JP2011106579A - Thrust bearing adjusting mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a thrust bearing adjusting mechanism easily and surely inhibiting rattling of a thrust bearing and preventing rattling of a shaft. <P>SOLUTION: The thrust bearing 7 is fixed to the outer end face 6 of a stand body 3, the end face of a fastening nut 9 screwed to the outer periphery of the shaft 5 is made to abut on the outer end face of the thrust bearing 7, and a whirl-stop flange 10 integrally fixed to the shaft 5 is provided on the outer end face side of the fastening nut 9. A through-hole is formed in the whirl-stop flange 10, a recess is formed in the fastening nut 9, and a positioning pin 11 is inserted into the recess via the through-hole for unification. The recess is formed in a plural number at equal intervals on the same circumference of the outer end face of the fastening nut 9, and the through-hole is formed in a plural number on the same circumference of the end face of the whirl-stop flange 10. An angular interval between the through-holes adjoining to each other is set at the angular interval except multiple numbers of an angular interval between the recesses adjoining to each other. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a thrust bearing adjusting mechanism that is provided in a device having a shaft rotatably supported by a thrust bearing between a pair of stand bodies fixed on a base, and for tightening and adjusting the thrust bearing. Is.

  For example, a slitter device or the like is known as a type of device that includes a shaft that is rotatably supported by a thrust bearing between a pair of stand bodies fixed on a base.

  The slitter device is supported by a pair of stand bodies fixed on a base at a distance from each other, and a thrust bearing and a journal bearing between them, and a plurality of ring-shaped blades are attached in the axial direction. It is roughly constituted by a pair of upper and lower shafts.

  Since the slitter device considers the structure of the device and the ease of maintenance, ball bearings are often used as thrust bearings and journal bearings that rotatably support the shaft.

  In the thrust bearing of the slitter device, the inner ring is fixed to the outer end surface of the stand body, and the end surface of the flange that is integrally fixed to the shaft is brought into contact with the outer end surface of the outer ring that is rotatable through a ball. Thus, the shaft is rotatably supported without moving in the thrust direction.

  The slitter device having the above-described configuration is configured such that a sheet-like material to be cut is inserted between the pair of upper and lower shafts, and a plurality of shearing forces are applied to the material to be cut by the blade attached to the shaft. Cut into strip-shaped material.

  By the way, in the slitter device, since a large stress in the thrust direction is constantly acting on the thrust bearing during operation, each part of the thrust bearing is worn by long-time operation. For this reason, the thrust bearing has a backlash in the thrust direction, and accordingly, the shaft also has a backlash in the thrust direction, and the accuracy of the width dimension of the belt-shaped material is deteriorated. was there.

  In order to solve this problem, as a conventional thrust bearing adjusting mechanism, a male screw part and a groove part are provided on the outer periphery of the end part of the shaft, and instead of the flange, an outer end surface of the outer ring of the thrust bearing is provided on the male screw part. A screwed bearing nut 21 shown in FIG. 6 is abutted, and a bearing washer 24 shown in FIG. 7 is provided on the outer end face side of the bearing nut 21.

  Here, the bearing nut 21 has four groove portions 22 formed at equal intervals on the outer peripheral portion, and a female screw portion 23 that is screwed with the male screw portion of the shaft on the inner peripheral portion.

  On the other hand, the bearing washer 24 has 18 teeth 25 formed at equal intervals on the outer peripheral portion, and one tooth 26 fitted into the groove portion of the shaft on the inner peripheral portion.

  The conventional thrust bearing adjusting mechanism having the above configuration rotates the bearing nut 21 screwed to the shaft in the tightening direction and presses the outer ring of the thrust bearing toward the inner ring side. Next, the tooth 26 on the inner periphery of the bearing washer 24 is fitted into the groove of the shaft at a position where the thrust bearing is free from rattling. Then, by appropriately selecting the outer peripheral teeth 25 at the position facing the groove portion 22 of the bearing nut 21, bending it toward the bearing nut 21, and inserting the groove into the groove portion 22 of the bearing nut 21, The rotation is suppressed, and the axial play of the shaft due to the play of the thrust bearing is suppressed.

  However, the conventional thrust bearing adjusting mechanism needs to remove the teeth 25 on the outer periphery of the bearing washer 24 fitted in the groove portion 22 of the bearing nut 21 every time the thrust bearing is tightened, which is troublesome. was there.

  In addition, when the outer peripheral teeth 25 of the bearing washer 24 once bent to fit into the groove portion 22 of the bearing nut 21 are bent again to fit into the groove portion 22 of the bearing nut 21, the outer peripheral teeth 25 are caused by brittle fracture. It may be damaged. For this reason, in many cases, it is necessary to replace the bearing washer 24 with a new one every time the thrust bearing is adjusted.

  Further, the conventional thrust bearing adjusting mechanism has no means for numerically managing the thrust bearing feed amount, which is how much the thrust bearing is tightened against the shakiness of the shaft. The above thrust bearing was tightened. For this reason, the bearing nut 21 is tightened too much in order to surely suppress the shakiness of the shaft in the thrust direction, and the thrust bearing generates heat and is damaged due to friction between the inner ring and outer ring of the thrust bearing and the ball. There was a problem.

  The present invention has been made to solve the problems of the prior art, and provides a thrust bearing adjustment mechanism that can easily and reliably suppress the rattling of the thrust bearing and suppress the shakiness of the shaft. It is to provide.

  In order to solve the above-mentioned problem, the thrust bearing adjusting mechanism according to claim 1 is provided in an apparatus including a shaft rotatably supported by a thrust bearing between a pair of stand bodies fixed on a base. In the thrust bearing adjusting mechanism for tightening and adjusting the thrust bearing in the thrust direction, the inner ring of the thrust bearing is fixed to the outer end surface of the stand body, and the outer ring outside the outer ring which is rotatable via the ball of the thrust bearing is fixed. An end face of a tightening nut screwed to the outer periphery of the shaft is brought into contact with the end face, and a non-rotating flange integrally fixed to the shaft is provided on the outer end face side of the tightening nut. A through hole is formed, and a concave portion is formed in the clamping nut so as to communicate with the through hole at an opposing position when the clamping nut rotates. The positioning pin is inserted into and integrated with the recess through the through hole, and a plurality of the recesses are formed at equal intervals on the same circumference of the outer end surface of the tightening nut. A plurality of the through holes are formed on the same circumference of the end face of the non-rotating flange, and an angular interval between the adjacent through holes excludes a multiple of an angular interval between the adjacent concave portions. It is characterized by being provided at angular intervals.

  According to a second aspect of the present invention, in the thrust bearing adjusting mechanism according to the first aspect, the through hole of the detent flange and the concave portion of the tightening nut can communicate with the outer periphery of the tightening nut while the tightening nut rotates once. The same number of scales as the combination is engraved at each angular interval where the through hole and the recess communicate with each other about the rotation axis of the tightening nut, and a mark serving as a reference for the scale is engraved on the outer periphery of the detent flange. It is characterized by having installed.

  According to the first aspect of the present invention, the inner ring of the thrust bearing is fixed to the outer end surface of the stand main body, and the outer ring of the outer ring, which is rotatable through the ball of the thrust bearing, is attached to the outer end surface of the shaft. By contacting the end face of the tightening nut screwed to the outer periphery, when each part of the thrust bearing is worn, the tightening nut screwed to the shaft is moved in the thrust direction, and the outer ring of the thrust bearing is moved. By pressing toward the inner ring side, rattling of the thrust bearing is suppressed.

  Then, by inserting the positioning pin into the recess of the tightening nut through the through hole of the non-rotating flange integrally fixed to the shaft, the positioning nut is prevented from rotating in the loosening direction. As a result, it is possible to reliably suppress the rattling of the thrust bearing, and accordingly, it is also possible to continue to suppress the shakiness of the shaft in the thrust direction. It is not necessary to replace parts such as a bearing washer every time the bearing is tightened and adjusted, and the maintenance cost can be reduced.

  In addition, the plurality of concave portions are formed at equal intervals on the same circumference of the outer end surface of the tightening nut, and the plurality of through holes are formed on the same circumference of the end surface of the non-rotating flange. Further, by rotating the tightening nut in the tightening direction, any one of the through holes and the recess can communicate with each other.

  By the way, if the angular interval between the adjacent through holes is a multiple of the angular interval between the adjacent concave portions, the through hole and the concave portion communicate with each other at each angular interval between the concave portions. .

  On the other hand, according to the present invention, since the angular interval between the adjacent through holes is provided at an angular interval excluding a multiple of the angular interval between the adjacent concave portions, a smaller angle is provided. Any one of the through holes and the recesses can communicate with each other at intervals, and the number of combinations in which the plurality of recesses and the plurality of through holes communicate with each other while the tightening nut is rotated is remarkably increased. As a result, it is possible to finely adjust the feed amount of the tightening nut.

  According to the second aspect of the present invention, there is provided a combination that allows the through hole of the detent flange and the recess of the tightening nut to communicate with each other on the outer periphery of the tightening nut while the tightening nut rotates once. The same number of scales are engraved at each angular interval where the through hole and the recess communicate with each other with the rotation axis of the tightening nut as the axis, and a mark serving as a reference for the scale is engraved on the outer periphery of the non-rotating flange. Therefore, it is possible to numerically manage the feed amount of the tightening nut with respect to the shakiness of the shaft by the scale and the mark. As a result, the feed amount of the tightening nut can be made moderate. As a result, it is possible to prevent the thrust bearing from being damaged and to reliably prevent the shaft from rattling. It becomes possible.

It is a longitudinal cross-sectional view which shows one Embodiment of the thrust bearing adjustment mechanism which concerns on this invention. It is a top view which shows the clamping nut of FIG. It is a top view which shows the rotation stop flange of FIG. FIG. 2 is a plan view showing a state in which the tightening nut of FIG. 1 is rotated at an angular interval of 3 degrees in the order of (a) to (d). It is a general view which shows the slitter apparatus to which FIG. 1 is applied. It is a top view which shows the bearing nut in the conventional thrust bearing adjustment mechanism. It is a top view which shows the bearing washer in the conventional thrust bearing adjustment mechanism.

1 to 5 show an embodiment in which a thrust bearing adjusting mechanism according to the present invention is applied to a slitter device.
First, as shown in FIG. 5, the slitter device includes a pair of stand bodies 2 and 3 fixed on the base 1 with a space therebetween, and a plurality of ring-shaped blades rotatably supported between them. It is roughly constituted by a pair of upper and lower shafts 5 attached with 4 in the axial direction.

  On the other hand, as shown in FIG. 1, the thrust bearing adjusting mechanism includes a thrust bearing 7 fixed to the outer end surface 6 of the stand body 3, a tightening nut 9 screwed with the male screw portion 8 of the shaft 5, a shaft 5 is constituted by a non-rotating flange 10 integrally fixed to 5 and a positioning pin 11.

  Here, the male screw portion 8 is formed on the outer periphery of the end portion of the shaft 5 protruding outward from the stand main body 3 side with a screw pitch of 2 mm, and the female screw portion 12 screwed with the male screw portion 8 is It is formed on the inner periphery of the tightening nut 9.

  Further, the thrust bearing 7 uses a ball bearing in the same manner as the slitter device of the prior art, and the inner ring 13 is fixed to the outer end surface 6 of the stand body 3 and can be rotated via the ball 14. When the end face of the tightening nut 9 is brought into contact with the outer end face of the shaft 15, the shaft 5 is rotatably supported without moving in the thrust direction.

  A bearing cover 16 is attached to the thrust bearing 7 radially outward from the outer end surface 6 of the stand body 3 toward the end surface of the tightening nut 9 so as to cover the thrust bearing 7. Intrusion of dust and the like is prevented.

  As shown in FIG. 2, the tightening nut 9 has a plurality (30 in the figure) of recesses 17 formed at equal intervals on the same circumference of the outer end surface. That is, the space between the adjacent recesses 17 is formed at an angular interval of 12 degrees with respect to the center.

  On the other hand, as shown in FIG. 3, the non-rotating flange 10 has a plurality of (four in the figure) through-holes 18 penetrating both end faces on the same circumference of the end face. The space is formed at an angular interval of 27 degrees with respect to the center.

  As a result, as shown in FIG. 4, the through-holes 18 extending from the upper side of the non-rotating flange 10 in the drawing to the center in the clockwise direction in FIG. As shown in a), any one of the through hole 18a and the recess 17 is communicated with each other. Then, between the through-hole 18b (the angular interval between the through-hole 18a is 27 degrees) and the concave portion 17 closest to the through-hole 18b in the tightening direction (the angular interval between the through-hole 18a is 24 degrees). The angular interval is 3 degrees. And between the through-hole 18c (the angular interval between the through-hole 18a is 54 degrees) and the concave portion 17 closest to the through-hole 18c in the tightening direction (the angular interval between the through-hole 18a is 48 degrees). The angular interval is 6 degrees. Further, between the through-hole 18d (the angular interval between the through-hole 18a is 81 degrees) and the recess 17 closest to the through-hole 18d in the tightening direction (the angular interval between the through-hole 18a is 72 degrees). The angular interval is 9 degrees.

  Therefore, when the tightening nut 9 is further rotated by 3 degrees in the tightening direction with respect to the center, as shown in FIG. 4B, the through hole 18b and the recess 17 communicate with each other. At this time, the through-hole 18c (the angular interval between the through-hole 18a is 54 degrees) and the concave portion 17 closest to the through-hole 18c in the tightening direction (the angular interval between the through-hole 18a is 51 degrees) and The angle interval between is 3 degrees. Further, between the through-hole 18d (the angular interval between the through-hole 18a is 81 degrees) and the recess 17 closest to the through-hole 18d in the tightening direction (the angular interval between the through-hole 18a is 75 degrees). The angular interval is 6 degrees.

  Further, when the tightening nut 9 is rotated by 3 degrees in the tightening direction with respect to the center, the through hole 18c and the recess 17 communicate with each other as shown in FIG. Further, between the through-hole 18d (the angular interval between the through-hole 18a is 81 degrees) and the concave portion 17 closest to the through-hole 18d in the tightening direction (the angular interval between the through-hole 18a is 78 degrees). The angular interval is 3 degrees.

  Further, when the tightening nut 9 is rotated 3 degrees in the tightening direction with respect to the center, as shown in FIG. 4D, the through hole 18d and the concave portion 17 have an angular interval of 81 between the through hole 18a. And communicate with each other. Then, the angular interval between the through hole 18a and the concave portion 17 closest to the through hole 18a in the tightening direction (the angular interval between the through hole 18a is 357 degrees) is 3 degrees.

  Further, when the tightening nut 9 is rotated 3 degrees in the tightening direction with respect to the center, as shown in FIG. 4A, the through hole 18a and the concave portion 17 communicate with each other again. Then, between the through-hole 18b (the angular interval between the through-hole 18a is 27 degrees) and the concave portion 17 closest to the through-hole 18a in the tightening direction (the angular interval between the through-hole 18a is 24 degrees). The angular interval is 3 degrees. And between the through-hole 18c (the angular interval between the through-hole 18a is 54 degrees) and the concave portion 17 closest to the through-hole 18c in the tightening direction (the angular interval between the through-hole 18a is 54 degrees). The angular interval is 6 degrees. Further, between the through-hole 18d (the angular interval between the through-hole 18a is 81 degrees) and the recess 17 closest to the through-hole 18d in the tightening direction (the angular interval between the through-hole 18a is 72 degrees). The angular interval is 9 degrees.

  That is, the recess 17 of the tightening nut 9 communicates with each other in the order of the through holes 18a, 18b, 18c, and 18d every time the tightening nut 9 is rotated by 3 degrees in the tightening direction with respect to the center.

  Therefore, in the present embodiment, 30 recesses 17 communicate with one through-hole 18 and four through-holes 18 are formed, so that the tightening nut 9 is rotated during one rotation of the tightening nut 9. There are a total of 120 combinations in which the nine concave portions 17 and the through-holes 18 of the non-rotating flange 10 can communicate with each other.

  On the other hand, on the outer periphery of the tightening nut 9, there are 120 scales, the number of which is the same as the number of combinations in which the concave portion 17 of the tightening nut 9 and the through hole 18 of the non-rotating flange 10 can communicate with each other while the tightening nut 9 rotates once. 19 is engraved at equal intervals every 3 degrees, and a mark 20 serving as a reference for the scale 19 is engraved on the outer periphery of the non-rotating flange 10.

  On the other hand, the positioning pin 11 is inserted into the recess 17 of the tightening nut 9 through the through hole 18 of the non-rotating flange 10.

  In the thrust bearing adjusting mechanism having the above-described configuration, first, the tightening nut 9 screwed with the shaft 5 is moved in the thrust direction, and the outer ring 15 of the thrust bearing 7 is pressed toward the inner ring 13 side. Suppresses rattling.

  Then, at the position where the thrust bearing 7 is free from rattling, the positioning pin 11 is inserted into a place where the through hole 18 of the non-rotating flange 10 and the recess 17 of the tightening nut 9 communicate with each other.

  That is, by inserting the positioning pin 11 into the concave portion 17 of the tightening nut 9 through the through hole 18 of the non-rotating flange 10 fixed to the shaft 5 integrally, the tightening nut 9 rotates in the loosening direction. Nothing will happen.

  As a result, it is possible to reliably suppress the rattling of the thrust bearing 7 and to suppress the rattling of the shaft 5 in the thrust direction accordingly. It is possible to prevent the accuracy of the deterioration. Further, it is not necessary to replace parts such as the bearing washer 24 every time the thrust bearing 7 is tightened and adjusted, and the maintenance cost can be reduced.

  Further, the angular interval (27 degrees) between the adjacent through holes 18 of the non-rotating flange 10 with respect to the rotation direction of the clamping nut 9 is set to the angular interval (12) between the concave portions 17 of the adjacent clamping nuts 9. Therefore, when the tightening nut 9 is rotated in the tightening direction, one of the through holes 18 and the recess 17 can be communicated with each other at every three degree angle interval. The number of combinations in which the 30 recesses 17 and the four through holes 18 communicate with each other while the 9 is rotated is remarkably increased to 120. As a result, the feed amount of the tightening nut 9 can be finely adjusted.

  Then, on the outer periphery of the tightening nut 9, 120 scales 19 of the same number as the combination in which the through-hole 18 of the non-rotating flange 10 and the recess 17 of the tightening nut 11 can communicate with each other while the tightening nut 9 rotates once, etc. Since the female screw portion 12 of the tightening nut 9 is provided with a screw pitch of 2 mm, the tightening nut 9 is 0.016 mm each time the scale 19 is moved by one scale. The number divided by) Rotate in the tightening direction and move in the thrust direction. Further, since a mark 20 serving as a reference of the scale 19 is engraved on the outer periphery of the non-rotating flange 10, the feed amount of the tightening nut 9 with respect to the shakiness of the shaft 5 is numerically determined by the scale 19 and the mark 20. Management is possible. As a result, the feed amount of the tightening nut 9 can be made moderate. As a result, it is possible to prevent the thrust bearing 7 from being damaged and to reliably prevent the shaft 5 from rattling. It becomes possible.

  The thrust bearing adjusting mechanism having the above-described configuration has been described only when the thrust bearing adjusting mechanism according to the present invention is applied to the slitter device. However, the thrust bearing adjusting mechanism is not limited to the slitter device, but a pair of stand bodies fixed on the base. Any device provided with a shaft rotatably supported by a thrust bearing can be applied.

DESCRIPTION OF SYMBOLS 1 Base 2 Stand main body 3 Stand main body 4 Cutlery 5 Axis 6 Outer end surface of stand main body 7 Thrust bearing 9 Tightening nut 10 Non-rotating flange 11 Positioning pin 12 Inner ring 14 Ball 15 Outer ring 17 Recessed part 18 Through hole 18a Through hole (0 degree angular interval) )
18b Through hole (angular interval 27 degrees)
18c Through-hole (angular spacing 54 degrees)
18d Through-hole (angular interval 81 degrees)
19 scales 20 marks

Claims (2)

In a thrust bearing adjustment mechanism that is provided in a device having a shaft rotatably supported by a thrust bearing between a pair of stand bodies fixed on a base, and tightens and adjusts the thrust bearing in the thrust direction.
The inner ring of the thrust bearing is fixed to the outer end face of the stand body, and the end face of the tightening nut screwed to the outer periphery of the shaft is abutted against the outer end face of the outer ring which is rotatable through the ball of the thrust bearing. A non-rotating flange integrally fixed to the shaft is formed on the outer end surface side of the tightening nut, a through hole is formed in the non-rotating flange, and the tightening nut is rotated when the tightening nut is rotated. A concave portion communicating with the through hole at the opposing position, and a positioning pin is inserted and integrated into the concave portion through the through hole.
In addition, a plurality of the recesses are formed at equal intervals on the same circumference of the outer end face of the tightening nut, and a plurality of the through holes are formed on the same circumference of the end face of the non-rotating flange. The thrust bearing adjusting mechanism, wherein the angular interval between the through holes is provided at an angular interval excluding a multiple of the angular interval between the adjacent recesses.   On the outer periphery of the tightening nut, the same number of scales as the combination in which the through-hole of the non-rotating flange and the recess of the tightening nut can communicate with each other while the tightening nut rotates once, with the rotation axis of the tightening nut as an axis. 2. The thrust bearing according to claim 1, wherein a mark serving as a reference for the scale is engraved on the outer periphery of the non-rotating flange, which is engraved at every angular interval at which the through hole and the recess communicate. Adjustment mechanism.

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