JP2016061685A - Thrust bearing assembly surface posture detection device and assembly surface posture detection method - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable assembly with a steel material as it is without an assembly surface transparent when assembling a thrust bearing to a rotation testing device or the like with high accuracy.SOLUTION: A probe 62 which can perform ultrasonic transmission and ultrasonic reception is arranged at a position facing a rolling element 19 of a thrust bearing 10 in an axial direction with a support member 33 held therebetween, echo intensity at the time of rotation of the probe 62 in a circumferential direction and a rotation angle of the probe 62 are measured over the whole circumference, and the inclination of the support member 33 is detected on the basis of the measurement result.SELECTED DRAWING: Figure 2

Description

  The present invention relates to an assembly surface posture detection device and an assembly surface posture detection method used when a thrust bearing is assembled with high accuracy.

The thrust bearing includes a plurality of rolling elements arranged annularly at a predetermined interval by a cage, and a pair of race rings are arranged to face each other in the axial direction across the rolling elements. Each of the pair of race rings is made of a steel material having a predetermined hardness, and is rotatable relative to each other around the axis of the thrust bearing.
Various rotation tests are performed to improve the performance of the thrust bearing. For example, a test for measuring characteristics such as temperature and torque is performed by observing the behavior of a rotating rolling element or rotating the rolling element under a load. In the rotation test, a support member that supports the thrust bearing in the axial direction is incorporated in parallel to the thrust bearing. In particular, in a thrust roller bearing in which the rolling element is a roller, when the direction of the support member is inclined with respect to the thrust bearing, the contact state between the roller and the bearing ring becomes uneven over the entire circumference. At this time, since the roller behaves abnormally, such as skewing, an accurate rotation test cannot be performed. For this reason, it is necessary to incorporate the thrust bearing and the support member in parallel with high accuracy.

  For example, in the roller behavior measuring device disclosed in Patent Document 1, one of the pair of race rings is integrated with a support member and is made of a transparent material. By making it transparent, the contact state between the roller and the race can be directly observed. Based on the observation result, the roller and the race are adjusted so as to be in uniform contact over the entire circumference.

JP 2013-156201 A

However, in the method of Patent Document 1, it is necessary to manufacture a transparent race ring with a material such as synthetic resin. Synthetic resin races have different physical properties such as surface hardness and elastic modulus compared to races made of steel, which is the original material. For this reason, when the rotation test is performed under the condition that a load is applied using a transparent race, the contact state between the roller and the race changes as compared to the case where the race is made of steel. End up. For this reason, it is impossible to perform a precise rotation test in consideration of the rigidity of the raceway.
On the other hand, when the race is made of the original steel material, it cannot be confirmed whether the thrust bearing and the support member are incorporated in parallel with each other. Therefore, there is a possibility that the rotation test is performed while the contact state between the roller and the raceway is not uniform over the entire circumference.
From such a situation, even if a rotation test is performed on a thrust bearing using a race ring made of an original steel material, by detecting the attitude of the support member and the thrust bearing, the thrust bearing and It is necessary to incorporate the support members so that they are arranged in parallel with high accuracy.

  An object of the present invention is to make it possible to detect the attitude of the support member and the thrust bearing without changing the material of the raceway ring when assembling the thrust bearing in a rotation test apparatus or the like. .

  One aspect of the thrust bearing assembly surface detecting device according to the present invention is a combination of a thrust bearing having rolling elements arranged at predetermined intervals in the circumferential direction and a support member for supporting the thrust bearing in the axial direction. A thrust bearing assembly surface orientation detecting device for detecting the orientation of the support member and the thrust bearing of a thrust bearing assembly, wherein the thrust bearing is opposed to the axial direction with the support member interposed therebetween. A rotating member that rotates coaxially with the thrust bearing, a rotation angle detecting device that detects a rotation angle of the rotating member, and a probe that can transmit an ultrasonic wave and receive an echo. The probe is attached to the rotating member at a position where the probe is irradiated with ultrasonic waves toward the rolling element with the support member interposed therebetween. The signal processing device includes a rotation angle signal from the rotation angle detection device, an echo signal from the ultrasonic device when the ultrasonic wave is irradiated toward the thrust bearing while rotating the rotating member, and , The relationship between the rotation angle signal and the echo signal is output.

  One aspect of the method for adjusting the mounting surface attitude of the thrust bearing according to the present invention is a thrust bearing that detects the attitude of the support member and the thrust bearing using the one aspect of the apparatus for detecting the mounting surface attitude of the thrust bearing. In this assembly surface orientation detection method, the rotating member is disposed at a position opposed to the thrust bearing in the axial direction with the support member interposed therebetween, and the probe is connected to the rolling element. A second step of simultaneously measuring the echo signal and the rotation angle by transmitting the ultrasonic wave toward the moving body together with the rotary member while being coaxial with the thrust bearing, and the echo signal and the rotation angle signal; And a third step of detecting the posture of the support member and the thrust bearing from the change of the echo signal with respect to the rotation angle.

  According to the present invention, it is possible to detect the attitude of the support member and the thrust bearing without changing the material of the raceway ring when assembling the thrust bearing in a rotation test apparatus or the like without changing the material of the bearing ring.

It is an axial sectional view of a thrust roller bearing. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a structural diagram illustrating a structure of a thrust roller bearing assembly surface posture detection device according to an embodiment of the present invention and a method of using the same. It is sectional drawing which shows the assembled state of the thrust roller bearing in a 1st contact state. It is a graph which shows the measurement result in the 2nd step of the posture adjustment procedure of the present invention. It is sectional drawing which shows the assembled state of the thrust roller bearing in a 2nd contact state. It is sectional drawing which shows the assembled state of the thrust roller bearing in a 3rd contact state. It is a local sectional view for explaining the elastic contact field of a roller and an inner ring race part in the 3rd contact state.

  Hereinafter, a thrust roller bearing assembly surface attitude detection device 70 according to an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is an axial sectional view of a thrust roller bearing 10. FIG. 2 explains the structure of the assembly roller attitude detection device 70 of the thrust roller bearing, and the bearing ring of the thrust roller bearing 10 incorporated in the rotation test device 30 using the assembly surface attitude detection device 70. It is a structural diagram explaining the method of detecting the attitude | position of.

  First, the thrust roller bearing 10 and the rotation test apparatus 30 will be described. The thrust roller bearing 10 of FIG. 1 includes a plurality of rollers 19 (rolling elements) arranged in a radial direction, a retainer 11, an outer ring 17, and an inner ring 14.

  The roller 19 is made of bearing steel. The outer peripheral surface has a cylindrical shape and is finished by grinding.

  The cage 11 has an annular shape and is manufactured by press-forming a thin steel plate such as an SPCC material. The cross section in the axial direction of the annular portion is substantially M-shaped. A plurality of pocket portions 12 penetrating in the axial direction are formed in the annular portion at predetermined intervals in the circumferential direction. The shape of the pocket portion 12 when viewed from the axial direction is a rectangle. One roller 19 is inserted into each pocket portion 12. A slight clearance is provided between the inner periphery 19 of the pocket portion 12 and the outer periphery of the pocket portion 12, and each roller 19 is held by the pocket portion 12 so as to be able to roll.

  The outer ring 17 and the inner ring 14 are each formed in an annular shape from a metal plate such as polished special band steel having sufficient hardness. The outer ring 17 includes an annular outer ring race portion 18 and a cylindrical outer flange 20 formed on the outer periphery of the outer ring race portion 18 over the entire circumference. The inner ring 14 includes an annular inner ring race portion 13 and an inner flange 15 formed over the entire inner periphery of the inner ring race portion 13.

  In the thrust roller bearing 10, the surface of the outer ring race portion 18 on the side where the outer flange 20 is formed and the surface of the inner ring race portion 13 on the side where the inner flange 15 is formed face each other across the roller 19. So that they are combined coaxially. At this time, slight clearances are provided between the outer periphery of the retainer 11 and the inner periphery of the outer flange 20 and between the inner periphery of the retainer 11 and the outer periphery of the inner flange 15. Thus, the cage 11 is guided in the radial direction by the outer flange 20 and the inner flange 15, and when the outer ring 17 and the inner ring 14 are relatively rotated coaxially, the cage 11 and 19 revolve together.

  In order to prevent the outer ring 17 and the inner ring 14 from being separated, the ends of the outer flange 20 and the inner flange 15 are crimped in a state where the outer ring 17 and the inner ring 14 are assembled to the thrust roller bearing 10. The outer locking portion 21 and the inner locking portion 16 projecting in the radial direction are formed.

  Next, the structure of the rotation test apparatus (thrust bearing assembly) 30 will be described with reference to FIG. The rotation test apparatus 30 includes a main body 36 fixed to a base (not shown), a fixed base 33 (support member) that supports the thrust roller bearing 10, and a rotating unit 50. In the following description, the left-right direction in the drawing is referred to as “axial direction”, the direction orthogonal to the axial direction is referred to as “radial direction”, and the direction of turning around the axis is referred to as “circumferential direction”.

The fixed base 33 has a flat plate shape, and an inner ring support surface 32 with which the inner ring race portion 13 of the thrust roller bearing 10 abuts is formed on one side in the thickness direction. On the inner ring support surface 32, a convex portion 34 extending in a direction perpendicular to the surface is formed. The convex portion 34 has a cylindrical shape, and an inner ring guide surface 34a is formed on the outer periphery thereof. The outer diameter dimension of the inner ring guide surface 34 a is slightly smaller than the inner diameter dimension of the inner flange 15 of the inner ring 14.
On the other side of the fixed base 33 in the thickness direction, a detection surface 35 formed in parallel with the inner ring support surface 32 is provided. The detection surface 35 is finished to a flat surface with small roughness by grinding.
The fixed base 33 is fixed to the main body 36 via a plurality of adjusting mechanisms 24 in a direction in which the thickness direction is substantially the axial direction.

  The adjustment mechanism 24 is installed at three locations at equal intervals in the circumferential direction away from the center of the convex portion 34 in the radial direction. Although a detailed description of the detailed structure of the adjustment mechanism 24 is omitted, the adjustment mechanism 24 is configured as follows, for example. A male screw 24a extending in the axial direction from the main body 36 and a male screw 24b extending in the axial direction from the fixed base 33 are provided facing each other in the axial direction. The torsion directions of the male screw 24a and the male screw 24b are opposite to each other. The sleeve 24c is provided with female screws that are respectively engaged with the male screw 24a and the male screw 24b at both ends in the axial direction. The dimension between the main body 36 and the fixed base 33 can be adjusted by rotating the sleeve 24c around the screw shaft. By individually extending and retracting each adjustment mechanism 24, the posture of the fixed base 33 can be adjusted to an arbitrary inclination.

  The rotating portion 50 is formed of a main shaft 56 that is rotatably supported by a rolling bearing (not shown), and a rotating flange 58 that is coaxially attached to the shaft end of the main shaft 56. The rotating unit 50 can move in the axial direction. By pressing the rotary flange 58 against the thrust roller bearing 10, an axial load can be applied to the thrust roller bearing 10.

  The rotating flange 58 has a cylindrical outer periphery, and an outer ring support surface 51 is formed on the side facing the fixed base 33 (the right side in the figure). The outer ring support surface 51 is a plane orthogonal to the axis of the main shaft 56. The outer ring support surface 51 is formed with an outer ring guide portion 52 that protrudes in the axial direction from the outer periphery to the entire periphery. An outer ring guide surface 52 a is formed on the inner periphery of the outer ring guide portion 52. The outer ring guide surface 52 a is a cylindrical surface coaxial with the main shaft 56, and the diameter dimension thereof is slightly larger than the outer diameter dimension of the outer flange 20 of the outer ring 17.

  A procedure for incorporating the thrust roller bearing 10 into the rotation test apparatus 30 will be described. First, the inner flange 15 of the thrust roller bearing 10 is fitted to the inner ring guide surface 34 a of the fixed base 33. Next, the rotating unit 50 is moved in the axial direction. The outer flange 20 of the thrust roller bearing 10 is fitted to the outer ring guide surface 52 a of the rotating flange 58. In this way, the thrust roller bearing 10 is assembled between the fixed base 33 and the rotating flange 58. Since the outer ring support surface 51 is in contact with the outer ring race portion 18 of the thrust roller bearing 10, the outer ring 17 is rotated by the rotation of the rotating flange 58.

  Next, referring to FIG. 2, a thrust roller bearing assembly surface posture detection device 70 (hereinafter simply referred to as “posture detection device”) will be described. Reference is made to FIG. 1 as appropriate. The posture detection device 70 includes a contact plate 71 (rotating member) that rotates integrally with the rotation applying unit 75, a rotation angle detection device 65, an ultrasonic device 60, and a signal processing device 67.

The contact plate 71 has a cylindrical shape, and on one side surface in the axial direction, a flat probe installation surface 71a perpendicular to the axis is formed. On the outer peripheral edge of the probe installation surface 71a, a shielding portion 73 that protrudes in the axial direction is formed over the entire circumference. Both the inner peripheral surface and the outer peripheral surface of the shielding part 73 have a cylindrical shape coaxial with the contact plate 71. The axial end of the outer peripheral surface and the axial end of the inner peripheral surface are connected by a shielding end surface 73a that is a plane orthogonal to the axis. The shielding end surface 73a is finished to a flat surface with a small surface roughness by grinding.
A cylindrical probe insertion hole 71b is provided in a direction perpendicular to the probe installation surface 71a on the radially inner side of the inner peripheral surface of the shielding portion 73. The probe insertion hole 71 b is formed at a position equal to the radius of the pitch circle of the roller 19 (a circle connecting the center point of the axial length of the roller 19) from the center of the contact plate 71.
A small-diameter hole penetrating in the thickness direction of the contact plate 71 is further provided on the bottom surface of the probe insertion hole 71b.
A universal joint mounting surface 71 c is formed on the other side surface in the axial direction of the contact plate 71. The universal joint attachment surface 71c is a surface parallel to the probe installation surface 71a, and one flange of the universal joint 85 described later is attached thereto.

  The rotation applying unit 75 includes a rotation shaft 77, a motor 76, and a pressing unit 79.

The rotary shaft 77 has a stepped cylindrical shape, and the main cylindrical portion 77a is rotatably supported by two rolling bearings 78 at two locations in the axial direction. The rotation shaft 77 has spline teeth 77 c extending in the axial direction on the outer periphery of the end portion on the side toward the rotation test apparatus 30. In addition, a stepped portion 77b having a smaller diameter than the main cylindrical portion 77a is formed on the outer periphery on the spline side from the main cylindrical portion 77a. A male screw is machined on the outer periphery of the stepped portion 77b. The rotation shaft 77 is coaxially formed with a communication hole 77d penetrating in the axial direction.
The rotation shaft 77 is connected to the rotation shaft of the motor 76 by a transmission belt or a gear, and rotates according to the rotation of the motor 76.

  The pressing portion 79 includes a movable plate 72, a fixed plate 74, a spring 86, and a universal joint 85.

  The movable plate 72 has a disc shape, and a universal joint mounting surface 72b for mounting the other flange of the universal joint 85 is formed on one side in the axial direction. On the other side in the axial direction of the movable plate 72, a spring receiving surface 72c for supporting the spring 86 in the axial direction is formed. The universal joint mounting surface 72b and the spring receiving surface 72c are both parallel to each other on a plane orthogonal to the axis. The movable plate 72 is coaxially provided with a hole penetrating in the axial direction. Spline teeth 72a extending in the axial direction are formed on the inner periphery of the hole. By engaging the spline teeth 72a with the spline teeth 77c formed on the rotating shaft 77, the movable plate 72 is fixed in the rotating direction with respect to the rotating shaft 77 and can move in the axial direction.

  The fixed plate 74 has a disc shape, and a spring receiving surface 74a for supporting the spring 86 in the axial direction is formed on one side in the axial direction. The spring receiving surface 74a is a plane orthogonal to the axis. A hole penetrating in the axial direction is provided coaxially in the fixed plate 74. A female screw is formed on the inner periphery of the hole. The fixing plate 74 is fixed to the rotating shaft 77 in the axial direction by screwing the female screw with a male screw formed on the step portion 77 b of the rotating shaft 77.

  A spring 86 is incorporated in a portion sandwiched between the movable plate 72 and the fixed plate 74 in the axial direction. The spring 86 is a compression coil spring and is incorporated coaxially with the rotating shaft 77.

  The contact plate 71 and the movable plate 72 are connected by a universal joint 85. For this reason, the contact plate 71 can be inclined in an arbitrary direction with the swing center of the universal joint 85 as a fulcrum. Thus, when the rotation applying unit 75 rotates, the contact plate 71 rotates in the circumferential direction.

  The rotation angle detection device 65 includes a sensor unit 65a and a pulse signal processing unit 65b. The sensor unit 65 a is formed by a rotary encoder fixed to the rotation shaft 77, an eddy current displacement sensor attached to a gear installed on the rotation shaft 77, or the like. Based on the pulse signal transmitted from the sensor unit 65a, the pulse signal processing unit 65b outputs a rotation angle signal V2 corresponding to the rotation angle of the rotation shaft 77. The rotation angle signal V 2 is transmitted to the signal processing device 67.

The ultrasonic device 60 includes a receiving / transmitting device 61 and a probe 62.
The receiving / transmitting device 61 includes a pulsar 61a that transmits an electric pulse to the probe 62, and a receiver 61b that receives an electric signal transmitted from the probe 62 and amplifies it.
The probe 62 includes an ultrasonic transmission unit and an ultrasonic reception unit that receives the reflected ultrasonic wave (hereinafter referred to as “echo”) when the transmitted ultrasonic wave is reflected from an object. It is configured. In the ultrasonic wave transmitting unit of the probe 62, the piezoelectric element is vibrated by the electric pulse signal transmitted from the pulsar 61 a of the ultrasonic device 60 and the ultrasonic wave is transmitted. When the probe 62 receives an echo, an output signal corresponding to the intensity of the received echo is transmitted to the receiver 61b of the transmission / reception device 61. The receiver 61b includes an amplifier, and outputs an echo signal V1 corresponding to the strength of the echo. The echo signal V1 is transmitted to the signal processing device 67.

  The probe 62 is mounted in the probe insertion hole 71b, and is mounted in a direction in which ultrasonic waves can be transmitted in a direction perpendicular to the probe installation surface 71a. The ultrasonic transmitter and ultrasonic receiver of the probe 62 are mounted at substantially the same position in the axial direction as the probe installation surface 71a. A clearance between the probe 62 and the inner peripheral surface of the probe insertion hole 71b is filled with a resin such as an epoxy resin. The signal line connected to the probe 62 is drawn out to the side of the universal joint mounting surface 71c through a small diameter hole. The signal line is connected to the transmission / reception device 61 through the communication hole 77 d of the rotating shaft 77.

  The signal processing device 67 outputs the relationship between the echo signal V1 and the rotation angle signal V2 based on the echo signal V1 corresponding to the echo intensity and the rotation angle signal V2 corresponding to the rotation angle of the rotation shaft 77. ing.

  Among the configurations of the posture detection device 70, a part of the rotation shaft 77 supported by the rolling bearing 78, the motor 76, the rotation angle detection device 65, the transmission / reception device 61 of the ultrasonic device 60, and the signal processing device 67. Are incorporated in one housing 90. A caster is attached to the bottom of the housing 90, and each of the above components can be moved as a unit.

  Next, a method for adjusting the attitude of the thrust roller bearing 10 and the fixed base 33 using the attitude detection device 70 will be described. At this time, since the inner ring support surface 32 of the fixed base 33 is inclined with respect to the outer ring support surface 51 of the rotating flange 58, the postures of the thrust roller bearing 10 and the fixed base 33 are inclined. The contact state between the thrust roller bearing 10 and the fixed base 33 will be described in three cases. The contact state in each case is defined as a first contact state, a second contact state, and a third contact state.

  FIG. 3 is a cross-sectional view showing an assembled state of the thrust roller bearing 10 incorporated in the rotation test apparatus 30 in the first contact state. In addition, the state in which ultrasonic waves propagate is schematically shown. In the following description, including the cases of the second contact state and the third contact state, the circumferential position of the thrust roller bearing 10 on the side where the outer ring support surface 51 and the inner ring support surface 32 are closest to each other in the axial direction. Is T1 (the upper side of the figure in FIG. 3), and the circumferential position on the side where the outer ring support surface 51 and the inner ring support surface 32 are farthest in the axial direction is T2 (the lower side of the figure in FIG. 180 degrees apart in the direction). In FIG. 3, the inclination of the inner ring support surface 32 is exaggerated for easy understanding of the description.

In the first contact state, the outer ring race portion 18 is in contact with the outer ring support surface 51 of the rotation flange 58 over the entire surface, and the inner ring support surface 32 of the fixed base 33 is inclined with respect to the inner ring race portion 13. The inner ring race portion 13 and the outer ring race portion 18 are parallel to each other, and sandwich the rollers 19 in the axial direction. The inner ring support surface 32 is in contact with the inner ring race portion 13 at the position T1, and is farthest from the inner ring race portion 13 in the axial direction at the position T2.
In the first contact state, “the attitude of the thrust roller bearing with respect to the fixed base” refers to an angle θ formed between the inner ring race portion 13 of the thrust roller bearing 10 and the inner ring support surface 32 of the fixed base 33. Assuming that the angle θ is not 0 °, a load is not equally applied to the rollers 19, and a phenomenon such as the rollers 19 skewing occurs. In this case, since the rotation test of the thrust roller bearing 10 cannot be accurately performed, it is necessary to adjust the posture of the fixed base 33 so that the angle θ is 0 °.

The adjustment of the posture of the fixed base 33 is performed according to the following procedure.
First step: The posture detection device 70 is moved to press the contact plate 71 against the fixed base 33. At this time, the contact medium 88 is filled between the contact plate 71 and the fixed base 33.
Second step: The probe 62 is rotated coaxially with the thrust roller bearing 10 while transmitting ultrasonic waves from the probe 62. The echo intensity is measured over the entire circumference. At the same time, the rotation angle of the rotation shaft 77 is measured.
Third step: The attitude of the fixed base 33 with respect to the raceway of the thrust roller bearing 10 is detected from the measurement results of the echo intensity and the rotation angle.
Fourth step: Based on the detection result, each adjustment mechanism 24 is adjusted so that the inclination of the fixed base 33 with respect to the raceway of the thrust roller bearing 10 becomes 0 °.

Each procedure will be specifically described with reference to FIGS.
In the first step, the rotation shaft 77 of the attitude detection device 70 is arranged so as to be coaxial with the main shaft 56 of the rotation test device 30. The attitude detection device 70 is moved to press the contact plate 71 against the fixed base 33. Since the contact plate 71 is supported by the universal joint 85, the direction of the contact plate 71 can be changed according to the direction of the detection surface 35 of the fixed base 33. The shield end surface 73a and the detection surface 35 are in close contact with each other over the entire circumference.
Further, when the housing 90 is moved toward the fixed base 33, the spline teeth 77 c slide and the rotating shaft 77 moves to the fixed base 33 side together with the fixed plate 74. At this time, since the spring 86 is compressed between the movable plate 72 and the fixed plate 74, the contact plate 71 is biased toward the detection surface 35 of the fixed base 33.

A liquid contact medium 88 is enclosed in a space radially inward of the shielding portion 73 between the fixed base 33 and the contact plate 71. As the contact medium 88, glycerin is preferably used. By filling the contact medium 88, the contact medium 88 connects the probe 62 and the detection surface 35 of the fixed base 33.
The contact plate 71 is supported by a universal joint 85. For this reason, even if the rotation axis 77 does not intersect the detection surface 35 at a right angle, the entire circumference of the shielding end surface 73a and the detection surface 35 is always in contact. Since both the shielding end surface 73a and the detection surface 35 are flat surfaces with small roughness, they are in close contact with each other over the entire circumference, and leakage of the contact medium 88 can be reliably prevented. Therefore, the contact medium 88 does not leak during the rotation of the rotating shaft 77.

In the second step, the probe 62 is turned in the circumferential direction. The rotating shaft 77 is rotated by a motor 76. The rotation speed is about one rotation per minute.
The distance in the radial direction from the turning center of the probe 62 is equal to the radius of the pitch circle of the roller 19. Therefore, the probe 62 is opposed to the roller 19 in the axial direction with the fixed base 33 interposed therebetween, and turns along the pitch circle of the roller 19.

Ultrasonic waves are transmitted from the probe 62. Ultrasound does not easily propagate in the air, but its strength does not easily decrease when propagating in a liquid substance. Since the probe 62 is in contact with the contact medium 88, the ultrasonic wave transmitted from the probe 62 into the contact medium 88 reaches the fixed base 33 without reducing its intensity. Further, since there is little reflection of ultrasonic waves at the interface between the contact medium 88 and the fixed base 33, the ultrasonic waves transmitted from the probe 62 are surely transmitted through the fixed base 33.
Similarly, an echo transmitted from the fixed base 33 side toward the probe 62 is transmitted into the contact medium 88 and reaches the probe 62 without reducing its intensity. The probe 62 outputs an echo signal from the transmission / reception device 61 according to the received echo intensity.

  Simultaneously with measuring the echo intensity, the rotation angle of the rotation shaft 77 is measured. When the rotating shaft 77 rotates, pulses are transmitted from the sensor unit 65a at predetermined intervals. Since the number of pulses per rotation is set in advance, the rotation angle of the probe 62 can be measured by counting the number of pulses from the sensor unit 65a.

  In the third step, the attitude of the fixed base 33 with respect to the raceway is detected based on the result measured in the second step. FIG. 4 is a graph showing the results measured in the second step. In FIG. 4, the horizontal axis indicates the circumferential position of the probe 62, and the vertical axis indicates the echo intensity at each position. The circumferential position is represented by a clockwise rotation angle when viewed from the direction of arrow A, with 0 ° when the probe 62 is at the position T2 in FIG.

The measurement results in FIG. 4 will be described with reference to FIG.
At the position T1 (the circumferential position of the probe is 180 °), the fixed base 33 and the rotary flange 58 are in contact with each other via the thrust roller bearing 10. For this reason, at the position T1, the ultrasonic wave W1 transmitted from the probe 62 is transmitted toward the rotary flange 58 (ultrasonic wave W2). For this reason, the intensity of the echo 1 at the position T1 is reduced. In FIG. 4, it is the echo intensity of P4.
When the probe 62 turns in the clockwise direction and is displaced toward the adjacent roller 19, the roller 19 does not exist in the traveling direction of the ultrasonic wave W1, so the ultrasonic wave W1 is transmitted between the inner ring race portion 13 and the outer ring. It is difficult for the clearance between the race portion 18 to pass through. Since the ultrasonic wave W1 is reflected on the surface of the inner race portion 13 on the rolling surface side, the intensity of the echo 1 is increased. In FIG. 4, it is the echo intensity of Q4.
When the probe 62 further turns in the clockwise direction and faces the adjacent roller 19, the ultrasonic wave W1 is transmitted toward the rotary flange 58, so that the intensity of the ultrasonic wave W2 increases again, The intensity of the echo 1 is reduced. In FIG. 4, it is the echo intensity of P5.

Thus, in FIG. 4, the echo intensity when the probe 62 is turned has a minimum value at a position where the probe 62 faces the roller 19 in the axial direction. In FIG. 4, the points where the echo intensity is minimized are indicated by points P0 to P8. However, in the position of the roller 19 adjacent to the position T1, the axial clearance between the fixed base 33 and the inner ring race portion 13 is larger than the position of T1. For this reason, the intensity of the ultrasonic wave W2 that passes through the gap decreases, and the intensity of the echo 1 reflected by the inner ring support surface 32 increases. As a result, the echo intensity (P5) at the position of the adjacent roller 19 is higher than the echo intensity (P4) at the position T1.
When the probe 62 further turns and faces the roller 19 at the position T2 (the circumferential position of the probe is 360 °), the axial clearance between the fixed base 33 and the inner ring race portion 13 is maximized. . For this reason, the intensity of the ultrasonic wave W2 that passes through the gap is minimized, and most of the ultrasonic wave W1 is reflected by the inner ring support surface 32. For this reason, the intensity of the echo 1 is increased. In FIG. 4, the echo intensity is P8.

  A curve connecting the minimum point P0 to the minimum point P8 in sequence (the curve indicated by a broken line in FIG. 4) is minimum at a circumferential position of 180 ° (position T1 in FIG. 3). Thereby, it can be known that the inner ring support surface 32 and the inner ring race portion 13 are closest to each other at the position T1. Since the minimum value increases as the circumferential position increases or decreases from the position P4, it can be known that the inner ring support surface 32 and the inner ring race portion 13 are separated from each other. From this measurement result, it can be known that the fixed base 33 is inclined in a direction approaching the thrust roller bearing 10 at a position T1 in FIG.

  In the fourth step, each adjustment mechanism 24 is adjusted based on the detection result so that the inclination of the fixed base 33 with respect to the raceway of the thrust roller bearing 10 becomes 0 °. Specifically, the sleeve 24c is rotated around the screw shaft so that the adjusting mechanism 24 close to the position T1 extends and the adjusting mechanism 24 close to the position T2 contracts. In this way, adjustment can be made so that the inclination of the fixed base 33 with respect to the raceway of the thrust roller bearing 10 becomes 0 °.

Next, a method of adjusting the posture of the fixed base 33 in the second contact state will be described with reference to FIG. FIG. 5 is a cross-sectional view showing an assembled state of the thrust roller bearing 10 at the position T2 in the second contact state. In addition, a state in which ultrasonic waves propagate is schematically shown.
The second contact state differs from the first contact state in that the inner race portion 13 is in contact with the inner race support surface 32 of the fixed base 33 over the entire circumference. The outer race portion 18 is in contact with the outer race support surface 51 of the rotary flange 58 over the entire surface. The inner race part 13 and the outer race part 18 are inclined with respect to each other. The rollers 19 are clamped in the axial direction by the inner race portion 13 and the outer race portion 18.
In the second contact state, “the posture of the thrust roller bearing with respect to the fixed base” refers to the angle θ formed by the inner race portion 13 and the outer race portion 18 of the thrust roller bearing 10.

  The method for adjusting the posture of the fixed base 33 in the second contact state differs from the first contact state only in the third step. Hereinafter, the third step will be described. The circumferential direction position of the probe 62 and the result of measuring the echo intensity at each position are the same as the measurement result of the first contact state, and will be described with reference to FIG.

  In the second contact state, the fixed base 33 and the rotary flange 58 are in contact with each other via the outer race part 18, the inner race part 13, and the rollers 19 at the position T <b> 1. For this reason, since the behavior of the ultrasonic wave when the probe 62 is at the position T1 is the same as that in the first contact state, the description thereof is omitted.

At the position T2, an axial clearance δ1 is provided between the roller 19 and the inner race portion 13, and an axial clearance δ2 is provided between the roller 19 and the outer race portion 18.
A part of the ultrasonic wave W3 incident on the inner race part 13 is transmitted through the clearance δ1 and propagates to the roller 19 as an ultrasonic wave W4 (W4 <W3), and is reflected on the surface of the inner race part 13 on the roller 19 side. Returns “echo 2”.
The ultrasonic wave W4 propagates inside the roller 19 and reaches the surface of the roller 19 on the outer race side. A portion of the ultrasonic wave W4 passes through the gap δ2 and propagates as an ultrasonic wave W5 (W5 <W4) to the outer ring race 18 and is reflected by the surface of the roller 19 on the outer ring race side to return “echo 3”. .

The sizes of δ1 and δ2 vary depending on the axial position of the roller 19 between the inner race portion 13 and the outer race portion 18. When δ1> δ2, the ultrasonic wave transmitted through the gap δ1 is small, so that echo 2> echo 3 is satisfied, and when δ1 <δ2, echo 2 <echo 3 is satisfied. Since the probe 62 measures the echo 2 and the echo 3 simultaneously, the measured echo intensity is the sum of the intensity of the echo 2 and the intensity of the echo 3. Therefore, almost the same echo intensity can be measured regardless of the position of the roller 19.
When the sum of the gaps (δ1 + δ2) is large, the echo intensity naturally increases. Therefore, the minimum value increases as the distance between the inner race part 13 and the outer race part 18 increases in the axial direction.

  Therefore, the curve that sequentially connects the minimum point P0 to the minimum point P8 is minimum at 180 ° (position T1) in the circumferential position. Thereby, it can be known that the outer race part 18 and the inner race part 13 are closest to each other at the position T1. Since the minimum value P8 (or P0) becomes large at the position T2, it can be known that the outer race part 18 and the inner race part 13 are most separated from each other. From this measurement result, it can be known that the fixed base 33 is inclined in a direction approaching the thrust roller bearing 10 at a position T1 in FIG.

  Next, a method for adjusting the posture of the fixed base 33 in the third contact state will be described with reference to FIGS. FIG. 6 is an axial cross-sectional view at a position T1 for explaining the assembled state of the thrust roller bearing 10 in the third contact state. FIG. 7 is a side view of the contact surface between the roller 19 and the inner race part 13 as viewed in the X direction. FIG. 6 schematically shows a state in which ultrasonic waves propagate. In FIG. 7, the example of the shape of the elastic contact area | region in the contact part of the roller 19 and the inner ring race part 13 is shown.

In the third contact state, the outer race part 18 and the inner race part 13 are in contact with the respective rollers 19 over the entire circumference, but the rotating flange 58 and the fixed base 33 are inclined to each other. The load distribution acting on each roller 19 is different. When the thrust roller bearing 10 receives a load, the contact point between the roller 19 and each of the race portions 13 and 18 is elastically deformed to form an elastic contact region having a certain spread (in FIG. The attached area). The size of the elastic contact area increases as the load increases.
In the third contact state, the “posture of the thrust roller bearing with respect to the fixed base” refers to an angle θ formed by the inner race portion 13 and the outer race portion 18 of the thrust roller bearing 10.

  The method for adjusting the posture of the fixed base 33 in the third contact state differs from the first and second contact states only in the third step. Hereinafter, the third step will be described.

  When the ultrasonic wave W6 incident on the inner race part 13 propagates through the inner race part 13 and enters the roller 19 (referred to as ultrasonic wave W7), a part of the ultrasonic wave W6 is reflected to become an echo 4. Further, even when the ultrasonic wave W 7 propagates through the roller 19 and enters the outer ring race portion 18 (referred to as an ultrasonic wave W 8), a part of the ultrasonic wave W 7 is reflected and becomes the echo 5. However, since each race part 19 is in contact, the intensity of the echo 4 or the echo 5 is extremely small.

  When the elastic contact area between the roller 19 and each of the race portions 13 and 18 is large, the ultrasonic waves W6 and W7 are easily transmitted, so that the echo intensity generated in the elastic contact area is small. When the elastic contact area is small, the echo intensity increases. Therefore, when the axial distance between the fixed base 33 and the rotary flange 58 at the position T1 is compared with the axial distance between the fixed base 33 and the rotary flange 58 at the position T2, the position T1 is closer. The contact load increases as the position approaches T1. As a result, the elastic contact area expands as it approaches the position T1, so that the echo intensity decreases. Similar to the first and second contact states, when the roller 19 does not exist in the traveling direction of the ultrasonic wave, the echo intensity increases.

  Thus, when the echo intensity is measured by turning the probe 62 in the circumferential direction, the echo intensity takes a minimum value at the position facing the roller 19. The minimum value is the smallest at the position T1 (the circumferential position is 180 °) and the largest at the position T2 (the circumferential position is 0 ° or 360 °). From this measurement result, it can be known that the fixed base 33 is inclined in the direction approaching the thrust roller bearing 10 at the position T1.

  As can be understood from the description of the third contact state, the echo intensity changes depending on the size of the elastic contact region between the roller 19 and each race portion. Therefore, it is appropriate that the size of the ultrasonic wave transmitting portion of the probe 62 is the same size as the shape when the roller 19 is projected in the axial direction. With this size, even when the elastic contact region is wide or narrow, an ultrasonic wave can be transmitted to the entire elastic contact region, and an echo from the elastic contact region can be reliably captured. On the other hand, when the size of the ultrasonic transmission unit is too large, ultrasonic waves are transmitted to a region other than the elastic contact region. At this time, since many areas where ultrasonic waves are not transmitted are included, the echo intensity increases as a whole, and it becomes difficult to detect a change in the echo intensity.

As described above, in the rotation test apparatus 30 using the thrust roller bearing assembly surface orientation adjusting apparatus 70 according to the embodiment of the present invention, the fixed base 33 and the thrust roller are interposed via the metal fixed base 33. The postures of the bearings 10 can be set parallel to each other.
In this way, when assembling the thrust bearing in a rotation test apparatus or the like, it is possible to detect the attitude of the support member and the thrust bearing without changing the material of the raceway ring without changing the original steel material.

  In the description of the present embodiment, the thrust roller bearing 10 has been described by taking a shell-integrated thrust roller bearing in which the inner and outer rings are combined as an example. However, the measurement object of the thrust bearing assembly surface adjusting device of the present invention is not limited to this. For example, the present invention can also be applied to a so-called cage-and-roller type thrust roller bearing in which a cage is simply combined. In the present embodiment, the case where the rolling elements are rollers has been described as an example. However, even if the rolling element is a ball, a tapered roller, a needle roller or the like, the same measurement can be performed.

10: Thrust roller bearing, 11: Cage, 12: Pocket part, 13: Inner ring race part, 14: Inner ring, 15: Inner flange, 17: Outer ring, 18: Outer ring race part, 19: Roller (rolling element), 20 : Outer flange, 24: adjustment mechanism, 30: rotation test device, 32: inner ring support surface, 33: fixed base (support member), 34: convex portion, 34a: inner ring guide surface, 35: detection surface, 50: rotation portion 51: outer ring support surface, 52: outer ring guide portion, 52a: outer ring guide surface, 56: main shaft, 58: rotating flange, 60: ultrasonic device, 61: transmitter / receiver device, 62: probe, 65: rotation angle Detection device, 67: Signal processing device, 70: Assembly surface posture detection device, 71: Contact plate (rotating member), 71a: Probe installation surface, 72: Movable plate, 73: Shielding part, 73a: Shielding end surface, 74: fixed plate, 75: times Applying section, 76: Motor, 77: rotary shaft, 78: rolling bearing, 79: pressing portion 85: universal joint 86: spring, 88: couplant, 90: casing

Claims (2)

A thrust bearing assembly comprising a thrust bearing having rolling elements arranged at predetermined intervals in the circumferential direction and a support member for supporting the thrust bearing in the axial direction, and the support member and the thrust bearing. An assembly surface attitude detection device for a thrust bearing for detecting an attitude,
A rotating member that is disposed at a position facing the thrust bearing in the axial direction across the support member, and rotates coaxially with the thrust bearing;
A rotation angle detecting device for detecting a rotation angle of the rotating member;
An ultrasonic device having a probe capable of transmitting ultrasonic waves and receiving echoes;
A signal processing device,
The probe is attached to the rotating member at a position where an ultrasonic wave is irradiated toward the rolling element across the support member,
The signal processing device includes: a rotation angle signal from the rotation angle detection device; and an echo signal from the ultrasonic device when the ultrasonic wave is irradiated toward the thrust bearing while rotating the rotating member. Originally, the relationship between the rotation angle signal and the echo signal is output.
Thrust bearing assembly surface attitude detector. A thrust bearing assembly surface orientation detection method for detecting the orientation of the support member and the thrust bearing using the thrust bearing assembly surface orientation detection device according to claim 1,
Arranging the rotating member at a position facing the thrust bearing in the axial direction across the support member; and
A second step of simultaneously measuring the echo signal and the rotation angle by rotating the probe together with the rotating member coaxially with the thrust bearing while transmitting ultrasonic waves toward the rolling element; Detecting a posture of the support member and the thrust bearing from a change of the echo signal with respect to a rotation angle based on the echo signal and the rotation angle signal;
A method for detecting the posture of an assembled surface of a thrust bearing.

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