JP5347391B2 - Measuring method of preload amount of bearing device and assembling method of bearing device - Google Patents

Description

  The present invention relates to a method for assembling a bearing device that rotatably supports an axle attached to a vehicle body of a vehicle, and more particularly to a method for measuring a preload amount of a bearing device.

  As the bearing device, there is known a rolling bearing device including a rotating body that rotates together with the axle, a fixed body that is attached to the vehicle body and surrounds the rotating body, and a rolling element that is disposed between the rotating body and the fixed body. It has been. In general, in a rolling bearing device, for the purpose of ensuring the accuracy of the axial gap and the radial gap between the rotating body and the stationary body, and suppressing vibration and noise in the axial direction, the rotating body and the stationary body are used. A preload is applied to the rolling elements.

  In addition, when managing the preload amount indicating the magnitude of the preload of the rolling bearing device, when assembling the rolling bearing device, the vibration applying device applies vibration to the rolling bearing device and the vibration applied to the rolling bearing device. It has been performed by detecting and estimating the amount of preload from the natural frequency of the rolling bearing device calculated based on the detection result (see, for example, Patent Document 1).

Here, with reference to FIG. 9, the measuring method of the amount of preload of the conventional rolling bearing apparatus is demonstrated.
As shown in FIG. 9, the rolling bearing device 100 includes a hub shaft 101 that rotatably supports an axle, an inner ring member 102 fixed to the hub shaft 101, an outer ring member 103 that surrounds the inner ring member 102, a hub It is comprised by the rolling element 104 arrange | positioned between each of the shaft 101 and the inner ring member 102, and the outer ring member 103. A screw portion 101 a is provided on the upper side in the axial direction of the hub shaft 101. A nut 105 is screwed to the threaded portion 101a so as to sandwich the inner ring member 102 in the axial direction.

  The measuring device AR that measures the amount of preload of the rolling bearing device 100 includes a jig 110 on which the rolling bearing device 100 is mounted, an exciter 120 that applies axial vibration to the rolling bearing device 100, and the rolling bearing device 100. A vibration detection unit 130 that detects vibration and an arithmetic processing unit 140 that calculates a natural frequency from information detected by the vibration detection unit 130 are configured.

  The vibrator 120 vibrates so as to sweep from the lower limit to the upper limit of a predetermined measurement frequency band, and applies vibration to the rolling bearing device 100. That is, in the rolling bearing device 100, vibration in the longitudinal vibration mode that is the vibration mode in the axial direction of the rolling bearing device 100 is mainly applied by the vibrator 120.

  The vibration detection unit 130 monitors the vibration of the rolling bearing device 100 by the vibration detection sensor 131 attached to the outer ring member 103 and the screw portion 101a. That is, the vibration detection sensor 131 outputs a signal corresponding to the vibration of the rolling bearing device 100. This output signal passes through the addition amplifier 132, the main amplifier 133, and the high-pass filter 134, and is input to the arithmetic processing unit 140.

The arithmetic processing unit 140 is in order of a transfer function computing device 141 that obtains a vibration mode of the natural frequency, a stiffness conversion computing device 142 that calculates the bearing stiffness from the natural frequency, and a preload computing device 143 that calculates the preload amount from the bearing stiffness. After passing the output signal from the vibration detection sensor 131, the preload amount as the calculation result of the preload calculation device 143 is displayed on the display unit 144.
JP 2000-74788 A

  By the way, in the measurement of the preload amount, due to the tolerance of the contact angle between the hub shaft 101, the inner ring member 102, and the outer ring member 103 and the rolling element 104, the natural frequency varies.

  In the conventional measuring apparatus AR, since the variation of the natural frequency obtained by the transfer function calculation device 141 is particularly large, the preload amount finally obtained based on the natural frequency is also relatively large. Therefore, it is difficult to sufficiently increase the accuracy in managing the preload amount due to variations in the preload amount.

Accordingly, the present invention has been made in view of the above circumstances, and the object of the present invention is to provide a preload for a bearing device that can suppress variations in the natural frequency and improve the accuracy in managing the preload amount. It is an object to provide a method for measuring a quantity and a method for assembling a bearing device.

  (1) One form of this measurement method has the following matters. This measurement method is a method for measuring a preload amount of a bearing device, and the bearing device includes a rotating body, a fixed body, and a rolling element, the rotating body rotates together with an axle, and the fixed body is The rotating body is enclosed, and the rolling element is disposed between the rotating body and the fixed body in a radial direction of the rotating body, and a preload is applied by the rotating body and the fixed body, and the measurement method includes: , Measuring step A, measuring step B, and measuring step C, wherein the measuring step A applies vibration to the bearing device by a vibrating means, and the measuring step B includes the bearing device by the vibrating means. The vibration applied to is detected by the detection means, and the natural frequency of the bending vibration mode of the bearing device is calculated based on the detection result of the detection means. The measurement step C is calculated in the measurement step B. The bending vibration mode The calculated value of the vibration frequency is included in a threshold region defined by the negative gap amount in the relationship between the preset natural frequency of the bending vibration mode of the bearing device and the negative gap amount of the bearing device. Based on this, it is determined that the amount of preload applied to the rolling element is within an appropriate range.
  (2) One form of the measuring method has the following matters. The relationship between the preset natural frequency of the bending vibration mode of the bearing device and the negative gap amount of the bearing device is the curve of the natural frequency of the bending vibration mode, the upper limit value of the negative gap amount, and the negative gap. An area between the natural frequency on the curve corresponding to the upper limit value of the negative gap amount and the natural frequency on the curve corresponding to the lower limit value of the negative gap amount. It is defined as a threshold area.
  (3) One form of the measuring method has the following matters. In the measurement step A, a hammering device is used as the vibration means.
  (4) One form of the measuring method has the following matters. In the measurement step B, a non-contact type sensor is used as the detection means.
  (5) One form of this assembly method has the following matters. This assembling method is an assembling method of the bearing device, and the assembling method includes a first step and a second step, and the first step uses the rotating body, the fixed body, and the rolling element. The said 2nd process has the said measurement process A, the said measurement process B, and the said measurement process C as described in any one of Claims 1-4.

  According to the inventor of the present application, the variation in the natural frequency in the bending vibration mode and the variation in the natural frequency in the longitudinal vibration mode were compared, and it was confirmed that the variation in the natural frequency in the bending vibration mode was smaller. Has been. This is considered because the natural frequency of the bending vibration mode is not easily affected by the tolerance of the contact angle. In view of these facts, the invention described above calculates the natural frequency of the bending vibration mode when measuring the amount of preload, so it is compared with the method for measuring the amount of preload of the conventional rolling bearing device shown in FIG. Thus, it is possible to improve the accuracy in managing the preload amount by suppressing variations in the natural frequency.

  ADVANTAGE OF THE INVENTION According to this invention, the assembly method of the bearing apparatus which can suppress the dispersion | variation in a natural frequency and can improve the precision concerning management of a preload amount can be provided.

  1 to 8, an embodiment of the bearing device assembling method according to the present invention is embodied as a method of assembling a rolling bearing device that is attached to a vehicle body and a wheel of a vehicle and supports an axle rotatably. explain.

  Further, hereinafter, the direction along the central axis of the rolling bearing device is referred to as “axial direction”, the direction orthogonal to the central axis of the rolling bearing device is referred to as “radial direction”, and the direction in which the rotating body rotates is referred to as “circumferential direction”. "

First, with reference to FIG. 1, the rolling bearing apparatus 1 of this embodiment is demonstrated.
As shown in FIG. 1, a rolling bearing device 1 is attached to a wheel and rotates together with an axle, a rotating body 2 attached to a vehicle body, a fixed body 3 surrounding the rotating body 2, and a radial direction. It is comprised by the holder | retainer 5 arrange | positioned in the space between the rotary body 2 and the fixed body 3, and the some rolling element 4 hold | maintained by the holder | retainer 5, respectively. Then, the rotating body 2 can rotate about the central axis with respect to the fixed body 3 via the rolling elements 4.

  The rotating body 2 includes a cylindrical portion 21 provided along the axial direction, a flange portion 22 extending outward from the cylindrical portion 21 in the radial direction, and a vehicle body side in the axial direction of the cylindrical portion 21. A fixed inner ring 24 is provided. The flange portion 22 is fixed to the vehicle wheel by a bolt. Further, in the radial direction, a substantially cylindrical inlay portion 23 extending from the flange portion 22 toward the vehicle outer side in the axial direction is provided inside the flange portion 22. The inlay portion 23 is fitted to the wheel of the wheel. The inner ring 24 is fixed to the upper end portion 21b of the cylindrical portion 21 by caulking. The inner ring 24 is provided with a vehicle body side raceway groove 24a in which the rolling element 4 is slidably contacted with the lubricating oil. Further, on the vehicle outer side in the axial direction of the cylindrical portion 21, a vehicle outer side track groove 21 a is provided in which the rolling element 4 is in sliding contact with the lubricating oil.

  The fixed body 3 is provided with a cylindrical portion 31 that surrounds the cylindrical portion 21 of the rotating body 2 and a flange portion 32 that extends outward from the cylindrical portion 31 in the radial direction. The flange portion 32 is provided with a through hole 32a for fixing a bolt. And the fixed body 3 is fixed with respect to a vehicle body, when the knuckle connected with a vehicle body is fixed to the flange part 32 with a volt | bolt. In the circumferential direction, four flange portions 32 are provided with a certain distance. A vehicle body side raceway groove 31 a and a vehicle exterior raceway groove 31 b are provided on the inner peripheral surface of the cylindrical portion 31 (that is, the inner surface of the cylindrical portion 31 in the radial direction).

  The cage 5 is provided in the space formed between the outer peripheral surface of the cylindrical portion 21 of the rotating body 2, that is, the outer surface of the cylindrical portion 21 in the radial direction and the inner peripheral surface of the cylindrical portion 31. Is provided in a manner corresponding to the vehicle body side track grooves 24a and 31a and the vehicle outer side track grooves 21a and 31b. That is, the rolling element 4 is in contact with the inner ring 24 and the fixed body 3 via the lubricating oil between the vehicle body side track groove 24a of the rotating body 2 and the vehicle body side track groove 31a of the fixed body 3. Has been placed. Further, between the outer raceway groove 21a of the rotating body 2 and the outer raceway groove 31b of the fixed body 3, the rolling element 4 is in contact with each of the cylindrical portion 21 and the fixed body 3 via lubricating oil. Is arranged. Each rolling element 4 is preloaded by the rotating body 2 and the fixed body 3 in a state where the cylindrical portion 21 and the inner ring 24 are caulked.

  In the radial direction, between the rotating body 2 and the fixed body 3, a vehicle outer side seal 6 and a vehicle body that are seals that suppress entry of dust and muddy water from the space outside the rolling bearing device 1 toward the rolling element 4. Side seals 7 are respectively provided. That is, the vehicle outer side seal 6 is provided on the vehicle outer side from the vehicle outer side raceway grooves 21a and 31b in the axial direction, and the vehicle body side seal 7 is provided on the vehicle body side from the vehicle body side raceway grooves 24a and 31a in the axial direction. Yes.

Next, with reference to FIG. 2 and FIG. 3, the structure of the preload amount measuring device A of the rolling bearing device will be described.
As shown in FIG. 2, the measuring apparatus A includes a jig 8 for placing the rolling bearing device 1, a vibration unit 9 for applying vibration to the rolling bearing device 1 placed on the jig 8, and vibration. Calculation detection for determining whether the preload amount of the rolling bearing device 1 is appropriate based on the vibration detection unit 10 for detecting the vibration of the rolling bearing device 1 applied by the unit 9 and the output signal of the vibration detection unit 10 Part 11.

  The jig 8 is a flat plate member made of an elastic member that absorbs vibration of the rolling bearing device 1 such as a rubber sheet. Then, the rolling bearing device 1 is placed on the jig 8 so that the end portion 23a on the vehicle exterior side of the spigot portion 23 of the rotating body 2 contacts the surface 8a on the vehicle body side in the axial direction of the jig 8. Is done.

  The vibration unit 9 is disposed on the vehicle body side with respect to the flange portion 32 of the fixed body 3 of the rolling bearing device 1 in the axial direction, and gives vibration to the rolling bearing device 1 by giving an impact to the flange portion 32. . That is, hammering is performed on the fixed body 3.

Here, with reference to FIG. 3, the detailed structure of the vibration part 9 is demonstrated.
As shown in FIG. 3, the vibration unit 9 includes a direct acting electromagnetic solenoid (hereinafter simply referred to as “solenoid 9a”) and a frame 9b that fixes and supports the solenoid 9a. The solenoid 9a has a hollow cylindrical fixed iron core 9c fixed to the frame 9b, a coil 9d formed by winding a conductive wire around the fixed iron core 9c, and a substantially columnar movable that is reciprocating with respect to the fixed iron core 9c. It is comprised by the iron core 9e. An elastic member 9g such as a coil spring that connects the frame 9b and the movable iron core 9e is disposed at the end 9f on the vehicle body side in the axial direction of the movable iron core 9e. Further, a hammer 9h for applying an impact to the flange portion 32 is fixed to the end of the movable iron core 9e on the vehicle outer side in the axial direction. The elastic member 9g urges the hammer 9h away from the flange portion 32 (that is, the vehicle body side in the axial direction in FIG. 3). As a result, when the coil 9d is not energized, the movable iron core 9e is held at the initial set position, that is, at a position that has passed a predetermined interval in the axial direction with respect to the flange portion 32 by the force of the elastic member 9g.

The application of impact to the flange portion 32 is performed as follows.
First, the coil 9d is energized. Thereby, the movable iron core 9e moves linearly along the axial direction from the initial setting position toward the flange portion 32 against the urging force of the elastic member 9g. Then, the hammer 9h collides with the flange portion 32 (two-dot chain line hammer 9h in FIG. 3), and an impact is applied to the flange portion 32. Thereafter, when the coil 9d is de-energized, the movable core 9e is moved away from the flange portion 32 (that is, the vehicle body side in the axial direction in FIG. 3) by the biasing force of the elastic member 9g. The movable iron core 9e is again held at the initial setting position.

  Here, since the measuring device A measures the preload amount based on the bending vibration mode of the rolling bearing device 1, the vibration of the bending vibration mode appears more noticeably when the hammer 9h applies the impact to the flange portion 32. It is desirable to be performed as follows. Therefore, the collision position of the hammer 9h with respect to the flange portion 32 is set to a portion of the flange portion 32 that is radially outside the through hole 32a (hereinafter referred to as “outer portion”).

Moreover, with reference to FIG. 2, the structure of the vibration detection part 10 and the calculation determination part 11 is demonstrated.
As shown in FIG. 2, in the axial direction, the vibration detection unit 10 is disposed so as to face the flange portion 32 of the fixed body 3, and is disposed away from the flange portion 32 in the axial direction. It is a contact type sensor. The vibration detection unit 10 uses a laser Doppler vibrometer. The vibration detection unit 10 detects the vibration applied to the rolling bearing device 1 by the vibration means 9 and transmits the detected vibration to the calculation determination unit 11 as an output signal.

  The calculation determination unit 11 includes a calculation unit 11a that decomposes the output signal from the vibration detection unit 10 for each frequency, and a determination unit 11b that compares the threshold frequency region of the natural frequency of the bending vibration mode of the fixed body 3. . The computing unit 11a includes a fast Fourier transform (FFT) as an analyzer. In addition, the determination unit 11b performs preloading based on the natural frequency of the bending vibration mode of the fixed body 3 obtained from the calculation unit 11a and the threshold region of the natural frequency of the bending vibration mode of the fixed body 3 set in advance. Determine if the amount is appropriate. This threshold region is preset as a region between the upper limit value and the lower limit value of the natural frequency of the bending vibration mode of the fixed body 3. Further, the upper limit value and the lower limit value of the natural frequency are set in advance based on the upper limit value and the lower limit value of the negative clearance amount (hereinafter simply referred to as “negative clearance amount”) of the rolling bearing device 1.

  Here, the negative gap amount is based on the value of the difference in the axial direction between the positions of the vehicle body side track grooves 24a and 31a that respectively contact the rolling element 4 in a state after the cylindrical portion 21 and the inner ring 24 are caulked. The amount obtained by subtracting the value of the difference in the axial direction between the rolling element 4 and the positions of the vehicle body side raceway grooves 24a and 31a before the cylindrical portion 21 and the inner ring 24 are crimped. That is, the axial distance between the contact position of the rolling element 4 and the vehicle body side raceway groove 24a and the contact position of the rolling element 4 and the vehicle body side raceway groove 31a, from the distance after caulking the cylindrical portion 21 and the inner ring 24. This corresponds to an amount obtained by reducing the distance before the cylindrical portion 21 and the inner ring 24 are caulked. In other words, the negative gap amount is based on the value of the axial difference between the positions of the vehicle body side raceways 24a and 31a that respectively contact the rolling element 4 in a state after the preload is applied to the rolling element 4. In addition, it can be a value obtained by subtracting the difference in the axial direction between the rolling element 4 and the positions of the vehicle body side raceway grooves 24a and 31a in a state before the preload is applied to the rolling element 4.

Next, with reference to FIG. 4 and FIG. 5, the difference between the determination method of the preload amount of the rolling bearing device of this embodiment and the determination method of the preload amount of the conventional rolling bearing device will be described.
4 and 5 show the relationship between the natural frequency and the negative gap amount in the bending vibration mode (FIG. 4) and the longitudinal vibration mode (FIG. 5) of the fixed body 3 from the three-dimensional model of the rolling bearing device 1. FIG. It is the result of having analyzed the upper limit value and lower limit value of the total of the contact angle and curvature tolerance between the rolling element 4 and the rotating body 2, the inner ring 24, and the fixed body 3 by the finite element method.

  As shown in FIG. 4, for example, at the point where the negative gap amount is −35 μm, the natural frequency and the bending vibration of the upper limit value curve of the bending vibration mode (hereinafter simply referred to as “upper limit curve A1”). The difference R1 between the natural frequency of the mode and the lower limit curve (hereinafter simply referred to as “lower limit curve B1”) is about 40 Hz. Then, on the lower limit curve B1, the amount of negative gap that provides the same natural frequency as the upper limit curve A1 at the above point is a point of about −44 μm. Therefore, at the natural frequency of the same bending vibration mode, the difference D1 between the negative gap amount in the upper limit curve A1 and the negative gap amount in the lower limit curve B1 is about 9 μm.

  On the other hand, as shown in FIG. 5, similarly, at the point where the negative gap amount is −35 μm, the natural frequency in the curve of the upper limit value of the natural frequency in the longitudinal vibration mode (hereinafter referred to as “upper limit curve A2”) and The difference R2 from the natural frequency in the lower limit curve (hereinafter referred to as “lower limit curve B2”) of the natural frequency of the bending vibration mode is about 500 Hz. Then, on the lower limit curve B2, the negative gap amount at which the same natural frequency as that of the upper limit curve A2 at the above point is obtained is a point of about −65 μm. Therefore, at the natural frequency of the same longitudinal vibration mode, the difference D2 between the negative gap amount in the upper limit curve A2 and the negative gap amount in the lower limit curve B2 is about 30 μm.

  Thus, between the bending vibration mode and the longitudinal vibration mode, the differences R1 and R2 between the natural frequency on the upper limit curve and the natural frequency on the lower limit curve in the same negative gap amount are different from each other. That is, in the case exemplified above, the bending vibration mode is about 40 Hz (R1 in FIG. 4), whereas the longitudinal vibration mode is about 500 Hz (R2 in FIG. 5). Indicates a small value.

  Further, the differences D1 and D2 between the negative clearance amount of the upper limit curve and the negative clearance amount of the lower limit curve at the same natural frequency are also different from each other. That is, in the case exemplified above, the bending vibration mode is about 9 μm (D1 in FIG. 4), whereas the longitudinal vibration mode is about 30 μm (D2 in FIG. 5). Indicates a smaller value.

  Therefore, according to the method for measuring the preload amount of the rolling bearing device 1 using the bending vibration mode of the present embodiment, as compared with the method for measuring the preload amount of the rolling bearing device using the conventional longitudinal vibration mode, an arbitrary Because the variation in the amount of negative clearance relative to the natural frequency is small, that is, the amount of variation in the preload amount of the rolling bearing device estimated from the amount of negative clearance is small, the preload amount of the rolling bearing device can be measured with high accuracy. .

  Next, referring to FIG. 2 and FIG. 9, the difference between the vibration applying method in the method for measuring the preload amount of the rolling bearing device of the present embodiment and the vibration applying method in the method for measuring the preload amount of the conventional rolling bearing device. explain.

  As shown in FIG. 9, in the conventional method for measuring the preload amount of the rolling bearing device 100, the vibrator 120 vibrates so as to sweep from the lower limit to the upper limit of the measurement frequency band, and the rolling bearing device 100 is vibrated. Give. That is, the vibrator 120 detects the resonance frequency with the natural frequency of the outer ring member 103 by changing the frequency of vibration applied to the rolling bearing device 100.

  On the other hand, as shown in FIG. 2, in the method for measuring the preload amount of the rolling bearing device 1 according to the present embodiment, the vibration exciter 120 only impacts the flange portion 32 of the fixed body 3 once, and the fixed body 3. The natural frequency of the bending vibration mode is detected. Therefore, compared with the conventional method for measuring the amount of preload of the rolling bearing device 100, the method for measuring the amount of preload of the rolling bearing device 1 according to the present invention determines whether or not the amount of preload of the rolling bearing device is appropriate. Time can be shortened. As a result, the production efficiency of the rolling bearing device 1 can be improved as compared with the conventional rolling bearing device 100. In addition, the vibration time of the vibration unit 9 in the method for measuring the preload amount of the rolling bearing device 1 according to the present invention is the time of vibration of the vibrator 120 in the method of measuring the preload amount of the conventional rolling bearing device 100. Compared to the above, since it is short, the formation of scratches due to vibrations of the rolling body 4 and the rotating body 2, the inner ring 24, and the vehicle body side raceway grooves 24a and 31a and the vehicle outside raceway grooves 21a and 31b of the fixed body 3 is suppressed. Can do.

  Next, referring to FIG. 6, the difference between the vibration detection unit 10 of the measuring device A of the rolling bearing device 1 of the present embodiment and the contact-type sensor used in the method for measuring the preload amount of the conventional rolling bearing device. Will be described.

  The graph of FIG. 6 shows the relationship of the natural frequency of the bending vibration mode of the fixed body 3 with respect to the weight change amount of the fixed body 3. From this graph, it can be seen that the natural frequency of the bending vibration mode of the fixed body 3 changes with a change in the weight of the fixed body 3. Specifically, it can be seen that the natural frequency of the bending vibration mode of the fixed body 3 decreases as the weight of the fixed body 3 increases.

  Here, for example, as shown in FIG. 9, when a contact-type sensor is used as the vibration detection sensor 131 as in the preload measuring device AR of the conventional rolling bearing device, the sensor must be directly attached to the fixed body 3. Don't be. Therefore, since the weight of the sensor is added to the fixed body 3, the natural frequency of the fixed body 3 is reduced by the weight of the sensor. As a result, the preload amount of the rolling bearing device estimated from the relationship between the bending vibration mode and the negative gap amount analyzed in FIG. 4 is significantly different from the actual preload amount of the rolling bearing device.

  Therefore, the vibration detection unit 10 of the measuring device A of the rolling bearing device 1 according to the present embodiment uses a non-contact type sensor to avoid adding the weight of the sensor to the fixed body 3. Further, fixing due to variations in the weight of the sensor and the contact pressure between the sensor and the fixed body 3 when the sensor is attached to the fixed body 3 (that is, the force applied to the fixed body 3 when the sensor is attached to the fixed body 3). Variations in the natural frequency of the bending vibration mode of the body 3 can be avoided. As a result, the preload amount of the rolling bearing device 1 can be estimated based on the graph shown in FIG. 4 without changing the natural frequency of the bending vibration mode of the fixed body 3.

  Further, in the contact-type sensor, the operator needs to attach the contact-type sensor to the fixed body 3 and to remove the sensor from the fixed body 3. However, in the non-contact type sensor of this embodiment, when the rolling bearing device 1 is placed on the jig 8, the non-contact type sensor is disposed at a position facing the flange portion 32 in the axial direction. Therefore, the above two steps can be made unnecessary. As a result, the method for measuring the preload amount of the rolling bearing device 1 according to the present invention can shorten the time for the operator to determine the preload amount as compared with the conventional method for measuring the preload amount of the rolling bearing device 100. .

Next, with reference to FIG. 4, FIG. 7, and FIG. 8, a method for assembling the rolling bearing device of the present invention will be described.
First, in step S1, the rolling bearing device 1 is assembled by combining the rotating body 2, the fixed body 3, and the rolling element 4 as a first process. Specifically, the inner ring 24 is fixed to the rotating body 2, and the rolling elements 4 held by the cage 5 are arranged between the rotating body 2 and the fixed body 3 in the radial direction. Then, the upper end portion 21 b of the cylindrical portion 21 of the rotating body 2 and the inner ring 24 are caulked. In the radial direction, a vehicle outer side seal 6 and a vehicle body side seal 7 are disposed between the rotating body 2, the inner ring 24 and the fixed body 3.

Next, as a second step, the preload amount of the rolling bearing device 1 assembled in the first step is measured.
Specifically, first, in step S <b> 2, the rolling bearing device 1 is placed on the jig 8. And as a 3rd process, in step S3, a vibration is given to the flange part 32 of the fixed body 3 of the rolling bearing apparatus 1 by the vibration part 9 which is a vibration means.

  Next, as a fourth step, the vibration applied to the flange portion 32 of the fixed body 3 of the rolling bearing device 1 by the vibration unit 9 is detected by the vibration detection unit 10 which is a vibration detection unit, and the characteristic of the bending vibration mode is determined. Detect frequency. Specifically, in step S <b> 4, the vibration detection unit 10 measures the vibration in the bending vibration mode of the vibration applied to the fixed body 3. In step S <b> 5, the natural frequency of the bending vibration mode of the stationary body 3 is detected from the vibration measured by the vibration detection unit 10 by the calculation unit 11 a of the calculation determination unit 11. More specifically, first, the vibration measured by the vibration detection unit 10 is converted into a vibration value (dB) every frequency (Hz) as shown in the graph of FIG. 8 by fast Fourier transform in the calculation unit 11a. Is broken down into Then, from the result of FIG. 8, the point P having the largest vibration value is detected as the natural frequency of the bending vibration mode of the fixed body 3. That is, the resonance frequency when the vibration is applied by the vibration unit 9 (that is, the frequency having the highest vibration value) is the natural frequency of the bending vibration mode of the fixed body 3. In particular, in the measuring apparatus A, when the excitation unit 9 applies an impact to the outer portion of the flange portion 32 of the fixed body 3, the bending vibration mode of the fixed body 3 is increased. Therefore, the natural frequency of the bending vibration mode of the fixed body 3 can be accurately detected from the graph shown in FIG.

  And in step S6, as a 5th process, the data which show the relationship between the natural frequency of the bending vibration mode of the fixed body 3 of the preset rolling bearing apparatus 1 shown in FIG. 4 and the preload amount of the rolling bearing apparatus 1 are shown. Then, the natural frequency of the bending vibration mode of the fixed body 3 detected in the third step is compared, and it is determined whether or not the preload applied to the rolling bearing device 1 is appropriate. Here, in FIG. 4, since the preload amount can be estimated from the negative gap amount, the upper limit value and lower limit value of the negative gap amount of the rolling bearing device 1 are determined from the upper limit value and lower limit threshold value of the preload amount. A threshold can be set. Accordingly, the preload of the rolling bearing device 1 is a threshold region between the upper limit value and the lower limit value threshold of the natural frequency of the bending vibration mode of the fixed body 3 corresponding to the upper limit value and the lower limit value threshold of the negative gap amount. This is the amount threshold region. Thus, whether or not the preload amount is appropriate is determined based on whether or not the natural frequency of the bending vibration mode of the fixed body 3 detected in the fourth step is within the threshold region of the natural frequency of the vibration mode. judge.

According to the assembly method of the rolling bearing device 1 of the present embodiment, the following effects can be obtained.
(1) In the method of assembling the rolling bearing device 1 of this embodiment, the preload amount of the rolling bearing device 1 is measured by the natural frequency of the bending vibration mode of the fixed body 3. According to this method, compared with the method of measuring the preload amount of the rolling bearing device 1 based on the longitudinal vibration mode, the method of measuring the preload amount of the rolling bearing device 1 based on the bending vibration mode is fixed to the rolling element 4. Since the influence of the contact angle and curvature with the vehicle body side track groove 31a and the vehicle outer side track groove 31b of the body 3, the vehicle side track groove 21a of the rotating body 2, and the vehicle body side track groove 24a of the inner ring 24 is small, the detected inherent The tolerance width (variation) of the negative gap based on the frequency can be reduced. Therefore, since the preload amount is estimated based on the negative gap, the preload amount of the rolling bearing device 1 based on the natural frequency can be estimated with high accuracy. As a result, it is possible to improve the accuracy of managing the preload amount of the rolling bearing device 1.

  (2) Compared with the method for estimating the preload amount of the rolling bearing device 1 based on the longitudinal vibration mode, in the method for estimating the preload amount of the rolling bearing device 1 based on the bending vibration mode, the longitudinal vibration shown in FIG. Compared with the difference R2 between the upper limit curve A2 and the lower limit curve B2 of the natural frequency data of the mode, the difference R1 between the upper limit curve A1 and the lower limit curve B1 of the natural frequency data created in advance shown in FIG. Therefore, the variation in the amount of negative clearance based on the upper limit curve and the lower limit curve of the natural frequency can be reduced. Therefore, in comparison with the method for estimating the preload amount of the rolling bearing device 1 based on the longitudinal vibration mode, the method for estimating the preload amount of the rolling bearing device 1 based on the bending vibration mode has an upper limit curve and a lower limit curve of the natural frequency. Since the variation in the amount of negative gap based on the above is small, the upper limit value and the lower limit value threshold of the negative gap amount can be set small. As a result, the amount of preload of the rolling bearing device 1 based on the natural frequency can be measured with higher accuracy. As a result, it is possible to improve the accuracy of managing the preload amount of the rolling bearing device 1.

  (3) According to the method for assembling the rolling bearing device 1 of the present embodiment, in the fourth step, within a threshold region that is a region between the upper limit value and the lower limit value of the bending vibration mode of the fixed body 3 set in advance. A method of estimating whether or not the preload amount is appropriate is made based on whether or not the detected natural frequency of the bending vibration mode of the fixed body 3 is entered. Therefore, it is estimated whether the preload amount of the rolling bearing device 1 is appropriate based on whether or not the natural frequency of the bending vibration mode of the fixed body 3 detected in the fourth step falls within the threshold region. Since it is possible, the operator can easily estimate whether the preload amount of the rolling bearing device 1 is appropriate.

  (4) According to the method for assembling the rolling bearing device 1 of the present embodiment, a device for hammering the vibration unit 9 which is a vibration means is used. Thereby, compared with the structure which gives a vibration with the conventional vibrator 120 shown in FIG. 9, the time which gives a vibration to the rolling bearing apparatus 1 can be shortened. Therefore, the assembly time of the rolling bearing device 1 can be shortened. In addition, since it is not necessary for the hammering to continuously apply vibration to the rolling bearing device 1, the rolling element 4 and the vehicle body side raceway groove 31 a, the vehicle outer side raceway groove 31 b, and the rotating body 2 are caused by the vibration. Scratches that occur when the vehicle outer race groove 21a and the vehicle body side race groove 24a of the inner ring 24 come into contact with each other can be suppressed.

  (5) According to the method for assembling the rolling bearing device of the present embodiment, the vibration detection unit 10 as the detection means uses a non-contact type sensor. Thereby, the weight change by the sensor of the vibration detection part 10 of the stationary body 3 of the rolling bearing device 1 can be avoided. That is, it is possible to avoid a change in the natural frequency of the bending vibration mode due to the weight of the sensor of the vibration detection unit 10 of the fixed body 3. Therefore, the preload amount of the rolling bearing device 1 can be measured with high accuracy. As a result, it is possible to improve the accuracy of managing the preload amount of the rolling bearing device 1.

(Other embodiments)
According to the rolling bearing device and the preload estimation method of the present embodiment, the following modifications are possible.

  In the above embodiment, the laser Doppler vibrometer is used as the non-contact type sensor of the vibration unit 9, but the present invention is not limited to the laser Doppler vibrometer. For example, in addition to the laser Doppler vibrometer, non-contact vibrometers such as an eddy current type, a capacitance type, and a laser type may be used.

  In the above embodiment, the solenoid 9a is used as the vibration unit 9, but the structure of the vibration unit 9 of the present invention is not limited to the solenoid 9a. For example, as the vibration unit 9, an impact may be applied to the flange portion 32 by dropping a member such as a steel ball onto the flange portion 32 of the fixed body 3. Further, for example, the flange portion 32 may be impacted by hitting the flange portion 32 with a rod-shaped member.

  In the above embodiment, the rotating body 2 and the inner ring 24 are caulked as the structure for fixing the rotating body 2 and the inner ring 24, but the present invention is limited to the fixing structure of the rotating body 2 and the inner ring 24. There is nothing. For example, as the fixing structure, the rotating body 2 may be provided with a screw portion, and the rotating body 2 and the inner ring 24 may be fixed by screwing a nut into the screw portion. Further, for example, the rolling bearing device may be configured to be integrated with a constant velocity joint (not shown).

  -In the said embodiment, although the vibration part 9 vibrated to the flange part 32 of the fixed body 3, the site | part which gives an impact with the vibration part 9 of this invention is not limited to this. In order to detect the natural frequency of the bending vibration mode of the rolling bearing device 1, vibration may be applied to the flange portion 22 of the rotating body 2 by the vibration unit 9.

  In the above embodiment, as a method of estimating the amount of preload of the rolling bearing device 1, the natural frequency of the bending vibration mode of the fixed body 3 measured as the difference R1 between the upper limit value and lower limit value of the natural frequency and the measured threshold value However, the present invention is not limited to this preload amount estimation method. For example, by providing a display device that displays a comparison result (for example, only OK / NG is displayed as a comparison result) between the difference R1 in the threshold and the natural frequency of the bending vibration mode of the fixed body 3 that is measured. The operator may estimate whether or not the preload amount of the rolling bearing device 1 is appropriate only from the comparison result displayed on the display device.

  In the above embodiment, a spherical steel ball is used as the rolling element 4. However, the configuration of the rolling element 4 of the present invention is not limited to this, and other shapes such as cylindrical rollers are used. May be.

Sectional drawing which shows the cross-section of the rolling bearing apparatus about one Embodiment which actualized the assembly method of the rolling bearing apparatus of this invention. The schematic diagram which shows the preload measuring apparatus of the rolling bearing apparatus about the assembly method of the rolling bearing apparatus of the embodiment. The schematic diagram which showed the vibration part of the preload measuring apparatus of the rolling bearing apparatus about the assembly method of the rolling bearing apparatus of the embodiment. About the method of assembling the rolling bearing device of the same embodiment, the rolling element and the rotating body analyzed by the finite element method from the three-dimensional model of the relationship between the natural frequency of the stationary body of the rolling bearing device and the negative gap amount in the axial direction, The graph which shows the threshold value of the bending vibration mode by the upper limit and the minimum of the tolerance of a contact angle and curvature with an inner ring | wheel and a fixed body. About the method of assembling the rolling bearing device of the same embodiment, the rolling element and the rotating body analyzed by the finite element method from the three-dimensional model of the relationship between the natural frequency of the stationary body of the rolling bearing device and the negative gap amount in the axial direction, The graph which shows the threshold value of the longitudinal vibration mode by the upper limit and lower limit of the tolerance of a contact angle and curvature with an inner ring | wheel and a fixed body. The graph which shows the relationship between the weight of a sensor, and the natural frequency of the bending vibration mode of a fixed body about the assembly method of the rolling bearing apparatus of the embodiment. The flowchart which shows the assembly process of the rolling bearing apparatus about the assembly method of the rolling bearing apparatus of the embodiment. The graph which shows the relationship between the frequency and vibration value which were obtained by the calculating part of the calculation determination part about the assembly method of the rolling bearing device of the embodiment. The schematic diagram which shows the measuring apparatus of the preload of the rolling bearing apparatus about the assembly method of the conventional rolling bearing apparatus.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Rolling bearing apparatus (bearing apparatus), 2 ... Rotating body, 21 ... Cylindrical part, 21a ... Outer raceway groove, 21b ... Upper end part, 22 ... Flange part, 23 ... Inlay part, 23a ... End part, 24 ... Inner ring (Rotary body), 24a ... vehicle body side raceway groove, 3 ... fixed body, 31 ... cylindrical portion, 31a ... vehicle body side raceway groove, 31b ... vehicle outer raceway groove, 32 ... flange portion, 32a ... through hole, 4 ... rolling element , 6 ... car body side seal, 7 ... car exterior seal, 8 ... jig, 8a ... surface, 9 ... vibration unit (vibration means), 9a ... solenoid, 9b ... frame, 9c ... fixed iron core, 9d ... coil, Reference numeral 9e: movable iron core, 9f: end, 9g: elastic member, 9h: hammer, 10: vibration detection unit (detection means), 11: calculation determination unit, 11a: calculation unit, 11b: determination unit.

Claims (5)

  A method for measuring a preload amount of a bearing device,
  The bearing device has a rotating body, a fixed body, and a rolling element,
  The rotating body rotates with the axle;
  The fixed body surrounds the rotating body,
  The rolling element is disposed between the rotating body and the fixed body in the radial direction of the rotating body, and a preload is applied by the rotating body and the fixed body,
  The measuring method has a measuring step A, a measuring step B, and a measuring step C,
  In the measurement step A, vibration is applied to the bearing device by a vibration means,
  In the measurement step B, the vibration applied to the bearing device by the vibration means is detected by a detection means, and the natural frequency of the bending vibration mode of the bearing device is calculated based on the detection result of the detection means. ,
  In the measurement step C, the calculated value of the natural frequency of the bending vibration mode calculated in the measurement step B is set in advance so that the natural frequency of the bending vibration mode of the bearing device and the negative gap amount of the bearing device are set. Therefore, it is determined that the preload amount applied to the rolling element is included in an appropriate range based on being included in the threshold region defined by the negative gap amount.
  Measuring method of preload amount of bearing device.   The relationship between the preset natural frequency of the bending vibration mode of the bearing device and the negative gap amount of the bearing device is the curve of the natural frequency of the bending vibration mode, the upper limit value of the negative gap amount, and the negative gap. An area between the natural frequency on the curve corresponding to the upper limit value of the negative gap amount and the natural frequency on the curve corresponding to the lower limit value of the negative gap amount. Define as threshold area
  A method for measuring a preload amount of the bearing device according to claim 1.   The measurement step A uses a hammering device as the vibration means.
  A method for measuring a preload amount of the bearing device according to claim 1.   The measurement step B uses a non-contact type sensor as the detection means.
  The measuring method of the amount of preload of the bearing apparatus as described in any one of Claims 1-3.   A method for assembling a bearing device,
  The assembly method includes a first step and a second step,
  In the first step, the bearing device is assembled using the rotating body, the fixed body, and the rolling element,
  Said 2nd process has the said measurement process A, the said measurement process B, and the said measurement process C as described in any one of Claims 1-4.
  A method for assembling the bearing device.

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