the hydraulic pressure measuring instrument 24, and the rotation speed of the crushing rotary table 35 measured by the table rotation speed measuring instrument 25 are acquired. Further, the load derivation unit 16 acquires the HGI of coal, which is crushing symmetric, from the control panel 28.

When the data necessary for deriving the load factor of the mill 1 is acquired, the load deriving unit 16 of the control device 15 derives the mill load factor based on the data acquired in S1 (S2). After deriving the mill load factor, the control device 15 then derives the driving force Wi and the circulating coal differential pressure ΔPci of the mill 1 at the reference time by the performance value deriving unit 17 (S3). After deriving the driving force Wi of the mill 1 and the circulating coal differential pressure ΔPci at the reference time, the control device 15 then performs the performance value acquisition process and acquires the current performance value (S4). The details of the performance value acquisition process will be described later.

When the current performance value is acquired in S4, the control device 15 shifts to S5. In S5, the determination unit 18 compares the current performance value (W, ΔPc) acquired in S4 with the reference performance value (Wi, ΔPci) derived in S3. Specifically, the current driving force W is larger than the driving force Wi at the reference time (Wi> W), and the current circulating coal differential pressure ΔPc is smaller than the circulating coal differential pressure ΔPci at the reference time (Wi). It is determined whether or not ΔPc <ΔPci).

If it is determined in S5 that the condition is satisfied, the process proceeds to S6. In S6, the load control unit 19 applies the hydraulic pressure (pressing load) applied by the tension rod 39 so that the current performance value (W, ΔPc) becomes the same value as the reference performance value (Wi, ΔPci). Decide to adjust. When it is decided to adjust the hydraulic pressure in S6, the process proceeds to S7. In S7, the hydraulic pressure control signal is transmitted to the tension rod 39, and the hydraulic pressure is adjusted as determined in S6. When the hydraulic control signal is transmitted, the control device 15 ends this process.

If it is determined in S5 that the conditions are not satisfied, the process proceeds to S8. In S8, it is determined not to adjust the hydraulic pressure (pressing load) applied to the tension rod 39. When it is decided to adjust the hydraulic pressure in S8, the process proceeds to S7. In S7, a hydraulic pressure control signal that does not adjust the hydraulic pressure as determined in S8 is transmitted to the tension rod 39. When the hydraulic control signal is transmitted, the control device 15 ends this process.

Next, the performance value acquisition process performed in S4 of the operation control process will be described with reference to the flowchart of FIG.
When this process is started, the control device 15 first acquires the primary air amount measured by the primary air amount measuring device 22 (S11). Next, it shifts to S12 and acquires the air differential pressure. After acquiring the air differential pressure, the control device 15 then acquires the differential pressure from the differential pressure measuring instrument 26 (S13). When the differential pressure is acquired, the control device 15 calculates the circulating coal differential pressure (ΔPc) based on the differential pressure acquired in S13 and the air differential pressure acquired in S12 (S14). Specifically, the circulating coal differential pressure (ΔPc) is calculated by dividing the air differential pressure acquired in S12 from the differential pressure acquired in S13. When the circulating coal differential pressure (ΔPc) is calculated, the control device 15 acquires the driving force (W) from the driving force measuring instrument 27 (S15). When the driving force (W) is acquired, the control device 15 ends this process.

The process described above is an example, and the present invention is not limited thereto. For example, as shown in FIG. 5, the determination unit 18 may make a determination. In FIG. 5, the step in which the determination unit 18 makes a determination is different from the example shown in FIG. Since the other steps are the same as those in FIG. 3, detailed description thereof will be omitted.
In the example shown in FIG. 5, in S25, the ratio of the current performance value (W, ΔPc) acquired in S4 to the reference performance value (Wi, ΔPci) derived in S3 (η (η = W /). Wi), λ (λ = ΔPc / ΔPci)) is derived, and the time change (dη / dt, dλ / dt) of their ratio is derived. The time change (dη / dt) of the driving force ratio is larger than 0 (dη / dt> 0), and the time change (dλ / dt) of the circulating coal differential pressure (ΔPc) ratio is larger than 0. It is determined whether or not it is small (dλ / dt <0). If it is determined that the condition is satisfied, the process proceeds to S6, and if it is determined that the condition is not satisfied, the process proceeds to S8.

According to this embodiment, the following effects are exhibited.
As a parameter that affects the performance value of the mill 1, there is a crushing capacity C of the mill 1. The crushing capacity C of the mill 1 is calculated by the following formula (4).
C = k × M × ω × D ... (4)
However, k: coefficient
M: Pressing load on the crushing roller
ω: Number of rotations of the crushing rotary table
D: Diameter of crushing rotary table As described above, as parameters for determining the crushing capacity C of the mill 1, there are a pressing load, a rotation speed of the crushing rotary table 35, and a diameter of the crushing rotary table 35. The diameter of the crushing rotary table 35 cannot be easily changed after the crushing rotary table 35 is installed once. Therefore, the inventors focused on the pressing load and the rotation speed of the crushing rotary table 35. The crushing capacity C can be increased or decreased by changing the pressing load and / or the rotation speed of the table portion. By increasing or decreasing the crushing capacity C, the performance value of the mill 1 can be adjusted. Hereinafter, the product of the pressing load, which is an element that determines the crushing capacity C, and the rotation speed of the crushing rotary table 35 is also referred to as crushing energy.
11A to 11C show the basic concept of this embodiment. When the supply amount of coal to the mill 1 is constant, the crushing energy is constant as shown in FIG. 11A in the conventional case (without control). Therefore, as shown in FIG. 11B, the pressure loss (circulating coal differential pressure) of the mill 1 decreases with the passage of the crushing time, and the crushing power (driving force of the driving device 20) increases as shown in FIG. 11C. On the other hand, in the case of the present embodiment (with control), the crushing energy is adjusted with the lapse of the crushing time as shown in FIG. 11A. In the present embodiment, the crushing energy is adjusted by adjusting the pressing load. By adjusting the crushing energy and controlling the pressure loss (circulating coal differential pressure) and the crushing power (driving force of the driving device 20) to be constant as shown in FIGS. 11B and 11C, the mill 1 Appropriate operation is possible according to changes over time.

With the operation of the mill 1, the crushing unit 30 (crushing rotary table 35 and crushing roller 36) for crushing coal changes over time. Examples of the secular variation of the crushing portion 30 include deformation of the crushing roller 36 and the crushing rotary table 35 due to wear and the like. As the crushed portion 30 changes over time, the performance value of the mill 1 fluctuates.
Further, since the crushing unit 30 crushes the coal by sandwiching the coal between the upper surface of the crushing rotary table 35 and the crushing roller 36, the performance value of the mill 1 ( In this embodiment, the driving force of the crushing unit 30 and the differential pressure of the circulating coal) vary.
In the present embodiment, the load control unit 19 adjusts the pressing load applied by the tension rod 39 so that the current performance value of the mill 1 approaches the performance value of the mill 1 at the reference time. As described above, the pressing load is one of the parameters that affect the performance value. As a result, even if the crushing unit 30 changes over time with the operation of the mill 1, the performance value of the mill 1 can be used as the performance value at the reference time. Since the performance value can be controlled in this way, even if the crushing unit 30 changes over time, the mill 1 can be appropriately operated according to the performance value (aging of the crushing unit 30).

In the present embodiment, since the pressurizing arm 37 is swingable with respect to the crushing rotary table 35 and the crushing roller 36 is swingably supported with respect to the pressurizing arm 37, a plurality of crushing rollers 36 are provided. It has a structure that can be moved in any direction. That is, the crushing roller 36 is supported with a relatively high degree of freedom with respect to the crushing rotary table 35. As a result, the crushing roller 36 moves to the position where the load is the least among the movable positions when crushing the coal. Generally, the crushing mode by the crushing unit 30 differs depending on the installation environment of the mill 1, the properties of the coal to be crushed, and the like. Since the crushing roller 36 of the present embodiment moves to the position where the load is the least when crushing, it wears according to the crushing mode in the mill 1. Therefore, the shape of the crushing roller 36 changes with aging so as to have a shape suitable for the crushing mode in the mill 1. Therefore, in the present embodiment, the performance value of the mill 1 changes so that the crushing performance (grinding efficiency) improves as the crushing portion 30 changes over time.

In the present embodiment, the pressing load of the tension rod 39 is adjusted so that the pressing load applied to the tension rod 39 is reduced. When the pressing load is reduced, the force for sandwiching the coal between the crushing rotary table 35 and the crushing roller 36 is weakened, so that the crushing performance is suppressed. As a result, it is possible to suppress the improvement of the crushing performance due to the aging of the crushing unit 30, and to suppress the excessive crushing of coal by the crushing unit 30. Therefore, it is possible to reduce the rate of wear and the like of the crushed portion 30 due to excessive crushing, and extend the product life of the crushed portion 30. By extending the product life of the crushing unit 30, it is possible to improve the operating rate of the plant or the like to which the crushing unit 30 is applied.

Further, in the present embodiment, since the crushing unit 30 changes over time, the crushing performance (crushing efficiency) is improved, so that the amount of crushed coal increases and the driving force of the crushing unit 30 increases, but the tension rod 39 Since the pressing load applied by the coal is reduced and the improvement of the crushing performance is suppressed, the increase in the driving force of the crushing portion 30 can also be suppressed. Therefore, it is possible to suppress an increase in the driving force of the crushing portion 30 due to excessive crushing and to save energy in the mill 1.

When the crushing section 30 changes over time, the crushing performance of the crushing section 30 also changes according to the aging of the crushing section 30. As a result, the driving force for driving the crushing unit 30 also changes. As a factor of the change in the driving force, the crushing performance is lowered due to the change in the shape of the crushing portion 30, so that more driving force is required and the crushing performance is improved by the change in the shape of the crushing portion 30. As a result, the amount of crushed coal increases. In the present embodiment, the driving force of the crushing unit 30 that changes due to the secular variation of the crushing unit 30 is used as the performance value. Therefore, it is possible to accurately grasp the secular variation of the crushed portion 30.

Further, in the present embodiment, since the driving force for driving the crushing unit 30 is used as the performance value of the mill 1, even if the crushing unit 30 changes over time due to the operation of the mill 1, the crushing unit 30 is used. The driving force to be driven can be a driving force at a predetermined reference time. Since the driving force can be controlled in this way, the mill 1 can be operated with an appropriate driving force even if the crushing portion 30 changes over time. Therefore, it is possible to accurately suppress an increase in the driving force of the crushing portion 30 due to excessive crushing, and to further save energy in the mill 1.

When the crushing section 30 changes over time, the crushing performance of the crushing section 30 also changes according to the aging of the crushing section 30. As the crushing performance changes, the amount of crushed coal in the mill 1 also changes. Since the amount of crushed coal causes a pressure loss with respect to the air flow for transportation, the differential pressure of circulating coal between the primary air duct 13 and the coal feed pipe 9 also changes. That is, the circulating coal differential pressure also changes according to the secular variation of the crushed portion 30. In the present embodiment, the circulating coal differential pressure that changes due to the secular variation of the crushed portion 30 is used as the performance value. Therefore, it is possible to accurately grasp the secular variation of the crushed portion 30.

The relationship between the passage of time and the hydraulic pressure, driving force, and circulating coal differential pressure when the control device 15 of the mill 1 according to the present embodiment performs the operation control process will be described with reference to FIGS. 10A to 10C. In FIG. 10A, the horizontal axis shows the passage of time, and the vertical axis shows the hydraulic pressure of the tension rod 39. Further, in FIG. 10B, the horizontal axis shows the passage of time, and the vertical axis shows the driving force of the crushing unit 30. Further, in FIG. 10C, the horizontal axis shows the passage of time, and the vertical axis shows the circulating coal differential pressure. Further, in FIGS. 10A to 10C, the case where the operation control process is performed is shown by a solid line, and the case where the operation control process is not performed is shown by a dotted line.

When the operation control process is not performed, the hydraulic pressure of the tension rod 39 does not change in the mill 1 according to the present embodiment (see FIG. 10A). Further, the crushing ability is improved by the secular variation of the crushing unit 30. Therefore, as the amount of coal to be crushed increases, the driving force of the crushing unit 30 increases (see FIG. 10B). Further, since the crushing capacity is improved, the differential pressure of the circulating coal is reduced by crushing the coal appropriately (see FIG. 10C).
On the other hand, when the operation control process is performed, the hydraulic pressure of the tension rod 39 is reduced because the process is performed (see FIG. 10A). Further, when the hydraulic pressure of the tension rod 39 is reduced, the pressing force of the crushing roller 36 against the crushing rotary table 35 is also reduced, so that an increase in the driving force of the crushing portion 30 is suppressed (see FIG. 10B). By reducing the hydraulic pressure of the tension rod 39, the improvement of the crushing capacity is suppressed (that is, the circulating coal differential pressure is increased as compared with the case where control is not performed), but the crushing portion 30 is crushed before the secular variation. Capability is maintained (see Figure 10C).

That is, in the mill 1 of the present embodiment, when the crushing unit 30 changes over time as the mill 1 operates, the crushing power and the crushing capacity (circulating coal differential pressure) are maintained in the state before the aging, and the tension rod is used. The oil pressure of 39 can be reduced.

[Second Embodiment]
Next, a second embodiment of the crushing device and the control method of the crushing device according to the present invention will be described with reference to FIGS. 12 to 17D. The second embodiment is different from the first embodiment in that the control device 15 has a table rotation speed control unit 70. Further, a part of the operation control process performed by the control device 15 is different from that of the first embodiment. The same components as those in the first embodiment are designated by the same reference numerals, and detailed description thereof will be omitted.

As shown in FIG. 12, the control device 15 according to the present embodiment has a table rotation speed control unit 70. In the table rotation speed control unit 70, the current performance value (driving force and circulating coal differential pressure) of the crushing device measured by the performance value measurement unit is the performance value of the mill 1 at the reference time derived by the performance value derivation unit 17. The rotation speed of the crushing rotary table 35 rotated by the driving device 20 is adjusted so as to have the same value as the driving force and the circulating coal differential pressure). Specifically, the rotation speed is adjusted using FIGS. 15 and 16, which are graphs showing the relationship between the rotation speed of the crushing rotary table 35 and the performance value. Since the details of the adjustment of the rotation speed are substantially the same as the adjustment of the hydraulic pressure in the first embodiment (see FIGS. 8 and 9), the description thereof will be omitted.

Next, the operation control process performed by the control device 15 according to the present embodiment will be described with reference to FIG. Since S1 to S5 and S8 are the same as the operation control process in the first embodiment, the description thereof will be omitted. If it is determined in S5 that the condition is satisfied, the process proceeds to S26. In S26, the crushing rotary table 35 is rotated by the drive device 20 so that the current performance value (W, ΔPc) becomes the same value as the reference performance value (Wi, ΔPci) by the table rotation speed control unit 70. Decide to adjust the number of revolutions of. When it is decided to adjust the rotation speed in S26, the process proceeds to S27. In S27, the table rotation speed control signal is transmitted to the control device 15, and the rotation speed is adjusted as determined in S26. When the table rotation speed control signal is transmitted, the control device 15 ends this process.

As shown in FIG. 14, the control device 15 may perform an operation control process. Since S1 to S4, S8 and S25 in FIG. 14 are the same as those in the first embodiment, the description thereof will be omitted. Further, since S26 and S27 in FIG. 14 are the same as the example of FIG. 13, the description thereof will be omitted.

According to this embodiment, the following effects are exhibited.
In the present embodiment, the rotation speed of the crushing rotary table 35 is adjusted so that the current performance value of the mill 1 approaches the performance value of the mill 1 at the reference time. As described above, the rotation speed of the crushing rotary table 35 is one of the parameters affecting the performance value. As a result, even if the crushing unit 30 changes over time with the operation of the mill 1, the performance value of the mill 1 can be set to the performance value at a predetermined reference time. Since the performance value can be controlled in this way, even if the crushing unit 30 changes over time, the mill 1 can be appropriately operated according to the performance value (aging of the crushing unit 30).

17A to 17C show the relationship between the passage of time and the rotation speed, driving force, and circulating coal differential pressure of the crushing rotary table 35 when the control device 15 of the mill 1 according to the present embodiment performs the operation control process. It will be explained using. In FIG. 17A, the horizontal axis shows the passage of time, and the vertical axis shows the rotation speed of the crushing rotary table 35. Further, in FIG. 17B, the horizontal axis indicates the passage of time, and the circulating coal differential pressure is shown. Further, in FIG. 17C, the horizontal axis shows the passage of time, and the vertical axis shows the driving force of the crushing unit 30. Further, in FIGS. 17A to 17C, the case where the operation control process is performed is shown by a solid line, and the case where the operation control process is not performed is shown by a dotted line.

When the operation control process is not performed, the rotation speed of the crushing rotary table 35 does not change in the mill 1 according to the present embodiment (see FIG. 17A). Further, since the crushing capacity is improved, the differential pressure of the circulating coal is reduced by crushing the coal appropriately (see FIG. 17B). Further, the crushing ability is improved by the secular variation of the crushing unit 30. Therefore, as the amount of coal to be crushed increases, the driving force of the crushing unit 30 increases (see FIG. 17C).
On the other hand, when the operation control process is performed, the rotation speed is reduced because the process is performed to reduce the rotation speed (see FIG. 17A). Further, when the rotation speed is reduced, an increase in the driving force of the crushing unit 30 is suppressed (see FIG. 17C). By reducing the number of revolutions, the improvement of the crushing capacity is suppressed (that is, the circulating coal differential pressure increases as compared with the case where control is not performed), but the crushing capacity of the crushing unit 30 before aging is maintained. (See FIG. 17B).

That is, in the mill 1 of the present embodiment, when the crushing unit 30 changes over time with the operation of the mill 1, the crushing power and the crushing capacity (circulating coal differential pressure) are maintained in the state before the aging, and the number of revolutions is increased. Can be reduced.

The relationship between the passage of time and the vibration value of the mill 1 (crushing device) when the control device 15 of the mill 1 according to the present embodiment performs the operation control process will be described with reference to FIG. 17D. In FIG. 17D, the case where the operation control process of the present embodiment is performed (when the rotation speed is adjusted) is shown by a solid line, and the case where the operation control process of the first embodiment is performed (when the pressing load is adjusted) is 1. It is shown by a dotted line, and the case where the operation control process is not performed is shown by a dotted line.
Here, the vibration value of the mill 1 measures displacement, velocity, acceleration, and the like. If the vibration value becomes too large (that is, if the vibration becomes too large), the mill 1 may be damaged, so that the measurement is performed. If the operation control process is not performed, the vibration value increases. This is because the shape of the crushing roller 36 becomes distorted due to the progress of wear of the crushing roller 36, and the crushing roller 36 has a high degree of freedom with respect to the crushing rotary table 35. This is because stable ones shift to multipoint contact and become unstable. On the other hand, even when the rotation speed of the crushing rotary table 35 is reduced or the pressing load is reduced, the increase in the vibration value of the mill 1 is suppressed as compared with the case where the operation control process is not performed. can do. Further, when the rotation speed of the crushing rotary table 35 is reduced, it is possible to suppress an increase in the vibration value of the mill 1 more than when the pressing load is reduced.
By suppressing the increase in the vibration value of the mill 1, for example, coal or the like having a characteristic that the friction coefficient of the powder is small and vibration is likely to occur can be used as a raw material.

[Third Embodiment]
Next, a third embodiment of the crushing device and the control method of the crushing device according to the present invention will be described with reference to FIG. The third embodiment is different from the first embodiment and the second embodiment in that the control device 15 has both the load control unit 19 and the table rotation speed control unit 70, as shown in FIG. .. Further, a part of the operation control process performed by the control device 15 is different from the first embodiment and the second embodiment. The same components as those in the first embodiment are designated by the same reference numerals, and detailed description thereof will be omitted. In the present embodiment, the determination unit 18 obtains a command value for adjusting the pressing load and the rotation speed. The determination of the pressing load by the determination unit 18 is the same as that of the first embodiment, and the determination of the rotation speed is the same as that of the second embodiment. It should be noted that the judgment by combining the judgment of the pressing load and the judgment of the rotation speed becomes complicated, so it is desirable to utilize machine learning or the like.

By adjusting the pressing load and the rotation speed as in the present embodiment, the performance value can be controlled more accurately.

The present invention is not limited to the invention according to the above embodiment, and can be appropriately modified without departing from the gist thereof.
For example, in the above embodiment, the predetermined reference time is set as the test run time of the mill 1, but the present invention is not limited to this. For example, it may be during the initial operation of the crusher or during the break-in operation of the crusher. The time before the crushed portion 30 changes over time is preferable.

The mill 1 may include a learning unit (not shown) that performs machine learning for deriving the degree of adjustment of the pressing load applied by the tension rod 39. The learning unit derives the degree of adjustment based on machine learning. The tension rod 39 adjusts the pressing load applied by the tension rod 39 so as to have the adjustment degree derived by the learning unit. According to this configuration, the pressing load of the tension rod 39 can be accurately adjusted.

1: Mill (crusher)
9: Coal feed pipe 11: Hopper 13: Primary air duct (gas supply unit for transportation)
15: Control device (control unit)
16: Load derivation unit 17: Performance value derivation unit 18: Judgment unit 19: Load control unit 20: Drive device 21: Coal supply amount measuring instrument 22: Primary air amount measuring instrument 23: Classifier rotation speed measuring instrument 24: Hydraulic measurement Instrument 25: Table rotation speed measuring instrument 26: Differential pressure measuring instrument 27: Driving force measuring instrument 28: Control panel 30: Crushing unit 31: Housing 32: Ceiling unit 33: Center chute 34: Stand 35: Crushing rotation table (table unit) )
36: Crushing roller (roller part)
37: Pressurized arm (frame part)
38: Bracket 39: Tension rod (load applying part)
40: Tension rod box 41: Rotation classifier 42: Fin 44: Throat vane 49: Hydraulic cylinder part 50: Drive part 60: Primary air (transport gas)
ML: Mill load factor Op: Hydraulic W: Driving force Wi: Driving force ΔPc: Circulating coal differential pressure ΔPci: Circulating coal differential pressure

Claims (8)

A crusher that crushes the object to be crushed.
It has a table portion that is rotationally driven around an axis in the vertical direction and a roller portion that is arranged so as to face the upper surface of the table portion, and is crushed between the upper surface of the table portion and the roller portion. A crushing part that crushes the object to be crushed by sandwiching the object,
A load derivation unit that derives the load of the crushing device at present, and a load derivation unit.
A performance value measuring unit that measures the current performance value of the crushing device,
A performance value derivation unit for deriving the performance value of the crushing device when the crushing device is operated with the current load derived by the load deriving unit at a predetermined reference time different from the current timing .
The current performance value measured by the performance value measuring unit based on the current performance value of the crushing device measured by the performance value measuring unit and the performance value of the crushing device at the reference time derived by the performance value deriving unit. A control unit that changes parameters that affect the performance value of the crushing device so that the performance value of the crushing device approaches the performance value of the crushing device at the reference time derived by the performance value deriving unit. Equipped with a crusher. A load applying portion for applying a pressing load toward the upper surface of the table portion to the roller portion is provided.
The parameter has a pressing load applied to the roller portion.
The control unit is based on the current performance value of the crushing device measured by the performance value measuring unit and the performance value of the crushing device at the reference time derived by the performance value deriving unit. Load control that adjusts the pressing load applied by the load applying unit so that the current performance value of the crushing device measured by is close to the performance value of the crushing device at the reference time derived by the performance value deriving unit. The crushing device according to claim 1, which has a part. A rotation drive unit for rotationally driving the table unit so as to have a predetermined rotation speed is provided.
The parameter has the rotation speed of the table portion and has.
The control unit is based on the current performance value of the crushing device measured by the performance value measuring unit and the performance value of the crushing device at the reference time derived by the performance value deriving unit. The number of rotations of the table unit rotated by the rotation drive unit so that the current performance value of the crusher measured by the crusher approaches the performance value of the crusher at the reference time derived by the performance value derivation unit. The crushing device according to claim 1 or 2, further comprising a table rotation speed control unit for adjustment. A frame portion provided inside the housing of the crushing device and supporting the roller portion is provided.
The frame portion is swingable with respect to the table portion.
The roller portion is swingably supported with respect to the frame portion.
The crushing device according to claim 2, wherein the load control unit adjusts the pressing load of the load applying unit so that the pressing load applied by the load applying unit is reduced. The crushing device according to any one of claims 1 to 4, wherein the performance value of the crushing device includes a driving force for driving the crushing unit. A transport gas supply unit that supplies transport gas that transports the crushed object to the outside,
A discharge unit for discharging the object to be crushed transported by the transport gas is provided.
The crushing device according to any one of claims 1 to 5, wherein the performance value of the crushing device includes a differential pressure between the pressure on the transport gas supply unit side and the pressure on the discharge unit side. A learning unit that performs machine learning to derive the degree of adjustment of the pressing load applied by the load applying unit, and a learning unit.
The learning unit derives the adjustment degree based on the machine learning, and obtains the adjustment degree.
The crushing device according to claim 2, wherein the load control unit adjusts the pressing load applied by the load applying unit so as to have the adjustment degree derived from the learning unit. It is a control method of a crushing device that crushes an object to be crushed.
A crushing step of crushing an object to be crushed by sandwiching the object to be crushed between an upper surface of a table portion that is rotationally driven around an axis in the vertical direction and a roller portion arranged so as to face the upper surface of the table portion. When,
The load derivation step for deriving the load of the crushing device at present, and
The performance value measurement step for measuring the performance value of the crushing device at present, and
A performance value derivation step for deriving the performance value of the crushing device when the crushing device is operated with the current load derived in the load deriving step at a predetermined reference time different from the current timing .
Currently measured in the performance value measurement step based on the current performance value of the crusher measured in the performance value measurement step and the performance value of the crusher at the reference time derived in the performance value derivation step. A control step for changing parameters that affect the performance value of the crushing device so that the performance value of the crushing device approaches the performance value of the crushing device at the reference time derived in the performance value derivation step. How to control the crusher equipped.

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