JP2015224726A - Bearing lock implement, shaft and bearing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bearing lock implement which is easy in attachment to a shaft, can effectively constrain the axial movement of a bearing, and is easy in processing.SOLUTION: A bearing lock implement 1 has a nut 2 which is screwed to a male screw part 10c protruded from a bearing 11 in a shaft 10, and fastened to a width face of the bearing 11 so as to abut thereon, and whirl-stop implements 3 which are engaged with whirl-stop recesses 4 formed at an outside diameter face the nut 2, and whirl-stop recesses 12 formed at an outside diameter face of the shaft 10, so as to regulate a mutual rotation of the shaft 10 and the nut 2. The whirl-stop recesses 4 of the nut are arranged in a plurality of pieces in a circumferential direction in an unequal distribution. For example, for the shaft with n pieces of the whirl-stop recesses 12 equally arranged in the circumferential direction, the number of the whirl-stop recesses 4 of the nut is configured to be n, and center opening angles at (n-1) of n positions between the whirl-stop recesses 4 of the nut are configured to be (360×(n+1)/n) degrees.

Description

  The present invention relates to a bearing lock that restrains axial movement of a bearing fitted to the outer periphery of the shaft, a shaft that restrains axial movement of the bearing fitted to the outer circumference by the bearing lock, and a bearing on the outer circumference of the shaft. The present invention relates to a bearing device fitted so as not to move in the axial direction.

  In order to prevent the bearing fitted to the outer periphery of the shaft from moving in the axial direction, it is widely practiced to lock the bearing by tightening a nut screwed into the male screw portion of the shaft so as to contact the width surface of the bearing. (For example, Patent Documents 1 and 2). In the bearing lock structure using this nut, it is necessary to regulate the mutual rotation of the shaft and the nut in order to prevent the nut from loosening. The rotation regulation includes a method using a washer and a method using a stopper.

  As shown in FIG. 11, a method using a washer includes a single inner peripheral protrusion 104a and a plurality of outer peripheral protrusions between a bearing 102 fitted to the outer periphery of the shaft 101 and a nut 103 screwed to the male screw portion 101a of the shaft 101. A washer 104 having 104b is interposed, and an inner peripheral protrusion 104a of the washer 104 is engaged with a groove-shaped detent recess 101b provided on the outer diameter surface of the male screw part 101a of the shaft 101, and a plurality of outer peripheral protrusions At least one of 104b is folded into and engaged with a groove-shaped detent recess 103a provided on the outer diameter surface of the nut 103, thereby restricting the mutual rotation of the shaft 101 and the nut 103.

  As shown in FIG. 12, the method using the clasp is to engage the rotation stopper 105 with each of the shaft rotation-preventing recess 101b and the nut rotation-preventing recess 103a, so that the shaft 101 and the nut 103 are engaged. Regulate mutual rotation. The rotation stopper 105 is fixed to the nut 103 with a bolt 106 or the like.

  In both of the method using the washer and the method using the stopper, the nut 103 for phase matching of the rotation stopper recesses 101b and 103a is provided by providing a plurality of rotation stopper recesses 101b and 103a on the shaft 101 and the nut 103, respectively. The amount of tightening is reduced. That is, when the nut 103 is tightened until it abuts against the width surface of the bearing 102, if the circumferential phase of the rotation-preventing recess 101b of the shaft 101 and the rotation-preventing recess 103a of the nut 103 do not match, the nut 103 Needs to be turned to the tightening side to match the circumferential phase of the anti-rotation recesses 101b and 103a. At that time, if a plurality of the rotation-preventing recesses 101b and 103a are provided, the angle at which the nut 103 is turned may be small. Conventionally, the shaft 101 and the plurality of anti-rotation recesses 101b and 103a of the nut 103 are both equally provided in the circumferential direction.

Utility Model Registration No. 3041291 JP 2001-208087 A

  As shown in FIG. 13 and FIG. 14, an example in which the rotation preventing recesses 101 b of the shaft 101 are evenly provided at three places and the rotation stopping recesses 103 a of the nut 103 are provided at even four places. Therefore, the tightening angle of the nut 103 will be considered. When the nut 103 is fastened to the bearing 102 (FIG. 12), the nut 103 is rotated by an angle α in the tightening direction A so that the rotation prevention recess 101b (1) and the nut 103 of the shaft 101 are rotated. The circumferential direction phase of the anti-rotation recess 103a (1) may be matched. On the other hand, in the state of FIG. 14, the nut 103 is rotated by an angle β (β> α) in the tightening direction A, so that the rotation preventing recess 101 b (2) of the shaft 101 and the rotation locking recess of the nut 103 are rotated. The circumferential phase of 103a (2) must be matched. That is, depending on the tightening position of the nut 103, the tightening angle of the nut 103 for phasing the rotation preventing recesses 101b and 103a may be increased.

  When the tightening angle of the nut 103 is large and the tightening amount is large, it is difficult to align the phases of the recesses 101b and 103a for rotation prevention. In particular, in the case of a large-sized product, since the tightening force of the nut 103 is large, the mounting of the bearing 102 becomes difficult when the tightening amount increases. Furthermore, if the tightening amount is excessive, there is a possibility of adversely affecting the male screw portion 101a of the shaft 101 and the screw thread of the nut 103.

  Conventionally, the amount of tightening of the nut 103 is excessively increased by increasing the number of the shaft rotation-preventing recesses 101b or increasing the number of the nut rotation-preventing recesses 103a as shown in FIG. I avoided it. The maximum tightening angle of the nut 103 in the case of FIG. 15 is 15 degrees. However, increasing the number of the shaft and nut detents 101b and 103a has a problem that the processing cost increases.

SUMMARY OF THE INVENTION An object of the present invention is to provide a bearing lock that can effectively restrain axial movement of a bearing fitted to the outer periphery of a shaft, can be easily attached to the shaft, and can be easily processed. .
Another object of the present invention is to provide a shaft that can effectively restrain the axial movement of a bearing fitted to the outer periphery of the shaft, can be easily attached to the shaft, and can be easily machined. It is to be.
Still another object of the present invention is to provide a bearing device that can effectively restrain axial movement of a bearing fitted to the outer periphery of a shaft, is easy to assemble, and is easy to process.

  The bearing lock device of the present invention is a bearing lock device that restrains axial movement of a bearing fitted to the outer periphery of the shaft, and is screwed into a male screw portion protruding from the bearing in the shaft, and the width surface of the bearing A nut that is tightened so as to be in contact with the nut, and a non-rotating recess provided on the outer diameter surface of the nut and a non-rotating recess provided on the outer diameter surface of the shaft, A rotation stopper for restricting the mutual rotation of the nuts, and a plurality of recesses for rotation prevention of the nut are provided in an uneven distribution in the circumferential direction.

  According to this configuration, the bearing that is fitted to the outer periphery of the shaft is constrained so that the bearing does not move in the axial direction by tightening the nut screwed into the male screw portion of the shaft so as to contact the width surface of the bearing. To do. Then, turn the nut in the tightening direction to match the circumferential phase of the shaft rotation-preventing recess and the nut rotation-prevention recess, and then turn the shaft rotation-prevention recess and the nut rotation-prevention recess respectively. Engage the detent. Thereby, the mutual rotation of the shaft and the nut is restricted, and the loosening of the nut is prevented. The reason for turning the nut in the tightening direction when phasing the shaft anti-rotation recess and the nut anti-rotation recess is to prevent loosening of the bearing by the nut.

  The number of nuts to prevent rotation of the nut is unevenly distributed in the circumferential direction, so that the amount of tightening of the nut for phase alignment can be achieved regardless of the circumferential phase relationship between the shaft and the nut. Can be reduced. If the tightening amount of the nut is small, the bearing can be easily attached to and detached from the shaft, and damage to the male screw portion of the shaft and the screw thread of the nut can be prevented. If the diameter of the shaft increases, the tightening amount increases even if the tightening angle is the same, so that the larger the bearing, the higher the effect.

  In addition, when the maximum tightening angle of the nut is the same, the non-rotating recesses of the nut are arranged more unevenly than the non-rotating recesses of the nut. The number can be reduced. Therefore, by arranging the recesses for preventing the rotation of the nuts in an uneven distribution, the processing of the nuts becomes easy and the manufacturing cost can be reduced.

In this invention, when there are n circumferentially spaced recesses on the shaft, the number of the recesses for the nuts is n, and the center of n locations between these nuts The center-to-center angle at the (n−1) locations of the inter-angle is preferably (360 × (n + 1) ÷ n ² ) degrees.

There are n counter-rotating recesses in the circumferential direction, and n counter-rotating recesses of n nuts are provided equally between the adjacent anti-rotation recesses of two adjacent shafts. The maximum tightening angle of the nut (assumed to be a “basic unevenly distributed nut”) is an angle obtained by dividing the total circumferential angle (360 degrees) by the square n ² of the number of recesses for preventing rotation of the nut, ie (360 ÷ n ² ) degrees. In other words, an n-numbered non-rotating recess for the nut has the same effect as an even-numbered n-numbered recess for the nut.
(360 × (n + 1) ÷ n ² ) degrees, which is the angle between the centers of the (n−1) places between the nut rotation stopper recesses, in other words, 360 degrees is the square of the number of nut rotation stopper recesses n It is obtained by adding 360 degrees to 360 degrees divided by ² (360 ÷ n ² ) and 360 degrees divided by the number n of the recesses for preventing rotation of the nut. In other words, compared with the basic uneven nut, the position of the recess for preventing rotation of each nut is shifted by (360 ÷ n) degrees, so the maximum tightening angle of the nut is (360 ÷ n ² ) degrees. There is no change. If the angle between the centers of the (n-1) locations between the nut rotation-preventing recesses is (360 × (n + 1) ÷ n ² ) degrees, the rotation-preventing recesses of each nut are distributed over the entire circumference. So the balance is good.

  Further, in the present invention, when the number of the recesses for preventing rotation of the shaft is equal to n in the circumferential direction, there are a plurality of recesses for preventing rotation of the nut, and all of them are (360 ÷ n) degrees. You may arrange | position within an angle range. The recesses for preventing rotation of the nuts may be evenly distributed or unevenly distributed within an angular range of (360 ÷ n) degrees.

Also in this case, the maximum tightening angle of the nut can be reduced. For example, when there are m number of recesses for preventing rotation of the nut, the maximum tightening angle of the nut is (360 ÷ (n × m)) degrees. When the nuts for preventing rotation of the nuts are evenly distributed within an angular range of (360 ÷ n) degrees and the number of recesses for preventing the rotation of the nuts is n, the above-mentioned basic uneven nuts are provided. The tightening angle is (360 ÷ n ² ) degrees.

  The shaft according to the present invention is a shaft in which a bearing is fitted to the outer periphery and the axial movement of the bearing is restricted by a bearing lock, and has a male screw portion protruding from the bearing, A non-rotating recess is provided on the radial surface, and the bearing lock member is provided on a nut that is screwed into the male screw portion and tightened so as to contact the width surface of the bearing, and an outer diameter surface of the nut. A non-rotating recess that engages with each of the non-rotating recess and the non-rotating recess of the shaft to restrict rotation of the nut, and the non-rotating recess of the shaft is unevenly distributed in the circumferential direction. It is characterized in that a plurality are provided.

  According to this configuration, the bearing that is fitted to the outer periphery of the shaft is constrained so that the bearing does not move in the axial direction by tightening the nut screwed into the male screw portion of the shaft so as to contact the width surface of the bearing. To do. Then, turn the nut in the tightening direction to match the circumferential phase of the shaft rotation-preventing recess and the nut rotation-prevention recess, and then turn the shaft rotation-prevention recess and the nut rotation-prevention recess respectively. Engage the detent. Thereby, the mutual rotation of the shaft and the nut is restricted, and the loosening of the nut is prevented.

  By arranging a plurality of recesses for preventing rotation of the shaft in the circumferential direction with uneven distribution, maximum tightening of the nut for phase alignment is possible regardless of the circumferential phase relationship between the shaft and the nut. The angle can be small. If the tightening angle of the nut is small and the tightening amount is small, the bearing can be easily attached to and detached from the shaft, and damage to the male screw portion of the shaft and the screw thread of the nut can be prevented. If the diameter of the shaft increases, the tightening amount increases even if the tightening angle is the same, so that the larger the bearing, the higher the effect.

  In addition, when the maximum tightening angle of the nut is the same, the shaft rotation-preventing recesses are arranged more unevenly than the shaft rotation prevention recesses are arranged evenly. The number can be reduced. Therefore, by arranging the recesses for preventing the rotation of the shaft in an uneven distribution, the shaft can be easily processed and the manufacturing cost can be reduced.

  A bearing device according to the present invention includes a shaft, a bearing fitted to the outer periphery of the shaft, a nut that is screwed into a male screw portion protruding from the bearing in the shaft, and is tightened so as to contact the width surface of the bearing. Engaging with the rotation-preventing recess provided on the outer diameter surface of the shaft and the rotation-preventing recess provided on the outer diameter surface of the nut, respectively, to restrict the mutual rotation of the shaft and the nut. And one of the recesses for preventing rotation of the shaft and the recesses for preventing rotation of the nut is provided in a plurality of evenly distributed in the circumferential direction, and the other is provided in a plurality of unevenly distributed in the circumferential direction. It is characterized by being.

  According to this configuration, the bearing that is fitted to the outer periphery of the shaft is constrained so that the bearing does not move in the axial direction by tightening the nut screwed into the male screw portion of the shaft so as to contact the width surface of the bearing. To do. Then, turn the nut in the tightening direction to match the circumferential phase of the shaft rotation-preventing recess and the nut rotation-prevention recess, and then turn the shaft rotation-prevention recess and the nut rotation-prevention recess respectively. Engage the detent. Thereby, the mutual rotation of the shaft and the nut is restricted, and the loosening of the nut is prevented.

  By arranging multiple non-rotating recesses on the shaft or non-rotating nuts in the circumferential direction, phase alignment is possible regardless of the circumferential phase relationship between the shaft and nut. Therefore, the tightening amount of the nut can be reduced. If the tightening amount of the nut is small, the bearing can be easily attached to and detached from the shaft, and damage to the male screw portion of the shaft and the screw thread of the nut can be prevented. If the diameter of the shaft increases, the tightening amount increases even if the tightening angle is the same, so that the larger the bearing, the higher the effect.

  In addition, when the maximum tightening angle of the nut is the same, the direction in which the recesses for rotating the shaft or the recesses for preventing the rotation of the nuts are arranged unevenly is more preferable than the case where the nuts are arranged evenly. It is possible to reduce the number of the shaft rotation-preventing recesses or the nut rotation-preventing recesses. For this reason, by arranging the non-rotating recesses for the shaft or the non-rotating recesses for the nut, the shaft or nut can be easily processed, and the manufacturing cost can be reduced.

  The bearing lock device of the present invention is a bearing lock device that restrains axial movement of a bearing fitted to the outer periphery of the shaft, and is screwed into a male screw portion protruding from the bearing in the shaft, and the width surface of the bearing A nut that is tightened so as to be in contact with the nut, and a non-rotating recess provided on the outer diameter surface of the nut and a non-rotating recess provided on the outer diameter surface of the shaft, An axial direction of the bearing fitted on the outer periphery of the shaft, since the nut includes a rotation stopper for restricting mutual rotation of the nut, and a plurality of recesses for rotation prevention of the nut are provided in an uneven distribution in the circumferential direction The movement can be effectively restrained, the attachment to the shaft is easy, and the processing is easy.

  The shaft according to the present invention is a shaft in which a bearing is fitted to the outer periphery and the axial movement of the bearing is restricted by a bearing lock, and has a male screw portion protruding from the bearing, A non-rotating recess is provided on the radial surface, and the bearing lock member is provided on a nut that is screwed into the male screw portion and tightened so as to contact the width surface of the bearing, and an outer diameter surface of the nut. A non-rotating recess that engages with each of the non-rotating recess and the non-rotating recess of the shaft to restrict rotation of the nut, and the non-rotating recess of the shaft is unevenly distributed in the circumferential direction. Therefore, the axial movement of the bearing fitted to the outer periphery of the shaft can be effectively restrained, and the bearing lock tool can be easily attached to the shaft and can be easily processed.

  A bearing device according to the present invention includes a shaft, a bearing fitted to the outer periphery of the shaft, a nut that is screwed into a male screw portion protruding from the bearing in the shaft, and is tightened so as to contact the width surface of the bearing. Engaging with the rotation-preventing recess provided on the outer diameter surface of the shaft and the rotation-preventing recess provided on the outer diameter surface of the nut, respectively, to restrict the mutual rotation of the shaft and the nut. And one of the recesses for preventing rotation of the shaft and the recesses for preventing rotation of the nut is provided in a plurality of evenly distributed in the circumferential direction, and the other is provided in a plurality of unevenly distributed in the circumferential direction. Therefore, the axial movement of the bearing fitted to the outer periphery of the shaft can be effectively restrained, the assembly is easy, and the processing is easy.

(A) is sectional drawing which shows the use condition of the bearing locking device concerning 1st Embodiment of this invention, (B) is the side view. It is a figure which shows the relationship between the nut and shaft of the bearing lock tool. It is a figure which shows the relationship between the nut and shaft of a bearing locking device concerning 2nd Embodiment of this invention. It is a figure which shows the relationship between the nut and shaft of a bearing lock tool concerning 3rd Embodiment of this invention. It is a figure which shows the relationship between the nut and shaft of a bearing locking tool concerning 4th Embodiment of this invention. (A) is sectional drawing which shows the use condition of the axis | shaft concerning 1st Embodiment of this invention, (B) is the side view. It is a figure which shows the relationship between a coaxial and a nut. It is a figure which shows the relationship between the axis | shaft concerning 2nd Embodiment of this invention, and a nut. It is a figure which shows the relationship between the nut and axis | shaft as a 1st comparative example. It is a figure which shows the relationship between the nut and axis | shaft as a 2nd comparative example. (A) is sectional drawing which shows the detent | locking structure of the nut which used the washer, (B) is the side view. (A) is sectional drawing which shows the detent | locking structure of the nut using a clasp, (B) is the side view. It is a figure which shows the relationship between the nut and shaft of one state in the conventional non-rotating structure of a nut. It is a figure which shows the relationship between the nut and shaft of a different state in the rotation prevention structure of a nut shown in FIG. It is a figure which shows the relationship between the different nut and axis | shaft in the structure of the conventional non-rotation of a nut.

A first embodiment of a bearing lock according to the present invention will be described with reference to FIGS.
As shown in FIG. 1, the bearing lock 1 is used to restrain the axial movement of a bearing 11 fitted to the outer periphery of the shaft 10. The shaft 10, the bearing 11, and the bearing lock 1 constitute a bearing device 9.

  The shaft 10 has a bearing fitting portion 10b having a smaller diameter than the shaft central portion 10a at one end, and a male screw portion 10c projects from the bearing fitting portion 10b toward the tip side. A plurality of groove-shaped anti-rotation recesses 12 along the axial direction are formed on the outer diameter surface of the male screw portion 10c at equal intervals in the circumferential direction. In this embodiment, the number of the rotation preventing recesses 12 is three.

  The bearing lock 1 includes a nut 2 screwed into the male screw portion 10 c and a rotation stopper 3 that prevents the nut 2 from rotating with respect to the shaft 10.

On the outer diameter surface of the nut 2, a plurality of groove-shaped detents 4 for preventing rotation are formed along the axial direction in an irregular manner in the circumferential direction. As shown in FIG. 2, in this embodiment, the number of the anti-rotation recesses 4 is three, and among the three center angles θ ₁₁ , θ ₁₂ , θ ₁₃ of the anti-rotation recesses 4 of these nuts, The two center-to-center angles θ ₁₁ and θ ₁₂ are 160 degrees, and the remaining one-center angle θ ₁₃ is 40 degrees. In other words, when the number of the shaft detent recesses 12 is n in the circumferential direction, the number of the nut detent recesses 4 is n. Of the n center-to-center angles of the nut-rotating recess 4, (n−1) center-to-center angles θ ₁₁ and θ ₁₂ are calculated by a calculation formula of (360 × (n + 1) ÷ n ² ). The angle value is assumed.

  In FIG. 1, the rotation stopper 3 is a C-shaped member, and both ends 3 a and 3 b of the rotation stopper 3 are engaged with the rotation stopper recess 12 of the shaft and the rotation stopper recess 4 of the nut, respectively. Against the nut 2. The rotation stopper 3 is fixed to the nut 2 with bolts 5 at a plurality of locations in the circumferential direction.

  A method for mounting the bearing 11 on the shaft 10 will be described. First, the bearing 11 is fitted into the bearing fitting portion 10 b of the shaft 10. Next, the nut 2 is screwed into the male screw portion 10 c of the shaft 10, and the nut 2 is tightened so as to contact the width surface of the bearing 11. Thereby, the bearing 11 is clamped from both sides by the step surface 10d of the shaft 10 and the nut 2 to restrain the bearing 11 from moving in the axial direction.

  Then, the nut 2 is turned in the tightening direction A so that the circumferential phases of the shaft rotation-preventing recess 12 and the nut rotation-preventing recess 4 coincide with each other, and then the shaft rotation-preventing shaft whose phase in the circumferential direction is matched. Both end portions 3a and 3b of the rotation stopper 3 are engaged with the recess 12 for rotation and the recess 4 for rotation prevention of the nut, respectively. Thereby, the mutual rotation of the shaft 10 and the nut 2 is restricted, and the nut 2 is prevented from loosening. In order to avoid the tightening of the bearing 11 by the nut 2 from being loosened, the nut 2 is turned in the direction A in which the nut 2 is turned when the phase-locking recess 12 on the shaft and the recess 4 on the nut 2 are aligned. is there.

In the state of FIG. 2, the circumferential direction phases of the shaft rotation-preventing recess 12 (1) and the nut rotation-stopping recess 4 (1) coincide with each other, and both rotation-stopping recesses 12 (1), 4 The rotation stopper 3 is engaged with (1). When the nut locking recess 4 (1) is displaced in the direction A in which the nut 2 is tightened with respect to the shaft locking recess 12 (1), the nut 2 is turned in the direction A to tighten the shaft. The rotation stopper 3 is engaged with the rotation stopper recesses 12 (2) and 4 (2) by matching the circumferential phases of the rotation stopper recess 12 (2) and the nut rotation stopper recess 4 (2). Combine. The tightening angle of the nut 2 at this time is 40 degrees at the maximum. Even if the shaft 10 and the nut 2 are in any circumferential phase relationship, the number of the nut rotation preventing recesses 4 and the center-to-center angles θ ₁₁ and θ ₁₂ are determined as described above. The tightening angle of the nut 2 is 40 degrees at the maximum (see No. 2 in Table 1).

The reason will be explained. There are n counter-rotating recesses 12 in the circumferential direction, and n counter-rotating recesses 4 of n nuts are provided between the two adjacent anti-rotation recesses 12 of the shaft. The maximum tightening angle of the nut 2 in this case (for example, FIG. 4) is an angle obtained by dividing the entire circumferential angle (360 degrees) of the nut ² by the square n ² of the number of the non-rotating recesses 4 of the nut, ie, ( 360 ÷ n ² ) degrees (see No. 7 in Table 1).
(360 × (n + 1) ÷ n ² ) degrees, which is the angle between the centers of the (n−1) places between the nut detent recesses 4, in other words, 360 degrees is the square of the number of nut detent recesses divided by n ² in (360 ÷ ^{n 2)} degrees, in which the sum divided by (360 ÷ n) of 360 ° by the number n of the detent recesses of the nut. Compared with FIG. 4, the position of the recess 4 for preventing rotation of each nut is shifted by (360 ÷ n) degrees, so that the maximum tightening angle of the nut 2 is (360 ÷ n ² ) degrees. There is no. In other words, an n-numbered non-rotating recess 4 for the nut prevents the same effect as a non-rotated recess 4 for the nut and n squares.

  FIG. 9 shows a comparative example in which the recesses 4 for preventing the rotation of the nut are provided at equal intervals. In this comparative example, the number of the anti-rotation recesses 12 on the shaft is three as in the first embodiment (FIG. 2), but the number of the anti-rotation recesses 4 on the nut is twice that of the first embodiment. It is six. Nevertheless, the maximum tightening angle of the nut 2 is 60 degrees larger than that of the first embodiment (see No. 1 in Table 1).

  Thus, the bearing lock 1 of the present invention requires a small tightening angle of the nut 2 for phasing. If the tightening angle is small and the tightening amount is small, the bearing 11 can be easily attached to and detached from the shaft 10, and damage to the male screw portion 10c of the shaft 10 and the thread of the nut 2 can be prevented. If the diameter dimension of the shaft 10 is increased, the tightening amount increases even if the tightening angle is the same. Therefore, the larger the bearing 11, the higher the effect.

In addition, since the number of the rotation-preventing recesses 4 of the nut 2 can be reduced as compared with the case where a plurality of the recess-rotation recesses 4 of the nut 2 are arranged in a uniform manner in the circumferential direction, the processing becomes easy. Manufacturing cost can be reduced. Further, if the angle between the centers of the (n−1) places between the nut rotation prevention recesses 4 is (360 × (n + 1) ÷ n ² ) degrees, the rotation prevention recesses 4 of the respective nuts are dispersed over the entire circumference. The balance is good.

FIG. 3 shows a second embodiment. This bearing locking device 1 is attached to a shaft 10 having four equally-rotating recesses 12 for the shaft, and the number of the recesses 4 for preventing the rotation of the nut 2 is four. Four center angles θ ₂₁ , θ ₂₂ , θ ₂₃ , and θ ₂₄ of the four rotation-preventing recesses 4 of the nut are center angles θ ₂₁ , θ ₂₂ , and θ ₂₃ of 112, 5 degrees, and the remaining The center-to-center angle θ _{24 at 1} is 22.5 degrees. The inter-center angles θ ₂₁ , θ ₂₂ , and θ ₂₃ are calculated by the calculation formula of (360 × (n + 1) ÷ n ² ); n = 4, as described above. In this case, the maximum tightening angle is 22.5 degrees (see No. 5 in Table 1).

  FIG. 10 shows a comparative example in which the nut rotation-preventing recesses 4 are provided at equal intervals. In this comparative example, the number of the anti-rotation recesses 12 on the shaft is the same as that of the second embodiment (FIG. 3), but the number of the anti-rotation recesses 4 on the nut is larger than that of the second embodiment. There are six. Nevertheless, the maximum tightening angle of the nut 2 is 30 degrees larger than that of the second embodiment (see No. 4 in Table 1).

FIG. 4 shows a third embodiment. This bearing lock 1 also has a plurality of non-rotating recesses 4 formed on the outer diameter surface of the nut 2 in an uneven manner in the circumferential direction. Are n equally spaced in the circumferential direction, all the nuts 4 for preventing rotation of the nuts are arranged within an angular range of (360 ÷ n) degrees. In this embodiment, since the number of the rotation stopper recesses 12 on the shaft is three, the rotation prevention recesses 4 of all the nuts are arranged within an angle range of 120 degrees. Moreover, the number of the rotation prevention recessed parts 4 of a nut is three, the same number as the rotation prevention recessed parts 12 of a shaft. The recesses 4 for preventing rotation of the nuts are equally distributed within an angle range of 120 degrees, and the center-to-center angles θ ₃₁ and θ ₃₂ are 40 degrees. In this case, the maximum tightening angle of the nut 2 is 40 degrees as in the first embodiment (see No. 3 in Table 1).

FIG. 5 shows a fourth embodiment. This bearing locking device 1 is also configured such that all the nuts for preventing rotation of the nuts 4 are equally arranged within an angular range of (360 ÷ n) degrees. The number of the recesses 4 is four. Accordingly, the recesses 4 for preventing rotation of the nuts are evenly distributed within an angle range of 90 degrees, and the center-to-center angles θ ₄₁ , θ ₄₂ , and θ ₄₃ are 22.5 degrees. In this case, the maximum tightening angle of the nut 2 is 22.5 degrees as in the second embodiment (see No. 6 in Table 1).

  In the third and fourth embodiments, the number of the shaft-retaining recesses 12 and the number of the nut-retaining recesses 4 are the same, but they may be different. In the case where the number of the recesses 12 for preventing the rotation of the shaft is n and the number of the recesses 4 for preventing the rotation of the nut is m, the angles between the centers of the rotation prevention recesses 4 of each nut are (360 / (n Xm)) degree. In this case, the maximum tightening angle of the nut 2 is (360 / (n × m)) degrees (see No. 8 in Table 1).

  Further, in the third and fourth embodiments, the nut rotation preventing recesses 4 are equally arranged within an angular range of (360 ÷ n) degrees, but within an angular range of (360 ÷ n) degrees. It may be unequal. Also in this case, the maximum tightening angle of the nut 2 can be reduced.

Next, a first embodiment of the shaft according to the present invention will be described with reference to FIGS.
As shown in FIG. 6, the shaft 10 has a bearing fitting portion 10b having a diameter smaller than that of the shaft center portion 10a at one end, and a male screw portion 10c projects from the bearing fitting portion 10b to the tip side. The axial movement of the bearing 11 fitted in the bearing fitting portion 10b is restrained by the bearing lock 1. The shaft 10, the bearing 11, and the bearing lock 1 constitute a bearing device 9.

On the outer diameter surface of the male screw portion 10c, a plurality of groove-like recesses 12 for rotation prevention along the axial direction are formed in an irregular manner in the circumferential direction. As shown in FIG. 7, in this embodiment, the number of the rotation-preventing recesses 12 is three, and among the three center angles φ ₁₁ , φ ₁₂ , φ ₁₃ of the rotation-preventing recesses 12 of the shafts, The center-to-center angles φ ₁₁ and φ ₁₂ are 160 degrees, and the remaining center-to-center angle φ ₁₃ is 40 degrees. When there are n rotation-preventing recesses 4 of the nut 2 to be described later that are equally distributed in the circumferential direction, the number of the shaft rotation-prevention recesses 12 is n. Of the n center angles of the recess 12 for preventing rotation of the shaft, (n−1) center angles φ ₁₁ and φ ₁₂ are calculated by a calculation formula of (360 × (n + 1) ÷ n ² ). The

  In FIG. 6, the bearing lock 1 includes a nut 2 screwed into the male screw portion 10 a of the shaft 10, and a rotation stopper 3 that prevents the nut 2 from rotating with respect to the shaft 10. On the outer diameter surface of the nut 2, a plurality of groove-shaped anti-rotation recesses 4 along the axial direction are formed at equal intervals in the circumferential direction. In this embodiment, the number of the recesses 4 for preventing rotation is 3, and the angle between the centers is 120 degrees. The anti-rotation tool 3 is a C-shaped member, and its both ends 3a and 3b are engaged with the anti-rotation recess 12 of the shaft and the anti-rotation recess 4 of the nut, respectively, so that the nut 10 is secured to the shaft 10. Stop 2 The rotation stopper 3 is fixed to the nut 2 with bolts 5 at a plurality of locations in the circumferential direction.

  A method for mounting the bearing 11 on the shaft 10 will be described. First, the bearing 11 is fitted into the bearing fitting portion 10 b of the shaft 10. Next, the nut 2 is screwed into the male screw portion 10 c of the shaft 10, and the nut 2 is tightened so as to contact the width surface of the bearing 11. Thereby, the bearing 11 is clamped from both sides by the step surface 10d of the shaft 10 and the nut 2 to restrain the bearing 11 from moving in the axial direction.

  Then, the nut 2 is turned in the tightening direction A so that the circumferential phases of the shaft rotation-preventing recess 12 and the nut rotation-preventing recess 4 coincide with each other, and then the shaft rotation-preventing shaft whose phase in the circumferential direction is matched. Both end portions 3a and 3b of the rotation stopper 3 are engaged with the recess 12 for rotation and the recess 4 for rotation prevention of the nut, respectively. Thereby, the mutual rotation of the shaft 10 and the nut 2 is restricted, and the nut 2 is prevented from loosening. In order to avoid the tightening of the bearing 11 by the nut 2 from being loosened, the nut 2 is turned in the direction A in which the nut 2 is turned when the phase-locking recess 12 on the shaft and the recess 4 on the nut 2 are aligned. is there.

In the case of the state of FIG. 7, the circumferential phase of the shaft rotation-preventing recess 12 (1) and the nut rotation-preventing recess 4 (1) coincide with each other, and both the rotation-preventing recesses 12 (1), 4 The rotation stopper 3 is engaged with (1). When the nut locking recess 4 (1) is displaced in the direction A in which the nut 2 is tightened with respect to the shaft locking recess 12 (1), the nut 2 is turned in the direction A to tighten the shaft. The rotation stopper 3 is engaged with the rotation stopper recesses 12 (3) and 4 (1) by matching the circumferential phases of the rotation prevention recess 12 (3) and the nut rotation prevention recess 4 (1). Combine. The tightening angle of the nut 2 at this time is 40 degrees at the maximum. Since the number of the shaft-rotating recesses 12 and the center-to-center angles φ ₁₁ , φ ₁₂ are determined as described above, no matter what circumferential phase relationship exists between the shaft 10 and the nut 2, The tightening angle of the nut 2 is 40 degrees at the maximum (see No. 9 in Table 1). The reason for this is the same as that in the case where the recesses 12 for preventing rotation of the shaft are equally distributed in the circumferential direction and the recesses 4 for preventing rotation of the nut are unevenly distributed, and the description thereof will be omitted.

FIG. 8 shows a second embodiment. This shaft 10 is applied with the bearing locking device 1 having four nut locking recesses 4 and the number of shaft locking recesses 12 is four. Between centers angle phi ₂₁ of four positions of the shaft rotation stopping recess 12, phi _22, phi _23, the center angle between the three of φ ₂₄ φ _21, φ _22, is phi ₂₃ in 112,5 degrees, rest The center-to-center angle φ _{24 at 2} is 22.5 degrees. The center-to-center angles φ ₂₁ , φ ₂₂ , and φ ₂₃ are calculated by the calculation formula of (360 × (n + 1) ÷ n ² ); n = 4, as described above. The maximum tightening angle in this case is 22.5 degrees (see No. 10 in Table 1).

  Although illustration is omitted, when there are n counterclockwise recesses 4 for the nut in the circumferential direction, there are a plurality of recesses 4 for antirotation of the shaft, all of which (360 ÷ n) You may arrange | position within the angle range of a degree. The center-to-center angles of the anti-rotation recesses 12 of each axis within the angular range of (360 ÷ n) degrees may be even or uneven. Also in this case, the maximum tightening angle of the nut 2 can be reduced.

DESCRIPTION OF SYMBOLS 1 ... Bearing lock tool 2 ... Nut 3 ... Anti-rotation tool 4 ... Recessed part 9 for nut rotation prevention ... Bearing apparatus 10 ... Shaft 10c ... Male thread part 11 ... Bearing 12 ... Recessed part for shaft rotation prevention

Claims (6)

  A bearing locking device for restraining axial movement of a bearing fitted to the outer periphery of a shaft, wherein the nut is screwed into a male screw portion projecting from the bearing in the shaft and tightened so as to contact the width surface of the bearing And the rotation-preventing recess provided on the outer diameter surface of the nut and the rotation-preventing recess provided on the outer diameter surface of the shaft, respectively, to restrict mutual rotation of the shaft and the nut. A bearing lock device comprising: a rotation stop device, wherein a plurality of recesses for rotation prevention of the nut are provided in an uneven distribution in the circumferential direction. In Claim 1, when the number of the recesses for rotation prevention of the shaft is equal to n in the circumferential direction, the number of recesses for rotation prevention of the nut is n, and n places between the rotation prevention recesses of the nuts A bearing locking device in which the center-to-center angle at (n-1) positions among the center-to-center angles is (360 × (n + 1) ÷ n ² ) degrees.   In Claim 1, when there are n circumferentially spaced recesses for the shaft, there are a plurality of recesses for the nut, all of which are at an angle of (360 ÷ n) degrees. Bearing locking device arranged within the range.   4. The bearing lock device according to claim 3, wherein all of the recesses for preventing rotation of the nut are arranged equally.   A shaft with a bearing fitted on the outer periphery and restrained in the axial direction of the bearing by a bearing lock, having a male thread protruding from the bearing, and for preventing rotation on the outer diameter surface of the male thread. A recess is provided, and the bearing locking device includes a nut that is screwed into the male screw portion and tightened so as to abut against the width surface of the bearing, a rotation-preventing recess provided on an outer diameter surface of the nut, and the nut A rotation stopper that engages with each of the shaft rotation-preventing recesses and restricts rotation of the nut, and a plurality of the shaft rotation-prevention recesses are provided unevenly in the circumferential direction. An axis characterized by that.   A shaft, a bearing fitted to the outer periphery of the shaft, a nut that is screwed into a male screw portion protruding from the bearing in the shaft, and is tightened so as to contact the width surface of the bearing, and an outer diameter surface of the shaft A rotation stopper that engages with a rotation-preventing recess provided on the nut and a rotation-prevention recess provided on the outer diameter surface of the nut, respectively, and that restricts mutual rotation of the shaft and the nut, One of the recesses for preventing rotation of the shaft and the recesses for preventing rotation of the nut is provided in a plurality in the circumferential direction, and the other is provided in a plurality in an uneven distribution in the circumferential direction. Bearing device.

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