JP6453028B2 - Crushing apparatus and lubricating oil replacement method for bearing of crushing apparatus - Google Patents

Description

  The present invention relates to a pulverizing apparatus and a lubricating oil replacement method for a bearing of the pulverizing apparatus.

A pulverizer is used to pulverize carbon-containing solid fuel such as coal used as fuel in a thermal power generation facility. The pulverizing apparatus pulverizes the carbon-containing solid fuel by pressing the carbon-containing solid fuel supplied to the pulverization table by the pulverizing roller. The pulverizing apparatus dries the pulverized carbon-containing solid fuel to classify it into fine particles, and supplies the classified carbon-containing solid fuel fine particles (pulverized coal in coal) to the outside.
Patent Document 1 describes that an eccentric shaft serving as a rotation shaft when a grinding roller included in a grinding device is brought close to or away from a grinding table is supported by a bearing device.

Japanese Patent Laid-Open No. 10-146536

Generally, a portion where a shaft member and a bearing device supporting the shaft member slide is filled with lubricating oil in order to improve and maintain the slidability.
When the bearing device is installed and operated in an environment where foreign matter such as fine particles exists in the vicinity of the bearing as in the pulverizing device described above, the foreign material enters the lubricating oil and deteriorates the lubricating oil. Therefore, there is a problem that the shaft member and the bearing member are worn.

  The bearing device disclosed in Patent Document 1 suppresses intrusion of pulverized coal into the bearing device using a seal gas. According to the bearing device disclosed in Patent Document 1, although pulverized coal can be prevented from entering the bearing device, pulverized coal that has entered the bearing device cannot be excluded. Therefore, the problem that the shaft member and the bearing member wear due to the pulverized coal that has entered the bearing device cannot be avoided.

  The present invention has been made to solve the above-described problem, and is a case where foreign matter enters a portion where the shaft member and the bearing member supporting the shaft slide and enters the lubricating oil. Another object of the present invention is to provide a crushing apparatus and a method for replacing a lubricating oil for a bearing in a crushing apparatus that can prevent a problem in which the lubricating oil deteriorates and wears the shaft member and the bearing member.

In order to solve the above problems, the present invention employs the following means.
A grinding apparatus according to an aspect of the present invention supports a grinding table, a grinding roller for grinding solid fuel between the grinding table, a shaft member that supports the grinding roller, and an outer peripheral surface of the shaft member. A bearing portion having an inner peripheral surface, and the bearing portion includes a cylindrical bearing member extending along a central axis, and externally supplied lubricating oil and an outer peripheral surface of the shaft member and an inner periphery of the bearing member. A lubricating oil supply section that supplies the lubricating oil space between the surface and a lubricating oil discharge section that collects the lubricating oil flowing out of the lubricating oil space and discharges the collected lubricating oil to the outside; The lubricating oil discharge portion has a lubricating oil discharge port for discharging the recovered lubricating oil to the outside, and the lubricating oil discharge port is in a flow state for allowing the recovered lubricating oil to flow out to the outside and the recovery to the outside The sealed state that does not allow the lubricating oil to flow out It includes a capability, the bearing member has a first annular groove formed in the inner peripheral surface of one end of the bearing member along the central axis, the other end portion of the bearing member along the central axis A second annular groove formed on the inner circumferential surface on the side, and at least around the central axis from one end connected to the first annular groove to the other end connected to the second annular groove A spiral groove formed on the inner peripheral surface so as to turn a part thereof, the lubricating oil supply section supplies the lubricating oil to the first annular groove, and the lubricating oil discharge section includes the second groove. The lubricating oil flowing out from the other end portion of the bearing member through the annular groove is discharged to the outside, and the grinding roller rotates about the shaft member, so that the distance to the outer peripheral portion of the grinding table And the lubricating oil is grease .

  According to the pulverizing apparatus according to one aspect of the present invention, the lubricating oil supplied from the outside is supplied to the first annular groove formed on the inner peripheral surface of the bearing member, and one end portion is connected to the first annular groove. Flows into the spiral groove. The lubricating oil that has flowed into the spiral groove turns around the central axis of the bearing member and then flows into the second annular groove from the other end of the spiral groove. The lubricating oil that has flowed into the second annular groove flows out from the other end of the bearing member, is collected by the lubricating oil discharge portion, and is discharged to the outside by the lubricating oil discharge portion.

Thus, according to the crushing device concerning one mode of the present invention, by supplying lubricating oil from the outside, the first annular groove, the spiral groove, and the second annular groove formed on the inner peripheral surface of the bearing device. The existing lubricating oil is discharged to the outside by the lubricating oil discharger and replaced with new lubricating oil.
Therefore, even when foreign matter such as fine powder of solid fuel pulverized by the pulverizer enters into the part where the shaft member and the bearing device supporting the shaft slide, the lubricating oil does not enter the lubricating oil. It is possible to prevent a problem that the shaft member and the bearing member are worn due to deterioration.

In the pulverizing apparatus according to one aspect of the present invention, the cross-sectional area of the second annular groove is larger than the cross-sectional area of the spiral groove, and the cross-sectional area of the first annular groove is larger than the cross-sectional area of the second annular groove. A large configuration may be used.
According to this configuration, since the cross-sectional area of the second annular groove is larger than the cross-sectional area of the spiral groove, the lubricating oil that has flowed into the spiral groove easily flows into the second annular groove when it flows out of the spiral groove. Further, since the cross-sectional area of the first annular groove is larger than the groove width of the second annular groove, the oil pressure of the lubricating oil in the second annular groove is easily increased, and the lubricating oil is appropriately discharged from the second annular groove. Can be made. Therefore, the replaceability of the lubricating oil in the bearing portion can be improved.

In the pulverizing apparatus according to one aspect of the present invention, the cross-sectional shape of the first annular groove, the cross-sectional shape of the second annular groove, and the cross-sectional shape of the spiral groove are semicircular, and the groove of the spiral groove The groove width of the second annular groove may be wider than the width, and the groove width of the first annular groove may be wider than the groove width of the second annular groove.
According to this configuration, since the groove width of the second annular groove is wider than the groove width of the spiral groove, the lubricating oil that has flowed into the spiral groove tends to flow into the second annular groove when flowing out of the spiral groove. Further, since the groove width of the first annular groove is wider than the groove width of the second annular groove, the oil pressure of the lubricating oil in the second annular groove is easily increased, and the lubricating oil is appropriately discharged from the second annular groove. Can be made. Therefore, the replaceability of the lubricating oil in the bearing portion of the pulverizer can be improved.

In the said structure, the width | variety of the edge part by the side of the other end part of the said bearing member of the said 2nd annular groove and the other end part of the said bearing member may be narrower than the groove width of the said 2nd annular groove.
By doing in this way, the outflow of the lubricating oil from the second annular groove to the other end portion of the bearing member can be facilitated, and the replaceability of the lubricating oil in the bearing portion of the crushing device can be further improved.

  In the pulverizing apparatus according to one aspect of the present invention, a substantially cylindrical holding member that accommodates an end portion of the shaft member and the bearing member is attached to an inner peripheral surface, and one end of the holding member in the central axis direction An annular fixing member that is attached to a portion and fixes the position of the bearing member in the central axis direction, and is disposed between an inner peripheral surface of the fixing member and an outer peripheral surface of the shaft member, and an external space. A seal portion that cuts off the space between the lubricating oil space, and the fixing member is configured so that the thrust bearing attached to the shaft member rotates around the central axis as the shaft member rotates. The seal portion slides in contact with the first seal member that suppresses leakage of the lubricating oil from the lubricating oil space to the outer space, and foreign matter enters the lubricating oil space from the outer space. Suppressed The first seal member is disposed closer to the bearing member than the second seal member, and the first seal member and the second seal member are continuously disposed. May be.

According to this configuration, the bearing member is attached to the inner peripheral surface of the holding member that houses the end portion of the shaft member. The position of the bearing member in the central axis direction is fixed by an annular fixing member. The external space and the lubricating oil space are blocked by a seal portion disposed between the inner peripheral surface of the fixing member and the outer peripheral surface of the shaft member. By continuously arranging the first seal member and the second seal member that the seal portion has, the first seal member disposed on the bearing member side suppresses leakage of the lubricant from the lubricant space to the external space. In addition, the second seal member suppresses entry of foreign matter from the external space into the lubricating oil space.
Therefore, according to this configuration, leakage of the lubricating oil from the lubricating oil space to the external space and entry of foreign matter from the external space to the lubricating oil space can be appropriately suppressed.

In the above configuration, the first seal member and the second seal member have the same shape and are formed of the same material, and the first lip of the first seal member and the second lip of the second seal member May be arranged symmetrically in the direction along the central axis.
By doing in this way, a pair of seal members of the same shape and the same material are arranged so that the first lip of the first seal member and the second lip of the second seal member are symmetrical in the direction along the central axis. With this relatively simple configuration, leakage of the lubricating oil from the lubricating oil space to the external space and entry of foreign matter from the external space to the lubricating oil space can be appropriately suppressed.

  In the above, the bearing portion has a shaft main body and a cylindrical sleeve attached to the outer peripheral surface of the shaft main body, and the bearing member and the seal portion are in contact with the outer peripheral surface of the sleeve. The step portion formed on the inner peripheral side of the fixing member accommodates the seal portion and a liner that is an annular plate member, and includes the bearing member, the seal portion, and the liner. The fixing member is disposed in contact with the fixing member in this order along the central axis, and the end of the outer peripheral surface of the sleeve and the end of the second lip are arranged at a predetermined distance depending on the thickness of the liner. They may be separated as described above.

  By doing in this way, even if the fixing member moves in the central axis direction by sliding between the fixing member and the thrust bearing, and the seal portion moves in the central axis direction accordingly, the moving distance is predetermined. If it is less than the distance, the end of the second lip does not reach the end of the outer peripheral surface of the sleeve. Accordingly, it is possible to appropriately suppress the entry of foreign matter from the external space into the lubricating oil space by the second lip. Since the predetermined distance is a distance depending on the thickness of the liner, the predetermined distance can be appropriately adjusted by using a liner having an appropriate thickness.

According to one aspect of the present invention, there is provided a lubricating oil replacement method for a bearing of a grinding device, a grinding table, a grinding roller for grinding solid fuel between the grinding table, a shaft member that supports the grinding roller, and the shaft and a bearing portion having an inner peripheral surface for supporting the outer peripheral surface of the member, the grinding rollers, by rotating around the shaft member, the grinding apparatus the distance to the outer periphery you change the grinding table A method for replacing a lubricating oil for a bearing , wherein the bearing portion includes a cylindrical bearing member extending along a central axis, and a lubricating oil space between an outer peripheral surface of the shaft member and an inner peripheral surface of the bearing member. It has a lubricating oil discharge part for collecting the lubricating oil flowing out and discharging the collected lubricating oil to the outside, and the lubricating oil discharging part has a lubricating oil discharge port for discharging the collected lubricating oil to the outside The lubricating oil discharge port is recovered to the outside. A flow state to flow out of lubricating oil, a function of switching between the sealed state not to flow out the lubricating oil the recovery to the outside, the bearing member, the inner end portion side of the bearing member along the central axis A first annular groove formed on the peripheral surface, a second annular groove formed on the inner peripheral surface on the other end side of the bearing member along the central axis, and the first annular groove are connected. A lubricating oil supply having a spiral groove formed on the inner peripheral surface so as to turn at least part of the periphery of the central axis from the one end to the other end connected to the second annular groove. A lubricating oil supply step of supplying lubricating oil supplied from the outside through the section to the first annular groove, and lubrication for circulating the lubricating oil from the first annular groove to the second annular groove through the spiral groove Oil flows out from the other end of the bearing member through the second annular groove And a lubricant oil discharge step of discharging the lubricating oil said recovered to the outside from the lubricant discharge unit with recovering the lubricating oil, the lubricating oil is Ru Oh grease.

  According to the lubricating oil replacement method for a bearing of a grinding apparatus according to an aspect of the present invention, the lubricating oil supplied from the outside is supplied to the first annular groove formed on the inner peripheral surface of the bearing member, and the first It flows into the spiral groove whose one end is connected to the annular groove. The lubricating oil that has flowed into the spiral groove turns around the central axis of the bearing member and then flows into the second annular groove from the other end of the spiral groove. The lubricating oil that has flowed into the second annular groove flows out from the other end of the bearing member and is collected, and is discharged to the outside through the lubricating oil discharge portion.

Thus, according to the lubricating oil replacement method for a bearing of a grinding device according to an aspect of the present invention, the first annular groove and the spiral formed on the inner peripheral surface of the bearing device by supplying the lubricating oil from the outside. Lubricating oil present in the groove and the second annular groove is discharged to the outside by the lubricating oil discharger and replaced with new lubricating oil.
Therefore, even when foreign matter such as fine powder of solid fuel pulverized by the pulverizer enters into the part where the shaft member and the bearing device supporting the shaft slide, the lubricating oil does not enter the lubricating oil. It is possible to prevent a problem that the shaft member and the bearing member are worn due to deterioration.

  According to the present invention, even when foreign matter enters a portion where the shaft member and the bearing member supporting the shaft slide and enters the lubricating oil, the lubricating oil deteriorates and the shaft member or the bearing It is possible to provide a pulverizing apparatus and a method for replacing a lubricating oil for a bearing of the pulverizing apparatus that can prevent a problem that the member is worn.

It is a longitudinal section showing a solid fuel crusher concerning one embodiment of the present invention. It is sectional drawing which shows the roller support part of the solid fuel crusher shown in FIG. It is sectional drawing which shows the bearing apparatus which concerns on one Embodiment of this invention. It is a principal part enlarged view of the bearing apparatus shown in FIG. It is sectional drawing which shows the bush shown in FIG. It is an expanded view which shows the bush shown in FIG.

Hereinafter, a carbon-containing solid fuel pulverization apparatus (for example, a coal pulverization mill apparatus) according to an embodiment of the present invention will be described. The carbon-containing solid fuel pulverization apparatus is an apparatus for pulverizing carbon-containing solid fuel such as coal. Hereinafter, a solid fuel pulverizer, which is a general generic name including a carbon-containing solid fuel pulverizer, will be described with reference to the drawings.
The solid fuel pulverization apparatus 10 of this embodiment is an apparatus of a type called a vertical mill.
The solid fuel crusher 10 of this embodiment includes a housing 11, a crushing table 12, a crushing roller 13, a drive unit 14, a drive shaft 15, a classification unit 16, and a solid fuel input unit 17.

The housing 11 is a hollow member having a substantially cylindrical shape and forms the outer peripheral surface of the solid fuel crusher 10. A carrier gas (such as air or nitrogen gas) is supplied to the lower end of the housing 11 via the flow path 18. The housing 11 is fixed to the upper surface of a rectangular parallelepiped concrete block 19 installed on the floor.
The crushing table 12 is disposed at a lower portion in the housing 11 and is attached to be rotatable around an axis extending in the vertical direction. The crushing table 12 rotates around the drive shaft 15 by the drive force from the drive unit 14.

  At a plurality of locations outside the crushing table 12, air outlets 32 are provided for allowing the carrier gas flowing in from the flow path 18 to flow out into the space above the crushing table 12 in the housing 11. A liner 33 is installed above the air outlet 32, and the liner 33 gives a turning force to the carrier gas blown out from the air outlet 32. The carrier gas to which the turning force is applied by the liner 33 becomes an air current as shown by an arrow in FIG. 1 and the carbon-containing solid fuel (hereinafter simply referred to as solid fuel) pulverized on the pulverization table 12 is the housing 11. To the classifying unit 16 above. When coal is used as the solid carbon fuel, the pulverized solid fuel becomes pulverized coal. Of the pulverized solid fuel mixed with the carrier gas, the pulverized product having a large particle size falls without reaching the classification unit 16 and is returned to the pulverizing table 12 and pulverized again.

The crushing roller 13 is pressed against the crushing surface 12 c of the crushing table 12 and crushes solid fuel such as coal with the crushing table 12 as the crushing table 12 rotates. The solid fuel becomes a pulverized fuel by being pulverized.
In FIG. 1, only one crushing roller 13 is shown, but a plurality of rollers 13 are arranged at regular intervals in the outer circumferential direction so as to press the crushing surface 12 c of the crushing table 12. For example, three rollers 13 are arranged on the outer peripheral portion 12b with an angular interval of 120 °. In this case, the portions where the three rollers 13 are in contact with the pulverizing surface 12 c (the portions to be pressed) of the pulverizing table 12 are equidistant from the central portion 12 a of the pulverizing table 12.

The classifying unit 16 includes a blade that rotates about the cylindrical axis of the substantially cylindrical housing 11. The pulverized product of the solid fuel that has reached the classification unit 16 has only a fine fuel smaller than a predetermined particle size flow into the blade due to the relative balance between centrifugal force and centripetal force generated by the flow of the rotating blade and the carrier gas. It flows out from the outlet 34 together with the carrier gas. The outlet 34 communicates with a supply channel (not shown) connected to a burner (not shown). When coal is used as the solid fuel, the coal is pulverized by the pulverization table 12 to generate pulverized coal, and the pulverized coal discharged from the outlet 34 is supplied to the pulverized coal burner.
The solid fuel input part 17 is attached so as to penetrate the upper end of the housing 11 and supplies the solid fuel input from the upper part to the central part 12 a of the crushing table 12.

Next, the configuration of the grinding roller 13 and the roller support portion 20 will be described with reference to FIG.
The outer space shown in FIG. 2 includes an inner housing outer space SA and an outer housing outer space SB. The housing internal / external space SA and the housing external / external space SB are both spaces located outside an internal space SP described later. The internal / external space SA is a space located inside the housing 11, and the external / external space SB is a space located outside the housing 11. Since the housing internal / external space SA is located inside the housing 11, it is a space in which pulverized coal or the like obtained by pulverizing solid fuel exists at high temperature (for example, about 250 ° C.).

The crushing roller 13 is supported on the housing 11 by a roller support portion 20.
The roller support unit 20 includes a rotary shaft 21 to which the grinding roller 13 is attached, a main body 22 that holds the rotary shaft 21, an eccentric shaft 23 (shaft member) that is fixedly attached to a side portion of the main body 22, and the main body 22. The arm 24 is attached to the upper surface so as to extend upward, and the protrusion 25 is provided on the lower surface of the main body 22 so as to protrude downward.

A hollow hub 26 having a substantially cylindrical shape is attached to the center of the crushing roller 13. The roller 13 is attached to the distal end portion of the rotating shaft 21 via the hub 26. Therefore, the roller 13 is rotatable in the circumferential direction around the rotation shaft 21.
The eccentric shaft 23 is arranged so that the central axis thereof is substantially horizontal and extends in the tangential direction of the circular shape of the grinding table 12. The roller support portion 20 is rotatable about the eccentric shaft 23. As the roller support portion 20 rotates about the eccentric shaft 23, the distance of the grinding roller 13 to the outer peripheral portion 12b of the grinding table 12 changes.

  A load applying portion 27 that presses the upper end portion of the arm 24 is attached to the housing 11. The load adding portion 27 includes an intermediate piston 28 attached to the housing 11 so as to be movable in the longitudinal direction, and a hydraulic load portion 29 attached to the outer periphery of the housing 11 and pressing the outer end portion of the intermediate piston 28. The inner end portion of the intermediate piston 28 is in contact with the outer peripheral side of the upper end portion of the arm 24. The load adding portion 27 causes the roller support portion 20 to swing around the eccentric shaft 23 by moving the intermediate piston 28 in the longitudinal direction by the hydraulic load portion 29.

The crushing roller 13 swings around the eccentric shaft 23 by the hydraulic load portion 29, and the outer peripheral surface thereof is pressed against the crushing surface 12 c of the crushing table 12, thereby rotating around the rotation shaft 21.
The protrusion 25 abuts against the stopper 30 when the roller support 20 swings to a certain position around the eccentric shaft 23.

  The stopper 30 functions as a limiting member that limits the amount of movement of the crushing roller 13 in the direction of pressing the crushing table 12. The stopper 30 is a screw member in which a male screw is carved on the outer peripheral surface, and is screwed with a female screw carved on the inner circumference of the holding portion 31 attached so as to penetrate the housing 11. The stopper 30 can be rotated manually with a dedicated special tool. Thereby, the relative position of the grinding roller 13 with respect to the grinding table 12 when it is closest to the grinding table 12 can be adjusted.

As shown in FIG. 3, a pair of bearing devices 50 are attached to both ends of the eccentric shaft 23 of the roller support portion 20 in the central axis X direction. The bearing device 50 is a substantially cylindrical device disposed coaxially with the central axis X of the eccentric shaft 23.
Although only the bearing device 50 attached to one end portion of the eccentric shaft 23 is shown in FIG. 3, the bearing device 50 is also attached to the other end portion of the eccentric shaft 23. As shown in FIG. 3, the bearing device 50 is fixed to the housing 11 by fastening bolts 60. Although only one fastening bolt 60 is shown in FIG. 3, a plurality of fastening bolts 60 are provided at a plurality of locations around the central axis X.

  As shown in FIG. 3, the bearing device 50 includes a bush 51 (bearing member), an end cup 52 (holding member), a bushing retainer 53 (fixing member), a lip seal 54 (seal part), a seal 55, An annular plate 56, a fastening bolt 57, a lubricating oil supply unit 58, and a lubricating oil discharge unit 59 are provided.

  The eccentric shaft 23 supported by the bearing device 50 includes a shaft main body 23a and a cylindrical sleeve 23b attached to the outer peripheral surface of the shaft main body 23a. As a material for the sleeve 23b, it is desirable to use a high-carbon chromium bearing steel having high wear resistance. For example, it is desirable to use a Rockwell hardness of 50 to 65. More preferably, the Rockwell hardness is 55 to 65. As the material of the sleeve 23b, the higher the Rockwell hardness, the higher the wear resistance. However, the material becomes expensive and the amount of wear of the bush 51 increases due to sliding with the bush 51. Hardness is preferred.

  The sleeve 23b is fixed to the shaft body 23a by shrink fitting. Therefore, the sleeve 23b is inserted into the shaft main body 23a in a state where the inner diameter is increased by heating, and is fixed to the shaft main body 23a by being cooled and reduced in inner diameter.

  Since the sleeve 23b is fixed to the shaft main body 23a by shrink fitting, there is an advantage that the replacement is easier than the case where the sleeve 23b is fixed by welding or other methods. The sleeve 23b prevents the shaft body 23a from being worn. When the sleeve 23b is replaced at a maintenance timing or the like, the sleeve 23b to be replaced is cut in the direction of the central axis X and removed from the eccentric shaft 23. Thereafter, a new sleeve 23b is fixed and fixed to the shaft body 23a by shrink fitting.

The bush 51 is a cylindrical member that has an inner peripheral surface that supports the outer peripheral surface of the sleeve 23 b of the eccentric shaft 23 and extends along the central axis X.
The end cup 52 is a substantially cylindrical member that accommodates the end of the eccentric shaft 23 and to which the bush 51 is attached to the inner peripheral surface. The bush 51 is capable of processing a groove for distributing lubricating oil, which will be described later, and needs to withstand abrasion by sliding friction with the sleeve 23b.
As a material of the bush 51, for example, it is desirable to use a steel pipe for machine structure, a high-strength brass casting, or the like.

  The bushing retainer 53 is a member attached to one end of the end cup 52 on the side of the housing inner / outer space SA in the central axis X direction. The bushing retainer 53 is an annular member that fixes the position of the bush 51 in the central axis X direction by pressing the end surface of the bush 51 toward the housing outer space SB.

The bushing retainer 53 slides in contact with the thrust plate 70 when the thrust plate 70 attached to the shaft main body 23 a of the eccentric shaft 23 rotates around the central axis X as the eccentric shaft 23 rotates.
The diameter of the inner peripheral surface of the thrust plate 70 is larger than the diameter of the outer peripheral surface of the sleeve 23b. This is because the thrust plate 70 can be moved along the outer peripheral surface of the sleeve 23b when maintaining the bearing device 50 and the like.

  The lip seal 54 is an annular member that is disposed between the inner peripheral surface of the bushing retainer 53 and the outer peripheral surface of the sleeve 23b of the eccentric shaft 23 and has a lip at the sliding contact position. The lip seal 54 blocks between the housing inner / outer space SA and the inner space SP (lubricating oil space) between the outer peripheral surface of the sleeve 23 b of the eccentric shaft 23. The lip seal 54 is made of, for example, fluorine rubber.

FIG. 4 is an enlarged view of a main part in which the vicinity of the lip seal 54 shown in FIG. 3 is enlarged. As shown in FIG. 4, the lip seal 54 includes a first lip seal 54a and a second lip seal 54b.
The first lip seal 54a has the first lip 54c arranged in a direction to suppress the leakage of the lubricating oil from the internal space SP where the lubricating oil exists to the housing internal / external space SA. When the first lip 54c is pressed in the radial direction toward the sleeve 23b by an elastic force, a seal region is formed at a contact position between the first lip 54c and the sleeve 23b. Due to this seal region, leakage of the lubricating oil from the internal space SP to the housing internal / external space SA is suppressed.

  The second lip seal 54b is configured such that the second lip 54d is arranged in a direction that suppresses intrusion of foreign matters such as pulverized coal from the housing inner / outer space SA to the inner space SP. When the second lip 54d is pressed in the radial direction toward the sleeve 23b by the elastic force, a seal region is formed at a contact position between the second lip 54d and the sleeve 23b. Due to this seal region, intrusion of foreign matter such as pulverized coal from the housing inner / outer space SA to the inner space SP is suppressed.

  As shown in FIG. 4, the first lip seal 54a is disposed closer to the bush 51 along the central axis X than the second lip seal 54b. The first lip seal 54a and the second lip seal 54b are arranged so that the first lip 54c and the second lip 54d face oppositely along the central axis X and are symmetric in the direction along the central axis X. Has been. In the present embodiment, the first lip seal 54a and the second lip seal 54b have the same shape and are made of the same material. For this reason, it is preferable because the types of parts of the first lip seal 54a and the second lip seal 54b can be reduced and the number of types of steel pipe parts for maintenance can be reduced. Further, according to the use environment, the shape and size of the first lip seal 54a and the second lip seal 54b may be individually selected so that each function can be further ensured.

  Here, the contact position (seal area) between the second lip 54d and the sleeve 23b will be described. As shown in FIG. 4, the contact position between the second lip 54d and the sleeve 23b is close to the end of the sleeve 23b in the direction of the central axis X. The term “end portion” as used herein refers to an end portion of the outer peripheral surface of the sleeve 23b that has the same diameter as the outer peripheral surface of the sleeve 23b at the contact position between the second lip 54d and the sleeve 23b and is effective as a contact position.

As shown in FIG. 4, the distance in the central axis X direction between the end portion of the outer peripheral surface of the sleeve 23b and the end portion of the second lip 54d is W. This distance W is called cost.
The distance in the central axis X direction between the end of the second lip seal 54b and the end of the second lip 54d is A. Further, the distance in the central axis X direction from the end of the bushing retainer 53 that contacts the thrust plate 70 to the end of the second lip seal 54b is B. The distance in the central axis X direction from the end of the bushing retainer 53 that contacts the thrust plate 70 to the end of the outer peripheral surface of the sleeve 23b is C. The following formula (1) holds between W, A, B, and C. By using equation (1), in the adjustment at the time of assembly such as maintenance, the value of the allowance W can be easily calculated by measuring the distance A, the distance B, and the distance C.
W = (A + B) -C (1)

The value of the allowance W needs to be 0 or more. The reason why it is necessary to set it to 0 or more is that if it is not set to 0 or more, an appropriate seal region is formed at the contact position between the outer peripheral surface of the sleeve 23b and the second lip 54d, and the contact position is not effective.
Further, the end of the outer peripheral surface of the sleeve 23b and the end of the second lip 54d are preferably separated by 0.5 mm or more, more preferably 0.7 mm or more. That is, the value of the allowance W is preferably 0.5 mm or more, and more preferably 0.7 mm or more.

  The reason why the cutting allowance W is set to 0.5 mm or more is that it is empirically known that when it is less than 0.5 mm, it may become 0 or less due to secular change. Therefore, it is more preferable that the value of the allowance W is 0.7 mm or more with a margin. However, if the value of the allowance W is excessively increased, the overall size of the apparatus and the size of replacement parts are increased.

  A lip seal 54 and a liner 80, which is an annular plate member, are accommodated in a stepped portion 53a formed on the inner peripheral side of the bushing retainer 53. As shown in FIG. 4, the bush 51, the lip seal 54, the liner 80, and the bushing retainer 53 are arranged along the central axis X in contact with each other in this order.

  The value of the allowance W is adjusted by the thickness of the liner 80 inserted between the end portion of the second lip seal 54 b and the stepped portion 53 a of the bushing retainer 53. As shown in FIG. 4, the value of the distance B changes by adjusting the thickness of the liner 80. That is, when the thickness of the liner 80 is increased, the value of the allowance W increases, and when the thickness of the liner 80 is decreased, the value of the allowance W decreases. By preparing in advance a plurality of types of liners 80 having different thicknesses and appropriately adjusting the thickness of the liner 80, the value of the allowance W can be adjusted to an appropriate value.

  By doing so, the bushing retainer 53 moves in the central axis X direction by sliding between the bushing retainer 53 and the thrust plate 70, and accordingly, the lip seal 54 moves toward the thrust plate 70 along the central axis X direction. Even when moving, the moving distance should be less than a predetermined distance (0.5 mm if the allowance W is 0.5 mm or more, 0.7 mm if the allowance W is 0.7 mm or more). For example, the end portion of the second lip 54d does not reach the end portion of the outer peripheral surface of the sleeve 23b, and an appropriate seal region is formed and maintained at the contact position between the outer peripheral surface of the sleeve 23b and the second lip 54d. Therefore, infiltration of pulverized coal (foreign matter) from the housing internal / external space SA to the internal space SP by the second lip seal 54b can be appropriately suppressed.

The seal 55 is an annular member disposed between the inner peripheral surface of the end cup 52 and the outer peripheral surface of the shaft main body 23 a included in the eccentric shaft 23. The seal 55 blocks the space between the outer space outside the housing SB and the inner space SP. The seal 55 has a shape such as a lip seal, a gasket, or an O-ring, and is formed of, for example, fluorine rubber.
As shown in FIG. 3, the annular peripheral portion of the seal 55 is in contact with an annular plate 56 that is fastened to the end face of the end cup 52 by fastening bolts 57 to form a seal region.

  The lubricating oil supply unit 58 supplies lubricating oil such as grease supplied from the outside to the internal space SP. The lubricant supply unit 58 includes a lubricant supply port 58a and a lubricant supply channel 58b. The lubricating oil supply port 58a is connected to a lubricating oil supply hose (not shown) through which lubricating oil pumped from a lubricating oil pump (not shown) is circulated.

The lubricating oil flowing in from the lubricating oil supply port 58a is supplied to the internal space SP through the lubricating oil supply channel 58b and the lubricating oil supply hole 51a provided in the outer peripheral surface of the bush 51.
When lubricating oil is not supplied, the lubricating oil supply port 58a may be plugged with a plug or the like. The lubricating oil supply port 58a may be provided with a check valve mechanism so that the lubricating oil supplied to the lubricating oil supply channel 58b does not flow out of the lubricating oil supply port 58a.

The lubricating oil discharger 59 collects the lubricating oil flowing out from the internal space SP and discharges the collected lubricating oil to the outside. The lubricating oil discharge part 59 has a lubricating oil discharge port 59a, a lubricating oil discharge flow path 59b, and a lubricating oil recovery part 59c.
The lubricating oil recovery part 59 c is a space for recovering the lubricating oil in the internal space SP that flows out from the end of the bush 51. The lubricating oil recovered by the lubricating oil recovery part 59c is guided to the lubricating oil discharge port 59a through the lubricating oil discharge channel 59b.

When the lubricating oil is not discharged to the outside, the lubricating oil discharge port 59a may be plugged with a plug or the like. Further, the lubricating oil discharge port 59a has a flow state in which the lubricating oil flows out from the lubricating oil discharge channel 59b to the outer space outside the housing SB, and a seal that does not flow the lubricating oil from the lubricating oil discharge channel 59b to the outer space outside the housing SB. It has a function to switch between stopped states.
The lubricating oil discharge port 59a is in a flow state when the lubricating oil collected by the lubricating oil collecting portion 59c is allowed to flow out to the outer space outside the housing SB, and the lubricating oil collected by the lubricating oil collecting portion 59c is placed outside the outer space outside the housing. When not letting it flow into SB, it is in a sealed state.

  Although various properties can be used as the lubricating oil, it is desirable to use, for example, a material excellent in load bearing performance, greasing performance, and heat resistance. Considering the greasing property, for example, it is desirable to use a lubricating oil having a consistency of 310 to 340 at room temperature (25 ° C.).

Next, the first annular groove 91, the second annular groove 92, and the spiral groove 93 formed on the inner peripheral surface of the bush 51 will be described with reference to FIGS.
As shown in FIGS. 5 and 6, the bush 51 includes a first annular groove 91 formed on the inner peripheral surface 51 b on the one end side of the bush 51 along the central axis X, and a bush 51 along the central axis X. The second annular groove 92 formed on the inner peripheral surface 51b on the other end side of the first spiral groove 93 and the spiral groove 93 (93a, 93a formed on the inner peripheral surface 51b between the first annular groove 91 and the second annular groove 92). 93b, 93c). As a cross-sectional shape of these grooves, for example, a semicircular shape can be adopted.

  The cross-sectional shape of the groove need not be limited to a semicircular shape, and may be a rectangular cross-sectional shape or a semi-elliptical cross-sectional shape. In the present embodiment, groove processing is easy by using the semicircular cross-sectional shape, and design management is easy because the groove cross-sectional area can be set by setting the groove width.

  In the present embodiment, one end of the bush 51 (the side where the first annular groove 91 is disposed) is closer to the crushing roller 13 than the other end of the bush 51 (the side where the second annular groove 92 is disposed). Located nearby. In the present embodiment, one end of the bush 51 and the lip seal 54 are disposed in the housing inner / outer space SA including the grinding roller 13. The other end of the bush 51 and the seal 55 are disposed in the outer housing outer space SB away from the grinding roller 13.

  The first annular groove 91 is an endless groove formed without interruption around the central axis X. The second annular groove 92 is an endless groove formed without interruption around the central axis X. The positions of the first annular groove 91 and the second annular groove 92 along the central axis X remain constant in any phase around the central axis X.

The spiral groove 93 has one and a half circumferences around the central axis X (at 540 ° around the central axis X) from one end connected to the first annular groove 91 to the other end connected to the second annular groove 92. It is formed on the inner peripheral surface 51b so as to turn over the phase change.
The range in which the spiral groove 93 turns around the central axis X is not limited to one and a half rounds shown in FIGS. For example, center axis X such as one revolution (360 ° phase change around central axis X), two rounds (720 ° phase change around central axis X), half circumference (180 ° phase change around central axis X), etc. The spiral groove 93 may be formed so as to turn at least a part of the periphery of the.

  The spiral groove 93 includes a first spiral groove 93a, a second spiral groove 93b, and a third spiral groove 93c. As shown in the development view of the bush 51 shown in FIG. 6, the extending directions of the first spiral groove 93a, the second spiral groove 93b, and the third spiral groove 93c are the same direction. Further, the intervals of the first spiral groove 93a, the second spiral groove 93b, and the third spiral groove 93c are constant.

  As shown in FIG. 6, one end of the first spiral groove 93a is connected to the portion P1 of the first annular groove 91, and the other end of the first spiral groove 93a is connected to the portion P2 of the second annular groove 92. . One end of the second spiral groove 93b is connected to the portion P3 of the first annular groove 91, and the other end of the second spiral groove 93b is connected to the portion P4 of the second annular groove 92. One end of the third spiral groove 93c is connected to the portion P5 of the first annular groove 91, and the other end of the third spiral groove 93c is connected to the portion P6 of the second annular groove 92.

  The portion P1, the portion P3, and the portion P5 are different portions of the first annular groove 91, respectively. The portion P2, the portion P4, and the portion P6 are different portions of the second annular groove 92, respectively. In the present embodiment, the lubricating oil supply hole 51a is provided in the portion P1.

  The phase intervals between the portion P1, the portion P3, and the portion P5 around the central axis X are 120 ° constant intervals, respectively. Similarly, the phase intervals of the portion P2, the portion P4, and the portion P6 around the central axis X are 120 ° constant intervals, respectively.

As shown in FIG. 6, the groove width W <b> 1 of the first annular groove 91, the groove width W <b> 2 of the second annular groove 92, and the groove width Wr of the spiral groove 93 are represented by the following expression (2). ing.
Wr <W2 <W1 (2)
That is, the groove width W2 of the second annular groove 92 is wider than the groove width Wr of the spiral groove 93, and the groove width W1 of the first annular groove 91 is wider than the groove width W2 of the second annular groove 92.
Various grooves between the end of the second annular groove 92 on the other end side of the bush 51 (the left end of the second annular groove 92 in FIG. 6) and the other end of the bush 51 of the second annular groove 92 are also provided. The width W3, which is a region without any gap, is narrower than the groove width W2 of the second annular groove 92.
As specific examples of the groove widths W1, W2, Wr, and width W3, for example, 18 mm, 12 mm, 6 mm, and 7 mm can be employed.

Next, a lubricating oil replacement method for the bearing device 50 will be described with reference to FIGS. 5 and 6.
In the bearing device 50 of the present embodiment, the bushing retainer 53 is present in the housing internal / external space SA, which is the interior of the housing 11 where the pulverizing roller 13 is present and pulverized coal is present. When the eccentric shaft 23 rotates around the central axis X, the contact portion between the bushing retainer 53 and the thrust plate 70 slides. Therefore, even if a seal region is provided in this contact portion, pulverized coal or the like is provided via this contact portion. May be introduced to the inner peripheral side of the bushing retainer 53.

  Since the contact portion of the bearing device 50 according to the present embodiment includes the lip seal 54, the foreign matter guided to the inner peripheral side of the bushing retainer 53 is prevented from entering the internal space SP. However, when the operation is continued for a long time, there are a small number of foreign substances that enter the internal space SP beyond the lip seal 54. When these foreign substances are accumulated, the sleeve 23b and the bush fixed and fixed to the eccentric shaft 23 are fixed. There is a possibility that much wear occurs in 51.

  In the bearing device 50 of the present embodiment, the lubricating oil in the internal space SP can be replaced with new lubricating oil by the following lubricating oil replacement method, so that the sleeve 23b and the bush 51 are often worn. Can be prevented.

  When replacing the lubricating oil in the internal space SP, the operator connects a lubricating oil supply hose (not shown) connected to a lubricating oil pump (not shown) to the lubricating oil supply port 58a. Further, the operator switches the lubricating oil discharge port 59a from the sealed state to a flow state in which the lubricating oil flows out from the lubricating oil discharge channel 59b to the outer space outside the housing SB.

Thereafter, the worker starts driving the lubricating oil pump. The lubricant pump pumps the lubricant through a lubricant supply hose and supplies it to the lubricant supply port 58a.
The lubricating oil supply channel 58b supplies the lubricating oil flowing in from the lubricating oil supply port 58a to the first annular groove 91 through the lubricating oil supply hole 51a (lubricating oil supply step).

  The first annular groove 91 supplies the lubricating oil flowing in through the lubricating oil supply hole 51a to one end portions of the first spiral groove 93a, the second spiral groove 93b, and the third spiral groove 93c. The lubricating oil supplied from the position P1 to the first spiral groove 93a flows through the first spiral groove 93a and is supplied from the position P2 to the second annular groove 92.

The lubricating oil supplied from the position P3 to the second spiral groove 93b flows through the second spiral groove 93b and is supplied from the position P4 to the second annular groove 92. The lubricating oil supplied from the position P5 to the third spiral groove 93c flows through the third spiral groove 93c and is supplied from the position P6 to the second annular groove 92.
In this way, the lubricating oil is circulated from the first annular groove 91 to the second annular groove 92 via the helical groove 93 (lubricating oil distribution step).
On the inner surface of the bush 51, the lubricating oil is supplied by branching from the first annular groove 91 to the plurality of spiral grooves 93 of the first spiral groove 93a, the second spiral groove 93b, and the third spiral groove 93c. The lubricating oil is supplied almost uniformly over the entire sliding surface between the bushes 51.

  The lubricating oil that has flowed into the second annular groove 92 from each of the other end portions of the first spiral groove 93a, the second spiral groove 93b, and the third spiral groove 93c along the central axis X (see FIG. The left end in FIG. The amount of lubricating oil flowing out from the other end of the bush 51 is an amount corresponding to the pressure of the lubricating oil in the second annular groove 92.

  3 recovers the lubricating oil flowing out from the other end of the bush 51 and supplies it to the lubricating oil discharge passage 59b. Since the lubricating oil discharge port 59a is in a circulating state, the lubricating oil supplied to the lubricating oil discharge flow path 59b is discharged to the outer space outside the housing SB (lubricating oil discharging step).

  The operator stops driving the lubricating oil pump when the lubricating oil supplied to the lubricating oil supply port 58a reaches a predetermined amount (for example, an amount sufficient to replace the lubricating oil in the internal space SP). Further, the operator may confirm the state (color, etc.) of the lubricating oil discharged from the lubricating oil discharge port 59a, and stop the driving of the lubricating oil pump at an appropriate timing.

The operation and effect of the bearing device 50 according to the present embodiment described above will be described.
According to the bearing device 50 of the present embodiment, the lubricating oil supplied from the outside is supplied to the first annular groove 91 formed in the inner peripheral surface 51b of the bush 51, and one end of the first annular groove 91 is provided. It flows into the spiral groove 93 to be connected.

  The lubricating oil flowing into the spiral groove 93 flows into the second annular groove 92 from the other end of the spiral groove 93 after turning the inner peripheral surface 51b of the bush 51 around the central axis X. The lubricating oil that has flowed into the second annular groove 92 flows out from the other end of the bush 51, is collected by the lubricating oil discharge portion 59, and is discharged to the outside by the lubricating oil discharge portion 59.

  Thus, according to the bearing device 50 of the present embodiment, the first annular groove 91, the spiral groove 93, and the second annular groove formed on the inner peripheral surface 51b of the bearing device 50 by supplying the lubricating oil from the outside. The lubricating oil present in the groove 92 is discharged to the outside by the lubricating oil discharger 59 and is replaced with new lubricating oil.

  Therefore, even if the fine particles enter the lubricating oil and enter the portion where the eccentric shaft 23 and the bearing device 50 that supports it slide, the fine particles that have entered with the lubricating oil are discharged. It is possible to prevent a problem that the lubricating oil is deteriorated and the sleeve 23b and the bush 51 are often worn.

In the bearing device 50 of the present embodiment, the groove width W2 of the second annular groove 92 is wider than the groove width Wr of the spiral groove 93, and the groove width of the first annular groove 91 is larger than the groove width W2 of the second annular groove 92. W1 is wide.
Since the groove width Wr of the spiral groove 93 is set narrower than the groove width W1 of the first annular groove 91, the flow path resistance of the spiral groove 93 is increased, and the plurality of spiral grooves from the first annular groove 91 are increased. The branching of the lubricating oil to 93 (first spiral groove 93a, second spiral groove 93b, third spiral groove 93c) becomes uniform.

Since the groove width W2 of the second annular groove 92 is wider than the groove width Wr of the spiral groove 93, when the lubricating oil flowing into the spiral groove 93 flows out of the spiral groove 93, it merges and flows into the second annular groove 92. Easy . For wider groove width W1 of the first annular groove 91 than the groove width W2 of the second annular groove 92, easy to increase the pressure of the lubricating oil in the second annular groove 92, the outlet is the spiral groove 93 of each helical groove 93 Since there is a flow path resistance than the inlet of, the branch to each spiral groove 93 becomes uniform. In addition, since the flow resistance of each spiral groove 93 and the second annular groove 92 is provided to provide resistance to the outflow of the lubricating oil, the lubricating oil can be appropriately discharged from the second annular groove 92. Therefore, the replaceability of the lubricating oil in the bearing device 50 can be improved.

  In the present embodiment, the groove cross-sectional area can be set by setting the groove widths W1, W2, and Wr by setting the cross-sectional shape of the groove to be a semicircular shape. Therefore, “Wr <W2 <W1”, which is the relationship shown in Expression (2), can be actually replaced with the size relationship of the groove cross-sectional area. That is, the groove sectional area of the second annular groove 92 is larger than the groove sectional area of the spiral groove 93, and the groove sectional area of the first annular groove 91 is larger than the groove sectional area of the second annular groove 92.

In the bearing device 50 of the present embodiment, the width W3, which is a region without various grooves between the end of the second annular groove 92 on the other end of the bush 51 and the other end of the bush 51, is the second width groove 3. It is narrower than the groove width W <b> 2 of the annular groove 92.
In this way, the presence of the width W3 provides an appropriate flow resistance without taking up more space than the groove width W2 of the second annular groove 92, so that the spiral groove 93 lubricates the second annular groove 92. it is possible to merge the oil. In addition, since the width W3 is narrow and an appropriate flow path resistance is obtained, the speed at which the lubricating oil flows from the second annular groove 92 to the other end of the bush 51 is reduced, and the lubricating oil collecting portion 59c makes it easy to collect the lubricating oil. . Therefore, it becomes easy to discharge the lubricating oil to the external space SB outside the housing via the lubricating oil discharge channel 59b, and the replacement performance of the lubricating oil in the bearing device 50 can be further improved.

  According to the bearing device 50 of the present embodiment, the bush 51 is attached to the inner peripheral surface of the end cup 52 that accommodates the end of the eccentric shaft 23. The position of the bush 51 in the direction of the central axis X is fixed by an annular bushing retainer 53. The inner space SP and the inner space SP are blocked by a lip seal 54 disposed between the inner peripheral surface of the bushing retainer 53 and the outer peripheral surface of the sleeve 23b.

  By arranging the first lip seal 54a and the second lip seal 54b included in the lip seal 54 back to back, the first lip 54c of the first lip seal 54a disposed on the bush 51 side is moved from the internal space SP into the housing. The leakage of the lubricating oil to the external space SA is suppressed, and the second lip 54d of the second lip seal 54b suppresses the entry of foreign matter from the housing internal / external space SA to the internal space SP.

  Therefore, according to the present embodiment, it is possible to appropriately suppress the leakage of the lubricating oil from the internal space SP to the external space SA in the housing and the entry of foreign matter from the external space SA in the housing to the internal space SP. .

In the present embodiment, the first lip seal 54a and the second lip seal 54b have the same shape and are made of the same material.
By doing so, lubrication from the internal space SP to the external space SA in the housing can be achieved with a relatively simple configuration in which a pair of lip seals having the same shape and the same material and having one type of lip seal facing the front and back are arranged. Oil leakage and entry of foreign matter from the housing internal / external space SA into the internal space SP can be appropriately suppressed. For this reason, the number of parts of the first lip seal 54a and the second lip seal 54b is reduced, and the number of types of replacement parts for maintenance can be reduced, which is preferable.

  In the present embodiment, the eccentric shaft 23 has a shaft main body 23a and a cylindrical sleeve 23b attached to the outer peripheral surface of the shaft main body 23a, and the bush 51 and the lip seal 54 are in contact with the outer peripheral surface of the sleeve 23b. The end of the outer peripheral surface of the sleeve 23b and the end of the second lip 54d are separated by a predetermined distance or more.

  By doing so, when the bushing retainer 53 and the thrust plate 70 slide due to secular change or the like, the bushing retainer 53 moves in the central axis X direction, and accordingly, the lip seal 54 moves in the central axis X direction. Even so, if the moving distance is less than the predetermined distance, the end portion of the second lip 54d does not reach the end portion of the outer peripheral surface of the sleeve 23b, so that an appropriate sealing region can be formed and maintained. Accordingly, it is possible to appropriately suppress the entry of foreign matter from the housing inner / outer space SA into the inner space SP by the second lip 54d.

[Other Embodiments]
In the above description, when replacing the lubricating oil, the operator connects the lubricating oil supply port 58a and the lubricating oil pump, and the operator switches the lubricating oil discharge port 59a from the sealed state to the distribution state. However, other embodiments may be used.
For example, the lubricating oil supply port 58a and the lubricating oil pump may be always connected, and the lubricating oil discharge port 59a may be kept in a constantly flowing state. In this case, the lubricating oil pump may be always driven to replace the lubricating oil at all times. Lubricating oil replacement may be performed while removing a foreign substance mixed by installing a filter in the lubricating oil pump inlet or outlet. Alternatively, the lubricating oil pump may be periodically driven to periodically replace the lubricating oil.

10 Solid fuel pulverizer (pulverizer)
11 Housing 12 Crushing table 13 Crushing roller 23 Eccentric shaft (shaft member)
23a Shaft body 23b Sleeve 50 Bearing device 51 Bush (Bearing member)
51a Lubricating oil supply hole 52 End cup (holding member)
53 Bushing retainer (fixing member)
53a Step part 54 Lip seal (seal part)
54a First lip seal (first seal member)
54b Second lip seal (second seal member)
54c 1st lip 54d 2nd lip 58 Lubricating oil supply part 59 Lubricating oil discharge part 70 Thrust plate (thrust bearing)
80 Liner 91 First annular groove 92 Second annular groove 93 Spiral groove SA Internal space SB External space SP External space SP Internal space (lubricant space)
W Spare allowance X Center axis

Claims (8)

A grinding table,
A crushing roller for crushing solid fuel with the crushing table;
A shaft member for supporting the grinding roller;
A bearing portion having an inner peripheral surface that supports the outer peripheral surface of the shaft member;
The bearing portion is
A cylindrical bearing member extending along the central axis;
A lubricating oil supply section for supplying lubricating oil supplied from the outside to a lubricating oil space between the outer peripheral surface of the shaft member and the inner peripheral surface of the bearing member;
A lubricating oil discharge part for recovering the lubricating oil flowing out of the lubricating oil space and discharging the recovered lubricating oil to the outside;
The lubricating oil discharge portion has a lubricating oil discharge port for discharging the recovered lubricating oil to the outside, and the lubricating oil discharge port is in a flow state for allowing the recovered lubricating oil to flow out to the outside and the recovery to the outside With a function to switch the sealed state that does not allow the lubricant to flow out,
The bearing member is
A first annular groove formed in the inner peripheral surface on one end side of the bearing member along the central axis;
A second annular groove formed in the inner peripheral surface on the other end side of the bearing member along the central axis;
A spiral formed on the inner peripheral surface so as to turn at least part of the periphery of the central axis from one end connected to the first annular groove toward the other end connected to the second annular groove. Having a groove,
The lubricating oil supply unit supplies the lubricating oil to the first annular groove;
The lubricating oil discharge portion discharges the lubricating oil flowing out from the other end portion of the bearing member through the second annular groove to the outside ,
The crushing roller rotates about the shaft member, thereby changing the distance to the outer periphery of the crushing table,
A crusher in which the lubricating oil is grease .   The pulverization apparatus according to claim 1, wherein a cross-sectional area of the second annular groove is larger than a cross-sectional area of the spiral groove, and a cross-sectional area of the first annular groove is larger than a cross-sectional area of the second annular groove. The cross-sectional shape of the first annular groove, the cross-sectional shape of the second annular groove, and the cross-sectional shape of the spiral groove are semicircular,
The crusher according to claim 1, wherein the groove width of the second annular groove is wider than the groove width of the spiral groove, and the groove width of the first annular groove is wider than the groove width of the second annular groove.   The pulverization apparatus according to claim 3, wherein a width between an end of the second annular groove on the other end side of the bearing member and the other end of the bearing member is narrower than a groove width of the second annular groove. A substantially cylindrical holding member that accommodates an end of the shaft member and is attached to the inner peripheral surface of the bearing member;
An annular fixing member attached to one end portion of the holding member in the central axis direction and fixing the position of the bearing member in the central axis direction;
A seal portion disposed between the inner peripheral surface of the fixing member and the outer peripheral surface of the shaft member and blocking between the external space and the lubricating oil space;
The fixing member slides in contact with the thrust bearing when a thrust bearing attached to the shaft member rotates around the central axis as the shaft member rotates,
The seal portion includes a first seal member that suppresses leakage of lubricant oil from the lubricant oil space to the external space, and a second seal member that suppresses entry of foreign matter from the external space to the lubricant oil space. Have
5. The device according to claim 1, wherein the first seal member is disposed closer to the bearing member than the second seal member, and the first seal member and the second seal member are continuously disposed. The crushing apparatus according to item.   The first seal member and the second seal member have the same shape and are formed of the same material, and the first lip of the first seal member and the second lip of the second seal member are connected to the central axis. The pulverization apparatus according to claim 5, wherein the pulverization apparatus is arranged so as to be symmetrical in a direction along the line. The bearing portion has a cylindrical sleeve to which the shaft member is attached to a shaft main body and an outer peripheral surface of the shaft main body,
The bearing member and the seal portion are disposed at a position in contact with the outer peripheral surface of the sleeve,
The step portion formed on the inner peripheral side of the fixing member accommodates the seal portion and a liner that is an annular plate member,
The bearing member, the seal portion, the liner, and the fixing member are arranged in a state of contacting in this order along the central axis,
The pulverizing apparatus according to claim 6, wherein an end portion of the outer peripheral surface of the sleeve and an end portion of the second lip are separated by a predetermined distance or more depending on the thickness of the liner. A crushing table, a crushing roller that crushes solid fuel between the crushing table, a shaft member that supports the crushing roller, and a bearing portion that has an inner peripheral surface that supports the outer peripheral surface of the shaft member , the milling roller, by rotating around the shaft member, a bearing lubricating oil replacement method pulverizer distance change with respect to the outer peripheral portion of the grinding table,
The bearing portion collects lubricating oil flowing out from a lubricating oil space between a cylindrical bearing member extending along a central axis and an outer circumferential surface of the shaft member and an inner circumferential surface of the bearing member. A lubricating oil discharge portion for discharging the collected lubricating oil to the outside, the lubricating oil discharge portion having a lubricating oil discharge port for discharging the collected lubricating oil to the outside, and the lubricating oil discharge port to the outside A function of switching between a distribution state in which the recovered lubricating oil is allowed to flow out and a sealed state in which the recovered lubricating oil is not allowed to flow out to the outside,
The bearing member includes a first annular groove formed on the inner peripheral surface on one end side of the bearing member along the central axis, and the inner ring on the other end side of the bearing member along the central axis. A second annular groove formed on the peripheral surface, and at least part of the periphery of the central axis pivots from one end connected to the first annular groove to the other end connected to the second annular groove And a spiral groove formed on the inner peripheral surface,
A lubricating oil supply step of supplying lubricating oil supplied from the outside through the lubricating oil supply unit to the first annular groove;
A lubricating oil flow step for flowing the lubricating oil from the first annular groove to the second annular groove via the spiral groove;
A lubricant oil discharge step of discharging to the outside the lubricating oil said recovered from the lubricating oil discharge section with recovering the lubricating oil that flows out from the other end of the bearing member via the second annular groove,
Equipped with a,
The lubricating oil bearing lubricant replacement method of Ah Ru grinding device with grease.

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