JP2007107671A - Thrust bearing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To keep stress of claw parts smaller than endurance limit without increasing plate thickness of a race in a thrust bearing device for positioning the race in its radial direction by respectively inserting the plurality of claw parts protruding at an outer circumference of the race into a plurality of positioning holes provided in a contact member. <P>SOLUTION: In a thrust bearing, a plurality of protruding parts protrude in the outer circumference of the race on which a rolling element rotates around a bearing axis, and a claw part is formed by bending an end of the protruding part in the bearing axis direction. In a contacting member with which the race contacts, a plurality of positioning holes are provided on a pitch circle centering on the bearing axis and each claw part is inserted and engaged in the respective positioning hole so that the race is positioned in the radial direction. In the positioning hole where the claw part contacts with a circumference wall of the positioning hole, the outer circumference edge part of the claw part contacts with the circumference wall of the positioning hole at a position deviated outward from its center. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a thrust bearing device used for an automatic transmission or the like, and more particularly to a thrust bearing device capable of reliably positioning a race on which rolling elements roll.

  In general, the thrust bearing is configured such that a roller is disposed between the first and second races, and a thrust load is received by contacting the first and second contact members in which the respective races rotate relative to each other. For example, when a step portion is formed on the first contact member, the first race is positioned in the radial direction by fitting a bent portion bent in the bearing axial direction with the step portion of the first contact member. However, for example, when a step portion cannot be formed on the second contact member 30, as shown in FIG. 8, a plurality of protrusions 32 protrude outward in the radial direction from the outer periphery of the second race 31, and The front end is bent in the bearing axial direction to form a claw portion 33. The second contact member 30 has a plurality of positioning holes 34 formed on a pitch circle PC concentric with the relative rotation center. Each claw 33 is engaged with each positioning hole 34, whereby the second race 31 is positioned in the radial direction with respect to the second contact member 30. When the first contact member and the second contact member 30 rotate relative to each other, the drag rotation torque T acts on the second race 31 as the roller rolls on the second race 31 with sliding. . For this reason, the claw portion 33 comes into contact with the peripheral wall 35 of the positioning hole 34, and the reaction force F acting on the claw portion 33 from the peripheral wall 35 is balanced with the drag rotation torque T.

  In the conventional apparatus, when the reaction force F acting on the claw portion 33 from the peripheral wall 35 is balanced with the drag rotation torque T, the inner peripheral edge portion of the claw portion 33 is located inside the peripheral wall center position of the positioning hole 34 as shown in FIG. Since the contact is made with the peripheral wall 35 at the biased position, the reaction force F acting on the peripheral wall 35 faces outward in the same direction as the normal direction of the contact point, and the radial component of the reaction force F causes the claw portion 33 to move outward. The bending moment acts on the inner peripheral surface of the bent portion, which is the base end portion of the claw portion 33. It is conceivable to increase the thickness of the second race 31 and increase the strength of the claw portion 33 in order to make the tensile stress acting on the inner peripheral surface of the bent portion with severe stress conditions less than the fatigue limit. If the increase is increased, it is necessary to change the peripheral parts, which limits the degree of freedom in designing the peripheral parts and causes a problem that the apparatus becomes larger.

  The present invention relates to a thrust bearing device for positioning a race in a radial direction by engaging a plurality of claw portions protruding from the outer periphery of the race into a plurality of positioning holes provided in an abutting member, thereby increasing the thickness of the race. It is to make the stress of the nail part below the fatigue limit without doing.

  In order to solve the above-described problem, the structural feature of the invention described in claim 1 is that a plurality of projecting portions project from the outer periphery of the race in which the rolling element revolves around the bearing axis, and the tip of the projecting portion is A claw portion is formed by bending in the bearing axis direction, and a plurality of positioning holes are formed on a pitch circle centered on the bearing axis line in the contact member with which the race contacts, A thrust bearing device in which the claw portion is engaged to position the race in the radial direction, and the outer peripheral edge portion of the claw portion is positioned in any positioning hole where the claw portion contacts the peripheral wall of the positioning hole. It is comprised so that the peripheral wall of the said positioning hole may be contacted in the position which deviated outside from the peripheral wall center position of the hole.

  The structural feature of the invention according to claim 2 is that, in claim 1, the outer peripheral edge portion of the claw portion contacts the peripheral wall of the positioning hole at a position offset outward from the peripheral wall center position of the positioning hole. In addition, the minimum value of the distance from the bearing axis of the claw that is set so that the inner peripheral edge of the claw is separated from the peripheral wall of the positioning hole is the distance from the bearing axis of the claw. It is.

  According to a third aspect of the present invention, in the first or second aspect, when the contact member rotates, the claw portion is a peripheral wall of the positioning hole at any rotational position of the corresponding contact member. In any of the positioning holes that come into contact with the positioning hole, the outer peripheral edge portion of the claw portion is configured to come into contact with the peripheral wall of the positioning hole at a position that is offset outward from the central position of the peripheral wall of the positioning hole.

  According to a fourth aspect of the present invention, there is provided a structural feature according to any one of the first to third aspects, wherein a normal line at a contact point at which the claw portion contacts the peripheral wall of the positioning hole is a rotation direction tangent line. It is inclined to 0 to 20 degrees inside.

  A structural feature of the invention according to claim 5 is that, in any one of claims 1 to 4, the thrust bearing device is a thrust bearing device that supports a thrust load of a rotating member of an automatic transmission. It is.

  In the invention according to claim 1 configured as described above, the race is in the radial direction by contacting the peripheral wall of the positioning hole at a position where the outer peripheral edge of the claw portion is offset outward from the central position of the peripheral wall of the positioning hole. Accordingly, a reaction force directed inwardly acts on the outer peripheral edge of the claw portion. Due to the radial component of the reaction force, an inward bending moment acts on the claw portion, and a compressive stress advantageous to the fatigue limit acts on the inner peripheral surface of the bent portion, which is the base end portion of the claw portion. Thereby, the stress of a nail | claw part can be made into a fatigue limit or less, without restricting the freedom degree of design of peripheral components, without making a race board thickness thick.

  In the invention which concerns on Claim 2 comprised as mentioned above, the bearing axis line of a nail | claw part when the outer-periphery edge part of a nail | claw part contacts the peripheral wall of a positioning hole in the position which deviated outside the peripheral wall center position of the positioning hole Since the minimum value of the distance from the claw is set to the distance from the bearing axis of the claw, the radial component of the reaction force acting on the claw is reduced, and the stress of the claw can be made below the fatigue limit.

  In the invention according to claim 3 configured as described above, when the abutting member rotates, the outer peripheral edge portion of the claw portion is positioned at the center of the peripheral wall of the positioning hole at any rotation position of the abutting member. It is positioned in the radial direction by contacting the peripheral wall of the positioning hole at a position biased to the outside. Thereby, even when the contact member rotates, a reaction force directed inwardly acts on the outer peripheral edge portion of the claw portion, and the stress of the claw portion can be reduced to the fatigue limit or less.

  In the invention according to claim 4 configured as described above, the radial component of the reaction force acting inwardly on the outer peripheral edge portion of the claw portion that contacts the peripheral wall of the positioning hole can be limited to a small value. The stress can be reduced below the fatigue limit.

  In the invention according to claim 5 configured as described above, since the thrust bearing device according to the present invention supports the thrust load of the rotating member of the automatic transmission, the stress of the claw portion without increasing the thickness of the race of the bearing device. Can be reduced below the fatigue limit, increasing the degree of freedom in designing peripheral components, and reducing the size and weight of the automatic transmission.

  Hereinafter, an embodiment of a thrust bearing device according to the present invention will be described with reference to the drawings when the thrust bearing device is used as a thrust bearing device for supporting a thrust load of a rotary member of a known automatic transmission. . The automatic transmission includes a torque converter and a multi-stage transmission mechanism. The torque converter and the multi-stage transmission mechanism are arranged in series on one axis and housed in a case. The multi-stage transmission includes a plurality of planetary gears having a sun gear, a ring gear, and a carrier that supports a planetary gear meshing with the sun gear and the ring gear as rotating elements, and includes a plurality of clutches and a plurality of brakes.

  The automatic transmission configured in this manner selectively engages a plurality of clutches to connect the rotating elements of the plurality of planetary gears, selectively transmits the output rotation of the torque converter, and selects a plurality of brakes. By engaging with each other and selectively restricting the rotation of each element of the planetary gear, the output rotation of the torque converter is shifted to a plurality of forward stages and one reverse stage and transmitted to the output shaft.

  In FIG. 1, reference numeral 11 denotes a thrust bearing constituting the thrust bearing device 2, and a large number of rollers 14 are sandwiched between the first and second races 12, 13, and the rollers 14 run on the first and second races 12, 13. Revolves around the bearing axis O1. The first race 12 contacts the end surface of the first rotating member 15 of the automatic transmission, and the second race 13 contacts the end surface of the second rotating member 16 and receives a thrust load via the roller 14. . The first race 12 is positioned in the radial direction with a bent portion bent in the bearing axial direction fitted to the outer peripheral portion of the tip end of the first rotating member 15.

  When the second rotating member 16 is fitted with the second race 13 to form a step portion for positioning the second race 13 in the radial direction, the apparatus becomes large. Therefore, the second rotating member 16 includes the bearing axis O1 of the thrust bearing device 2. A plurality of positioning holes 18 are bored at equiangular α intervals on a concentric pitch circle PC. When the number of the positioning holes 18 is 5, the angle α is 72 degrees. The second race 13 has a plurality of projecting portions 19 projecting outward in the radial direction from the outer periphery, and claw portions 20 are formed by bending the tips of the projecting portions 19 in the bearing axial direction. Each claw portion 20 is engaged with each positioning hole 18, whereby the second race 13 is positioned in the radial direction with respect to the second rotating member 16. The second rotating member 16 is a contact member in which a race contacts and a plurality of positioning holes are formed on a pitch circle centered on the bearing axis.

  Since the first rotating member 15 and the second rotating member 16 rotate relative to each other, the drag rotation torque T acts on the second race 13 when the roller 14 rolls on the second race 13 with sliding. At this time, as shown in FIG. 2, the reaction force F acts on the claw portion 20 in contact with the peripheral wall 23 of the positioning hole 18 from the peripheral wall 23, and balances with the drag rotation torque. In this case, since the second rotating member 16 also rotates, the outer peripheral edge of the claw 20 in the positioning hole 18 where the claw 20 contacts the peripheral wall 23 of the positioning hole 18 at any rotational position of the second rotating member 16. The part 21 is configured to come into contact with the peripheral wall 23 of the positioning hole 18 at a position offset outward from the peripheral wall central position 22 of the positioning hole 18. That is, the second race 13 is positioned in the radial direction with any of the claw portions 20 contacting the peripheral wall 23 of the positioning hole 18. At this time, at any rotation position of the second rotation member 16, the outer peripheral edge 21 of the claw 20 is the center of the peripheral wall of the positioning hole 18 in any positioning hole 18 where the claw 20 contacts the peripheral wall of the positioning hole 18. It is comprised so that the surrounding wall of the positioning hole 18 may be contacted in the position which deviated outside the position 22. FIG. The peripheral wall central position 22 of the positioning hole 18 is a position where the pitch circle PC concentric with the bearing axis O <b> 1 intersects the peripheral wall 23 of the positioning hole 18.

  Next, at any rotational position of the second rotating member 16, the outer peripheral edge 21 of the claw 20 contacts the peripheral wall 23 of the positioning hole 18 at a position offset outward from the peripheral wall central position 22 of the positioning hole 18. In order to configure as described above, an example of a method for setting the distance from the bearing axis O1 of the claw 20 and the width of the claw 20 will be described.

  As the shape of the thrust bearing device 2, the second race 13 has N protrusions 19 that are parallel to both sides from the outer periphery of an annular plate having a plate thickness t, and the tip of the protrusion 19 is formed at equal intervals. The claws 20 are formed by being bent 90 degrees and formed into a partial cylindrical shape. Therefore, as shown in FIG. 3, the claw portion 20 is symmetrical with respect to the center line passing through the center in the circumferential direction and the center of the second race 13, and both side surfaces of the claw portion 20 are parallel to the center line. The width of the part 20 is b, and the thickness is t. The claw radius at the center in the thickness direction of the claw portion 20 centered on the bearing axis O1 is R, the inner diameter of the claw portion 20 is Ri, and the outer diameter is Ro. The radius of the positioning hole 18 drilled in the second rotary member 16 on the pitch circle PC at an equal angle α interval is r, and the X and Y coordinate values of the center of each positioning hole 18n are cn and dn. The radius of the pitch circle PC is Rpc.

  First, assuming that there is no dimensional variation, the outer peripheral edge portion 21 and the inner peripheral edge portion 24 of the claw portion 20 are equivalent to the outer side and the inner side of the peripheral wall center position 22 of the positioning hole 18 as shown in FIG. Assuming that the nail thickness t is extremely smaller than the nail radius R, assuming that the nail thickness t is in contact with the peripheral wall 23 of the positioning hole 18, the reaction force acting on the outer peripheral edge 21 and the inner peripheral edge 24 of the nail 20. Fi and Fo are substantially equal, and the radial components of the reaction forces Fi and Fo cancel each other, and no radial bending moment acts on the claw portion 20. The claw radius R at this ideal position is equal to the radius Rpc of the pitch circle PC, is set by R = Rpc, and the claw width b is approximated to the diameter 2r of the positioning hole 18.

  Actually, since a clearance for engaging the claw portion 20 into the positioning hole 18 is necessary, the claw width b is set to an appropriate value b smaller than 2r. In this case, the claw radius R, which is the distance from the bearing axis O1 of the claw portion 20, is increased by a minute amount ΔR, and the claw portion is in any positioning hole 18 where the claw portion 20 contacts the peripheral wall 23 of the positioning hole 18. It is determined whether or not the outer peripheral edge portion 20 of the 20 contacts the peripheral wall 23 of the positioning hole 18 at a position offset outward from the peripheral wall central position 22 of the positioning hole 18. Set to. Since the clearance between the claw portion 20 and the positioning hole 18 is reduced by increasing the claw radius R, the claw width b is decreased by a small amount Δb as the claw radius R increases.

  Next, a determination method when it is assumed that there is no dimensional variation of each part will be described. The calculation prerequisites used for the determination are as follows.

(1) The initial position is the state shown in FIG. 3 in which the center of one positioning hole 18 drilled at an equal angle α interval on the pitch circle PC is displaced clockwise from the Y axis by an angle θ. positioning holes 18 a first positioning holes 18 ₁ displaced from the axis by an angle theta, 2 th.. the hole 18 engaged by the pawl portion 20 in ₁ 1 th claw portion 20 _1, and the following clockwise The n-th positioning hole 18n and the claw portion 20n are used.

(2) When the claw radius R is increased by ΔR and the claw width b is decreased by Δb from the dimensions of the claw portion 20 at the ideal position, each claw portion 20n is moved from the ideal position in FIG. The distance ΔYon until the outer peripheral edge portion 21n comes into contact with the peripheral wall 23n of each positioning hole 18n is calculated, and the distance until the inner peripheral edge portion 24n comes into contact with the peripheral wall 23n of each positioning hole 18n. ΔYin is calculated.

(3) In each positioning hole 18n, the smaller one of the distances ΔYon and ΔYin out of the outer peripheral edge 21n and the inner peripheral edge 24n of each claw 20n contacts the peripheral wall 23n of the positioning hole 18n. Since each claw 20n is intended to come into contact with the peripheral wall 23n of the positioning hole 18n at the outer peripheral edge 21n, ΔYon <ΔYin needs to be established in each positioning hole 18n.

(4) Since the second rotation member 16 rotates, the angle Δα between adjacent positioning holes 18 is not the same as the number N of positioning holes, for example, an angle Δα divided by N + 1 (when there are five claw portions 20) (2) and (3) are repeated with the second rotating member 16 rotated by 12 degrees. At any rotational position of the second rotating member 16, ΔYon <ΔYin needs to be established in each positioning hole 18n.

(5) The nail radius R is increased by ΔR and the nail width b is decreased by Δb until (2) to (4) are satisfied. The initial nail radius R and nail width b satisfying (2) to (4) are set as the specifications of the nail portion 20.

Specifically, as the first step, calculation is performed for the _first claw portion 18 _{1 at} the initial position. As shown in FIGS. 5 and 6, in the XY coordinate system in which the bearing axis O1 as the origin, the angle between the center line and the Y-axis of the claw portion 20 ₁ theta,
The angle between the center line of the line segment and the claw portion 20 ₁ connecting the inner peripheral edge portion 24 and the bearing axis O1 of the pawl portion 20 ₁ .theta.i,
The angle between the line segment connecting the outer peripheral edge 21 of the claw 20 ₁ and the bearing axis O _{1 and} the center line of the claw 20 ₁ is θo,
The radii of the inner and outer peripheral surfaces of the claw 20 centered on the bearing axis O1 are Ri, Ro,
Inner peripheral edge portion 24 of the claw portions 20 _1, X-coordinate value of the outer peripheral edge portion 21, the Y coordinate value Xfi1, Xfo1, Yfi1, Yfo1,
Inner peripheral edge portion 24, the Y-coordinate value of a point outer periphery 21, respectively as the Y axis and the parallel line segments intersects the positioning holes 20 ₁ Yhi1, Yhol,
The radius of the positioning holes 20 ₁ and r.

Inner peripheral edge portion 24 of the claw portion 20 _1, the angle θi between the center line of the line segment and the claw portion 20 ₁ connecting each of the outer peripheral edge portion 21 and the bearing axis O1, .theta.o is
θi = sin ⁻¹ b / 2Ri
It is calculated from θo = sin ⁻¹ b / 2Ro.
As apparent from FIG. 3, 5, 6, the inner peripheral edge portion 24 of the claw portions 20 _1, X coordinate value Xfi1 of the outer peripheral edge portion 21, Xfo1, is
Xfi1 = Ri x sin (θ + θi)
It is obtained from Xfo1 = Ro × sin (θ + θo).
Inner peripheral edge portion 24 of the claw portions 20 _1, Y coordinate values Yfi1, Yfo1 of the outer peripheral edge portion 21,
Relational expression Xfi1 ² + Yfi1 ² = Ri ^{2 for} the second race 13
Xfo1 ² + Yfo1 ² = Ro ²
The claw portion 20 ₁ of the inner peripheral edge portion 24, the outer peripheral edge portion 21 respectively as parallel to the Y axis line segment positioning holes 20 ₁ and Y-coordinate values of the point of intersection Yhi1, Yhol is
Relational expression for positioning hole 18
(Xfi1−c1) ² + (Yhi1−d1) ² = r ²
Obtained from ^{(Xfo1-c1) 2 + (} Yho1-d1) 2 = r 2.

The second race 13, since the stop moves downward until the claw portion 20 ₁ is brought into contact with the positioning holes 18 ₁ of the peripheral wall 23, in the inner peripheral edge portion 24 and the outer peripheral edge portion 21 of the claw portion 20 _1, the inner peripheral edge Difference YY1 between the Y coordinate value Yfi1 of the portion 24 and the Y coordinate value Yhi1 of the peripheral wall 23 below the inner peripheral edge 24 and the difference between the Y coordinate value Yfo1 of the outer peripheral edge 21 and the peripheral wall 23Y coordinate value Yho1 below the outer peripheral edge 21 The smaller ΔYo1 comes into contact with the peripheral wall 23 first. Since the purpose of the outer peripheral edge portion 21 of the claw portion 20 contacts the peripheral wall 23 of the positioning hole 18 at a position biasing outward from the peripheral wall center 22 of the positioning hole 18, the positioning holes 18 _1,
ΔYo1 <ΔYi1 must be satisfied. If this inequality is not satisfied, the nail radius R is increased by ΔR and the nail width b is decreased by Δb until the satisfaction is satisfied, and the calculation is repeated, and ΔYo1 when ΔYo1 <ΔYi1 is first satisfied is the first nail portion. the 20 ₁ of eccentricity.

As the second step, for the second... Nth claw portion 20, the same calculation as that of the _first claw portion 201 described above is repeated, and the eccentricity ΔYo2. Then, the minimum value in the claw radius R corresponding to the amount of eccentricity in each claw 20n and the claw width b at that time are used as the origin of the claw 20 at the initial position.

Next, as a third step, at any angular position of the second rotating member 16, the center of one positioning hole 18 is moved from the Y axis in order to set the nail position where ΔYon <ΔYin is first established. The initial position is the state of FIG. 3 that is displaced clockwise by the angle θ. For example, the angle θ between the center of the adjacent positioning hole 18 and the bearing axis O1 is set to 1 for the number N of positioning holes 18. The calculation similar to that at the initial position is repeated with the angle α / (N + 1) rotated clockwise by the added value (N + 1), and the eccentricity ΔYo11... ΔYonn at each divided angle position is calculated. . Specifically, as shown in FIG. 7, the angle θ formed between the center line of the _first claw 201 at the initial position and the Y axis is expressed as θ + α / (N + 1), θ + 2α / (N + 1). And sequentially increasing the calculation at each division angle position. The minimum value among the nail radii R set as the nail coordinates at the initial position and each divided angle position of the second rotating member 16 and the nail width b at that time are defined as the nail parts 20.

  As described above, it is confirmed that the outer peripheral edge portion 21 of the claw portion 20 is in contact with the peripheral wall 23 of the positioning hole 18 in each positioning hole 18 with the second rotating member 16 rotated to the divided angle position. Even if the second race 13 is displaced in any direction with respect to the second rotating member 16, the outer peripheral edge 21 of the claw 20 in any positioning hole 18 where the claw 20 contacts the peripheral wall 23 of the positioning hole 18. Is in contact with the peripheral wall 23 of the positioning hole 18 at a position offset outward from the central position 22 of the peripheral wall of the positioning hole 18.

  Actually, there are dimensional variations in the inner and outer diameters Ri, Ro, claw width b, claw angle, radius r of the positioning hole 18 and X and Y coordinate values (cn, dn) of the center of the positioning hole 18n. Therefore, by performing the above calculation with dimensional tolerances added to each dimension, the outer peripheral edge 21 of the claw 20 is displaced to the peripheral wall 23 of the positioning hole 18 at a position offset outward from the peripheral wall central position 22 of the positioning hole 18. The specification of the nail | claw part 20 can be set so that it may contact.

Specifically, for example, when the X and Y coordinate values (cn, dn) of the center of the positioning hole 18n are allowed to have a large tolerance Δc, Δd and the radius r is allowed to be a large tolerance Δr, each tolerance is allowed. The above calculation is performed for all the combinations in which the symbol appears, and the specification of the claw portion 20 is set.
That is, (Xfin−cn) ² + (Yhin−dn) ² = r ²
{Xfin− (cn + Δc)} ² + {Yhi1−dn} ² = r ²
{Xfin- (cn + Δc)} 2 + {Yhi1- (dn + Δd)} 2 = r 2
...
{Xfin− (cn + Δc)} ² + {Yhi1− (dn + Δd)} ² = (r + Δr) ²
Then, calculation is performed for all combinations of tolerances and the specifications of the claw portion 20 are set.

  In the above-described embodiment, the second rotating member 16 rotates. If the second rotating member 16 does not rotate, the claw portion 20 can be moved to the peripheral wall 23 of the positioning hole 18 by performing the first and second steps without performing the third step. In any of the positioning holes 18 that come into contact with the positioning hole 18, the outer peripheral edge 21 of the claw 20 is in contact with the peripheral wall 23 of the positioning hole 18 at a position offset outward from the peripheral wall central position 22 of the positioning hole 18. Nail radius R and nail width b can be set.

  In the above embodiment, the claw radius R is increased by a minute amount ΔR, and the outer peripheral edge 21 of the claw 20 is positioned in the positioning hole 18 in any positioning hole 18 where the claw 20 contacts the peripheral wall 23 of the positioning hole 18. It is determined whether or not it contacts the peripheral wall 23 of the positioning hole 18 at a position that is offset outward from the peripheral wall central position 22, and a value that first satisfies this condition is set as the claw radius R. If the normal value at the contact point at which the claw portion 20 contacts the peripheral wall 23 of the positioning hole 18 is inclined to 0 to 20 degrees inward with respect to the rotation direction tangent, the claw portion 20 acts on the claw portion 20. The component of the reaction force F in the radial direction can be limited to a small value, and the stress at the claw portion can be reduced below the fatigue limit. Therefore, as long as the claw radius R satisfies this condition, the claw radius R may be set to a value that does not satisfy the condition first.

The expanded sectional view of this thrust bearing device. The figure which shows the state which the nail | claw part of the bearing apparatus which concerns on embodiment contacts the surrounding wall of a positioning hole. The figure for deriving the computing equation for calculating the amount of eccentricity of the 1st claw part. The figure which shows the state which a nail | claw part contacts the surrounding wall of a positioning hole in an ideal state. The figure which shows the angle which the line segment which connects the inner peripheral edge part of a nail | claw part and a bearing axis line makes with an X-axis. The figure which shows the angle which the line segment which connects the outer periphery part of a nail | claw part and a bearing axis line with an X-axis. The figure which shows the state which calculates the amount of eccentricity in each division | segmentation angle position of a 2nd rotation member. The figure which shows the state which the nail | claw part of the conventional thrust bearing apparatus contacts the surrounding wall of a positioning hole.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 2 ... Thrust bearing apparatus, 11 ... Thrust bearing, 12, 13 ... 1st, 2nd race, 14 ... Roller, 15 ... 1st rotation member, 16 ... 2nd rotation member, 18 ... Positioning hole, 19 ... Projection part, 20 ... claw part, 21 ... outer peripheral edge part, 22 ... central position, 23 ... peripheral wall, 24 ... inner peripheral part, R ... claw radius, b ... claw width, r ... positioning hole radius, ΔYon ... eccentricity.

Claims (5)

A contact member in which a plurality of projecting portions project from the outer periphery of the race in which the rolling element revolves around the bearing axis, the tip of the projecting portion is bent in the direction of the bearing axis, and a claw is formed. A thrust bearing device in which a plurality of positioning holes are formed on a pitch circle centered on the bearing axis, and the claw portions are inserted into the positioning holes to position the race in the radial direction. In any positioning hole in which the claw portion comes into contact with the peripheral wall of the positioning hole, the outer peripheral edge portion of the claw portion comes into contact with the peripheral wall of the positioning hole at a position offset outward from the central position of the peripheral wall of the positioning hole. A thrust bearing device comprising: In Claim 1, While the outer peripheral edge part of the said nail | claw part contacts the peripheral wall of the said positioning hole in the position which deviated outside the peripheral wall center position of the said positioning hole, the inner peripheral edge part of the said nail | claw part is the said positioning hole. A thrust bearing device, characterized in that a minimum value of the distance from the bearing axis of the claw portion set so as to be separated from the peripheral wall is a distance from the bearing axis of the claw portion. 3. The positioning device according to claim 1, wherein when the abutting member rotates, in any positioning hole where the claw portion contacts the peripheral wall of the positioning hole at any rotation position of the corresponding contact member, A thrust bearing device, wherein the peripheral portion is configured to contact the peripheral wall of the positioning hole at a position offset outward from the central position of the peripheral wall of the positioning hole. The normal line at the contact point at which the claw portion contacts the peripheral wall of the positioning hole is inclined inward by 0 to 20 degrees with respect to the rotational tangent line. Thrust bearing device. The thrust bearing device according to any one of claims 1 to 4, wherein the thrust bearing device is a thrust bearing device that supports a thrust load of a rotating member of an automatic transmission.

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