JP2006105894A - Slewing gear for characteristic measurement of rolling bearing, characteristic measurement device of rolling bearing, and characteristic measurement technique - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To measure dynamic torque of a rolling bearing 1 while an inner ring 5 is tilted to an outer ring 3 or the rotary ring under supposition of the assembled error and the like. <P>SOLUTION: The bottom face of a bush 31 tilting to a virtual plane perpendicular to the central axis of the outer ring 3 is abutted on the top face of the inner ring 5 fitted externally into a part of the main shaft 16 via a washer 37. The bush 31 is pressed toward the inner ring 5 by a pressing machine 32 so as to tilt the inner ring 5 to the outer ring 3 at a predetermined angle. In this state, the outer ring 3 is rotated and the resulting torque acting to the inner ring 5 is measured by a dynamic torque measuring section 11 via the main shaft 16. Because the main shaft 16 is supported rotatably by a static pressure air bearing 17, dynamic torque can be measured with a high degree of accuracy. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to, for example, a rotating device for measuring characteristics of a rolling bearing used to measure characteristics such as dynamic torque of a rolling bearing having a small diameter (for example, an inner diameter of about 8 to 15 mm) incorporated in a fan motor of an air conditioner, and the like. Further, the present invention relates to an improvement in a characteristic measuring apparatus for a rolling bearing incorporating the same and a characteristic measuring method for the rolling bearing. Specifically, it is for measuring characteristics generated in the rolling bearing when the outer ring is rotated with the inner ring inclined with respect to the outer ring.

  When designing various mechanical devices, it is necessary to measure the dynamic torque of the rolling bearing to be incorporated into the rotation support portion of the mechanical device. Such dynamic torque measurement is also necessary to improve the performance of the rolling bearing. Further, it is necessary to measure acoustic characteristics such as the noise level of the rolling bearing from the viewpoint of improving the performance. Among these, as a technique for measuring the dynamic torque of a rolling bearing, for example, there are inventions described in Patent Documents 1 to 3. In the case of the inventions described in these Patent Documents 1 to 3, a rolling bearing is installed in a normal state, and characteristics such as dynamic torque are measured. That is, in a state where a plurality of rolling bearings are incorporated in the measuring apparatus, the center axes of the inner ring and the outer ring that constitute the rolling bearing are substantially matched. In such a state, the dynamic torque of the rolling bearing is measured.

  On the other hand, in general, when a rolling bearing is incorporated in a rotation support portion of various mechanical devices, the center axis of the inner ring may be inclined with respect to the rotation axis due to an assembly error or the like. For this reason, it is important to grasp the allowable use limit of the rolling bearing when the central axis of the inner ring is inclined. However, in the case of the prior art as described in each of the above Patent Documents 1 to 3, it is possible to measure the characteristics when the rolling bearing is assembled in a normal state, but there are assembly errors and the like. However, it is impossible to measure the characteristics of the rolling bearing alone, which is a measurement target when the central axis of the inner ring is inclined. Of course, even in the case of the above-described prior art, it is possible to perform the measurement work in a state where the central axis of the inner ring is inclined to some extent, but the state deviated from the assembled state corresponding to the normal range, or Assuming assembly errors that may occur in actual usage conditions, it is not possible to perform the measurement work in a state in which the central axis of the inner ring is accurately tilted as desired.

JP 2000-155073 A JP 2000-162092 A JP 2001-194270 A

  In consideration of the above-described circumstances, the present invention measures characteristics such as dynamic torque of a rolling bearing in a state where the inner ring is accurately inclined as desired with respect to the rotation axis of the outer ring, assuming assembly errors and the like. It was invented to realize a possible structure.

Of the rolling bearing characteristic measuring rotating device, the rolling bearing characteristic measuring device and the characteristic measuring method according to the present invention, the rolling bearing characteristic measuring rotating device according to claim 1 has an outer ring raceway on an inner peripheral surface. This rolling bearing is used to measure the characteristics of a rolling bearing comprising an outer ring, an inner ring having an inner ring raceway on the outer peripheral surface, and a plurality of rolling elements provided between the outer ring raceway and the inner ring raceway. The rotational force is transmitted to.
In particular, in the case of the rotating device for measuring characteristics of a rolling bearing according to the first aspect of the present invention, the rotating device includes a housing and an inclination imparting mechanism.
Of these, the housing holds the outer ring and can transmit a rotational force to the outer ring.
The inclination imparting mechanism is for inclining the inner ring by a predetermined angle with respect to the outer ring.

According to a third aspect of the present invention, there is provided a rolling bearing characteristic measuring device comprising a rotation transmitting portion, a rotation driving portion, and a measuring portion.
Among these, the rotation transmission part can freely transmit the rotational force to the rolling bearing.
In addition, the rotation driving unit rotationally drives an outer ring constituting the rolling bearing via the rotation transmission unit.
The measuring unit measures the characteristics of the rolling bearing.
In particular, in the rolling bearing characteristic measuring device according to claim 3, the rotation transmitting portion is the rolling bearing characteristic measuring rotating device described above, and the inner ring constituting the rolling bearing is inclined with respect to the outer ring. When the outer ring is rotated in a state of being caused to be rotated, the characteristics generated in the rolling bearing are measured.

  Further, in the method for measuring characteristics of a rolling bearing according to claim 8, in order to measure the characteristics of the rolling bearing described above, a bush whose one end surface is inclined with respect to a virtual plane perpendicular to the axial direction of the outer ring is provided. Place it concentrically with the outer ring. At the same time, the one end face is brought into direct or indirect contact with the end face of the inner ring. In this state, the bush is pressed toward the inner ring with respect to the axial direction of the outer ring. Thus, the inner ring is inclined at a predetermined angle with respect to the outer ring. Then, the characteristics of the rolling bearing when the outer ring is rotated are measured.

  In the case of the present invention configured as described above, it is possible to measure the characteristics of the rolling bearing in a state where the inner ring is inclined with respect to the outer ring, which is a rotating ring, assuming assembly errors and the like.

Of the above-described inventions, in order to implement the rotating device for measuring characteristics of a rolling bearing according to claim 1, preferably, as described in claim 2, the inner ring is inclined at a predetermined angle with respect to the outer ring. An inclination provision mechanism is comprised from a bush and a press mechanism.
Of these bushes, the end surface on the side that directly or indirectly contacts the end surface of the inner ring is inclined with respect to a virtual plane orthogonal to the axial direction of the outer ring, and is disposed concentrically with the outer ring.
The pressing mechanism presses the bush toward the inner ring in the axial direction of the outer ring.
With this configuration, a predetermined inclination angle can be given to the inner ring quantitatively and reliably with a simple structure. Further, by changing the inclination angle of the end face of the bush, the inclination angle applied to the inner ring can be freely changed.

Further, when carrying out the rolling bearing characteristic measuring device according to claim 3 or the rolling bearing characteristic measuring method according to claim 8, as described in claim 4 or claim 9, The rolling bearing is a small diameter ball bearing, and the characteristic to be measured is the dynamic torque of the small diameter ball bearing alone.
With this configuration, it is possible to accurately measure the dynamic torque of a small-diameter ball bearing when the inner ring is tilted, and to investigate the effects of assembly errors etc. on the allowable use limit of this small-diameter ball bearing. .
In the case of measuring dynamic torque as described above, preferably, as described in claim 5, the main shaft that constitutes the measuring part and supports the inner ring is rotatable by a hydrostatic gas bearing having substantially zero friction torque. To support. Then, when the outer ring is rotated, the rotational torque acting on the inner ring is measured via the main shaft, thereby measuring the dynamic torque of the rolling bearing.
If comprised in this way, the measurement of the dynamic torque of a rolling bearing can be performed with high precision. That is, since the dynamic torque is measured via a main shaft that is rotatably supported by a hydrostatic gas bearing, the frictional resistance generated when the main shaft rotates can be almost eliminated, and the dynamic torque can be more accurately determined. It can be measured.

On the other hand, when carrying out the rolling bearing characteristics measuring device according to claim 3 or the rolling bearing characteristics measuring method according to claim 8, the invention is changed to claims 6 to 7 or claims 10 to 11. As described, the characteristic to be measured may be the acoustic characteristic of the rolling bearing in addition to or separately from the dynamic torque of the rolling bearing.
If comprised in this way, the influence which an assembly | attachment error etc. exerts on the acoustic characteristic of a rolling bearing can be investigated.

  1 to 5 show an embodiment of the present invention. A rolling bearing 1, which is an object to be measured in this embodiment, includes an outer ring 3 having an outer ring raceway 2 on an inner peripheral surface, an inner ring 5 having an inner ring raceway 4 on an outer peripheral surface, and the outer ring raceway 2 and the inner ring raceway 4. It is a small-diameter ball bearing provided with a plurality of rolling elements 6, 6 provided so as to be capable of rolling therebetween. In the present specification and claims, the term “small-diameter ball bearing” means not only a small-diameter ball bearing (inner diameter: 8 to 15 mm) incorporated in a fan motor or the like, but also a miniature ball bearing and a relatively small-diameter single row. A ball bearing including a deep groove type ball bearing and having an inner diameter of 1 to 15 mm (preferably 5 to 10 mm) shall be used. In the case of the present embodiment, the dynamic torque of the rolling bearing 1 configured in this way is measured in a state where a predetermined inclination angle is applied to the inner ring 5. In this way, the dynamic torque measuring device 7 that measures the dynamic torque of the rolling bearing 1 includes a rotation transmission unit 9, a rotation drive unit 10, and a dynamic torque measurement unit 11 arranged on the upper portion of a base 8, respectively. Of these, the rotation transmitting portion 9 is supported by a bracket 12 fixed to the upper surface of the base 8. The rotation transmission unit 9 includes a hollow fixed shaft 13, a pulley unit 14, a housing 15, and an inclination imparting mechanism 18.

  The hollow fixed shaft 13 is arranged in the vertical direction and is fixed to the upper portion of the bracket 12. For this reason, the hollow fixed shaft 13 does not rotate during operation. The pulley portion 14 is disposed concentrically with the hollow fixed shaft 13 on the outer diameter side of the upper half of the hollow fixed shaft 13 and is rotatably supported by bearings 19 and 19. A belt groove 20 is formed on the outer peripheral surface of the intermediate portion of the pulley portion 14, and the belt 22 is stretched between the pulley 21 constituting the rotation driving portion 10 described later. The bearings 19 and 19 that support the pulley portion 14 are those having sufficiently larger rigidity than the rolling bearing 1 that is a measurement target.

  The housing 15 is fixed to the upper surface of the pulley portion 14 by a plurality of bolts 23 and 23. The outer ring 3 constituting the rolling bearing 1 is fitted and fixed to the inner peripheral surface of the housing 15. For this reason, the outer ring 3 rotates together with the housing 15. A step surface 46 is provided on the inner peripheral surface of the housing 15, and the lower end surface of the outer ring 3 is brought into contact with the step surface 46 to prevent the outer ring 3 from being displaced downward. Further, the central axis of the inner peripheral surface of the housing 15 coincides with the central axis of the pulley portion 14. For this reason, the outer ring 3 fitted in the housing 15 is also arranged concentrically with the pulley portion 14.

  On the other hand, on the inner diameter side of the hollow fixed shaft 13, the upper half portion of the main shaft 16 constituting the dynamic torque measuring unit 11 is vertically penetrated. The main shaft 16 is disposed concentrically with the hollow fixed shaft 13, and a gap is interposed between the outer peripheral surface of the intermediate portion of the main shaft 16 and the inner peripheral surface of the hollow fixed shaft 13. The main shaft 16 has a lower half portion formed by a hollow rotating shaft portion 24 having a U-shaped cross section and an annular shape as a whole, and an upper half portion formed by a solid rotating shaft portion 45 formed in a stepped cylindrical shape. , Respectively. The solid rotary shaft portion 45 and the hollow rotary shaft portion 24 include a convex portion 25 provided concentrically with the solid rotary shaft portion 45 on the lower end surface of the solid rotary shaft portion 45, and the hollow rotary shaft portion 24. By being engaged with the upper end opening of each other, they are arranged concentrically with each other. The flange 26 provided at the lower end of the solid rotary shaft 45 is brought into contact with the upper surface of the hollow rotary shaft 24, and a plurality of circumferential directions of the flange 26 are screwed and tightened with bolts 27. These rotary shaft portions 45 and 24 are connected to each other in a separable manner.

  The hollow rotary shaft portion 24 is supported by the static pressure gas bearing 17 so as to be rotatable with respect to the hollow fixed shaft 13. That is, the static pressure gas bearing 17 is installed below the hollow fixed shaft 13 between the inner peripheral surface of the bracket 12 and the outer peripheral surface of the hollow rotary shaft portion 24. For this purpose, the static pressure gas bearing 17 is fixed to the lower portion of the hollow fixed shaft 13 by a bolt 28. Further, flanges 29a and 29b are formed respectively at the upper end and the lower end of the hollow rotary shaft 24, and the inner end surfaces of these flanges 29a and 29b are arranged in the axial direction of the hydrostatic gas bearing 17 (FIG. 1). 2 in the vertical direction), and further, the outer peripheral surface of the intermediate portion of the hollow rotary shaft portion 24 is opposed to the inner peripheral surface of the static pressure gas bearing 17 through a minute gap. The static pressure gas bearing 17 has a structure in which a gas such as air is ejected from the inner peripheral surface and both axial end surfaces. For this reason, the hollow rotating shaft portion 24 is rotatably supported by the static pressure gas bearing 17.

  A small-diameter shaft portion 30 is formed near the upper end of the middle portion of the solid rotation shaft portion 45. The small-diameter shaft portion 30 is disposed concentrically with the housing 15 so as to penetrate the inner diameter side of the housing 15 in the vertical direction. The small-diameter shaft portion 30 is an intermediate portion of the solid rotation shaft portion 45, and the outer peripheral surface is formed to be smaller than the outer diameter of the portion facing the inner peripheral surface of the hollow fixed shaft 13. An inner ring 5 constituting the rolling bearing 1 is arranged on the surface. Therefore, the rolling bearing 1 as a measurement target is installed between the inner peripheral surface of the housing 15 and the outer peripheral surface of the small-diameter shaft portion 30. Note that the inner ring 5 needs to be loosely fitted to the small-diameter shaft portion 30 in order to be inclined by an inclination applying mechanism 18 described later. That is, it is necessary to provide a gap between the inner peripheral surface of the inner ring 5 and the outer peripheral surface of the small-diameter shaft portion 30 to allow the inner ring 5 to tilt.

  A support shaft 33 is formed near the upper end of the solid rotation shaft 45 and above the small-diameter shaft 30. The tilt applying mechanism 18 is arranged around the support shaft portion 33. The inclination imparting mechanism 18 includes a bush 31 and a pressing mechanism 32. Of these, the bush 31 is formed in a cylindrical shape as a whole. The bush 31 is concentric with the support shaft 33 (not inclined) and axially (in the upper and lower directions in FIGS. 1 and 2). Direction) and can be fitted with the radial gap slightly suppressed. The small-diameter shaft portion 30 and the support shaft portion 33 constituting the solid rotation shaft portion 45 are formed concentrically with each other. For this reason, the support shaft portion 33 is also arranged concentrically with the housing 15, and the bush 31 fitted outside the support shaft portion 33 is arranged concentrically with the outer ring 3 fitted inside the housing 15. .

  As shown in detail in FIG. 4, the bush 31 has one end face (lower end face in FIGS. 1, 2, and 4) inclined with respect to a virtual plane α that is orthogonal to the axial direction of the outer ring 3. On the other hand, the other end surface (the upper end surface in FIGS. 1, 2, and 4) is formed in parallel with the virtual plane α. The inclination angle θ of the one end face is about 0 to 3 degrees. For example, as shown in Table 1 below, if a plurality of bushes having different inclination angles θ (10 in the case of this embodiment) are prepared, the bushes can be applied to the inner ring 5 simply by replacing the bushes. The tilt angle can be adjusted.

  The pressing mechanism 32 includes a spring receiving member 34 formed in a cylindrical shape and a spring 35. Of these, the spring receiving member 34 is fixed to a portion near the upper end of the support shaft portion 33 in a state where axial displacement is prevented by tightening a screw 36. And the said spring 35 is arrange | positioned between the lower end surface of this spring receiving member 34, and the other end surface of the said bush 31, and the force which turns to this bush 31 downward is provided with respect to the perpendicular direction. The vertical direction and the direction of the central axis of the outer ring 3 coincide with each other. Further, a washer 37 is provided between one end surface of the bush 31 and the upper end surface of the inner ring 5. The washer 37 is loosely fitted to the upper end portion of the small diameter shaft portion 30. Therefore, the washer 37 can be displaced with respect to the axial direction of the small diameter shaft portion 30. The washer 37 can be omitted. In this case, one end surface of the bush 31 and the upper end surface of the inner ring 5 are brought into direct contact with each other.

  As described above, by providing the washer 37 between the bush 31 and the inner ring 5, a downward force applied to the bush 31 is applied to the inner ring 5 via the washer 37. The force applied to the inner ring 5 inclines the inner ring 5 and acts on the inner ring 5 as an axial load. That is, the washers 37 installed between the bush 31 and the inner ring 5 are in contact with both end surfaces of the bush 31 and the upper end surface of the inner ring 5, respectively. For this reason, in the case of the present embodiment, the flatness of both side surfaces of the washer 37 is finished satisfactorily, and the parallelism between these both side surfaces is improved. Therefore, the plate thickness dimension of the washer 37 hardly varies in the circumferential direction (the thickness is uniform over the entire circumference). Then, the washer 37 is inclined along the inclination of the one end surface of the bush 31 by pressing the bush 31 downward with the one end surface of the bush 31 in contact with the upper surface of the washer 37. Accordingly, the upper end surface of the inner ring 5 that contacts the lower surface of the washer 37 is also inclined. Since there is almost no variation in the plate thickness dimension in the circumferential direction of the washer 37, the upper end surface of the inner ring 5 is inclined at substantially the same angle as the inclination of the one end surface of the bush 31. As a result, the central axis of the inner ring 5 is inclined with respect to the central axis of the outer ring 3 according to the inclination of one end surface of the bush 31.

  Further, the downward force applied to the inner ring 5 from the tilt applying mechanism 18 via the washer 37 as described above becomes an axial load on the inner ring 5. Therefore, the rolling bearing 1 is in a state where a preload is applied. The axial load applied to the inner ring 5 can be changed by exchanging the spring 35 constituting the inclination applying mechanism 18 or changing the compression amount. Therefore, in the case of this embodiment, the inclination angle of the inner ring 5 and the axial load applied to the inner ring 5 are changed, and the dynamic torque of the rolling bearing 1 (small-diameter ball bearing alone) is changed under various conditions. Measurement is possible.

  In addition, as described above, the inclination angle of the inner ring 5 can be adjusted by preparing a plurality of bushes 31 having different inclination angles on one end face. In the present embodiment, however, the inner ring 5 is actually adjusted. The inclination angle can be confirmed. For this purpose, two laser-type micro displacement meters 38, 38 are installed above the tilt applying mechanism 18 (FIG. 2). The laser beams of these micro displacement gauges 38 and 38 are irradiated toward the outer diameter of the upper surface of the washer 37. For this reason, the outer diameter of the washer 37 is larger than the outer diameters of the bush 31 and the spring receiving member 34. In this way, by irradiating the laser beam of the minute displacement meter 38, 38 toward the outer diameter portion of the washer 37, the tilt angle of the inner ring 5 can be measured via the washer 37.

More specifically, the micro displacement gauges 38, 38 are located at positions P ₁ , P ₂ (point-symmetric) of the upper side surface of the washer 37 that are shifted 180 degrees from each other with respect to the circumferential direction of the washer 37 (point symmetry). FIG. 3) is irradiated with a laser beam, and axial displacements (vibrations) at these positions P ₁ and P ₂ are measured. These positions P ₁ and P ₂ have the same radial distance from the central axis of the small-diameter shaft portion 30 (present on the same arc centered on the central axis of the small-diameter shaft portion 30). In this manner, the main shaft 16 is rotated once (for example, manually) in a state where the laser beams are irradiated to the positions P ₁ and P ₂ on the upper side surface of the washer 37. Then, a minute axial displacement at each of the positions P ₁ and P ₂ is measured over the entire circumference of the washer 37. Then, the maximum value of the absolute value of the minute displacement at each of the positions P ₁ and P ₂ is calculated and processed, whereby the inclination angle of the inner ring 5 with respect to the washer 37 and the outer ring 3 is determined. It can be determined accurately, and it can be confirmed whether or not the inclination angle is a desired angle.

  In the case of the present embodiment, the outer ring 3 is rotationally driven by the rotation driving unit 10 via the rotation transmitting unit 9 in a state where the inner ring 5 is inclined by a predetermined angle by the inclination imparting mechanism 18 as described above. That is, the rotation drive unit 10 includes a motor 40 supported on a motor bracket 39 on the upper surface of the base 8, and the pulley 21 that is rotationally driven by the motor 40. As described above, the belt 22 is stretched between the pulley 21 and the pulley portion 14 constituting the rotation transmitting portion 9 on the outer peripheral surface of the pulley 21. For this reason, the pulley portion 14 is rotated via the pulley 21 and the belt 22 by rotationally driving the motor 40. Then, the outer ring 3 is rotationally driven through the housing 15 fixed to the upper surface of the pulley portion 14.

  When the outer ring 3 is rotationally driven as described above, a rotational force (dynamic torque) that tries to rotate with the inner ring 5 is generated. In this embodiment, the dynamic torque is measured by the dynamic torque measuring unit 11. The dynamic torque measuring unit 11 includes the main shaft 16, a swing arm 41 provided at the lower end of the main shaft 16, and a torque sensor 42 capable of detecting torque transmitted via the swing arm 41. Become. The torque sensor 42 is attached to an adapter 43 installed on the side surface of the bracket 12. The swing arm 41 is fixed to a part of the flange 26 formed in the lower end portion of the main shaft 16 in the circumferential direction, and is a long hole 44 opened in a part of the hollow fixed shaft 13 in the circumferential direction. Protruding from. The long hole 44 is opened in a fan shape of about 90 degrees starting from the central axis of the hollow fixed shaft 13. Therefore, the swing arm 41 can swing and turn within the opening range of the long hole 44.

  When the inner ring 5 tends to rotate due to the rotational force caused by the rotation, the rotational force acting on the inner ring 5 is oscillated through the main shaft 16 constituted by the small-diameter shaft portion 30 on which the inner ring 5 is externally fitted. It is transmitted to the arm 41. The swing arm 41 tends to turn in the same direction as the rotation direction of the inner ring 5. Therefore, by detecting the turning force of the swing arm 41 with the torque sensor (load sensor) 42, the rotational force acting on the inner ring 5, that is, the dynamic torque of the rolling bearing 1 (small-diameter ball bearing alone). Can be measured as

  In the case of the present embodiment, the hollow rotary shaft portion 24 constituting the main shaft 16 is rotatably supported by a static pressure gas bearing 17 with respect to the hollow fixed shaft 13. For this reason, the main shaft 16 is rotatably supported with the frictional resistance being substantially zero. Therefore, in the case of the present embodiment, the dynamic torque of the rolling bearing 1 can be measured with almost no frictional resistance of the support bearing device, and the dynamic torque can be measured with high accuracy.

  In the case of the present embodiment, the dynamic torque can be measured in a state where an axial load is applied to the inner ring 5 and a predetermined inclination angle is applied. That is, in the case of the present embodiment, the outer ring 3 is rotated in a state where a downward force is applied to the inner ring 5 by the tilt applying mechanism 18. In addition, since one end surface of the bush 31 constituting the inclination imparting mechanism 18 that contacts the upper end surface of the inner ring 5 is inclined, the inner ring 5 is inclined at a predetermined angle. Therefore, in the case of the present embodiment, an axial load is applied to the inner ring 5 and the inner ring 5 is inclined with respect to the outer ring 3 assuming an assembly error or the like. It is possible to measure dynamic torque.

  In the case of this embodiment, the inner ring 5 is inclined by pressing the bush 31 having the one end face inclined against the upper end face of the inner ring 5 through the washer 37. The bush 31 is inclined according to the inclination angle of the one end face. For this reason, the inner ring 5 can be tilted quantitatively and reliably.

  In the case of this embodiment configured and operated as described above, the amount of inclination of the inner ring 5 at the usage limit of the rolling bearing 1 can be grasped, and the influence of assembly errors etc. on the allowable usage limit of the rolling bearing can be investigated. Can do. Therefore, the structure of the present embodiment can be a means for obtaining a reference for judging the allowable limit of the assembly error.

  In addition, in the case of a present Example, the acoustic characteristic of the rolling bearing 1 can also be measured in addition to the measurement of the dynamic torque mentioned above or separately from the measurement of dynamic torque. That is, an acoustic measuring device such as a microphone is installed in the vicinity of the rolling bearing 1 to measure noise generated in the rolling bearing 1 when the outer ring 3 is rotated with the inner ring 5 being inclined. Thereby, it is possible to investigate the influence of the assembly error or the like on the acoustic characteristics such as the bearing sound generation state and the noise level.

Sectional drawing which shows the dynamic torque measuring apparatus of the rolling bearing of a present Example. The A section enlarged view of FIG. The figure which abbreviate | omitted one part and was seen from the upper part of FIG. Sectional drawing of the bush integrated in the dynamic torque measuring apparatus of the rolling bearing of a present Example. The figure seen from the lower part of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Rolling bearing 2 Outer ring raceway 3 Outer ring 4 Inner ring raceway 5 Inner ring 6 Rolling body 7 Dynamic torque measuring device 8 Base 9 Rotation transmission part 10 Rotation drive part 11 Dynamic torque measurement part 12 Bracket 13 Hollow fixed shaft 14 Pulley part 15 Housing 16 Main shaft 17 Static pressure gas bearing 18 Inclination imparting mechanism 19 Bearing 20 Belt groove 21 Pulley 22 Belt 23 Bolt 24 Hollow rotary shaft portion 25 Convex portion 26 Flange 27 Bolt 28 Bolt 29a, 29b Flange 30 Small diameter shaft portion 31 Bushing 32 Pressing mechanism 33 Support shaft Part 34 Spring receiving member 35 Spring 36 Screw 37 Washer 38 Micro displacement meter 39 Motor bracket 40 Motor 41 Oscillating arm 42 Torque sensor 43 Adapter 44 Long hole 45 Solid rotating shaft part 46 Step surface

Claims (11)

  Characteristics of a rolling bearing comprising an outer ring having an outer ring raceway on an inner peripheral surface, an inner ring having an inner ring raceway on an outer peripheral surface, and a plurality of rolling elements provided between the outer ring raceway and the inner ring raceway so as to be freely rollable. A rotating device for measuring the characteristics of a rolling bearing that transmits a rotational force to the rolling bearing, and a housing that holds the outer ring and is capable of transmitting the rotational force to the outer ring, and the inner ring A rotating device for measuring characteristics of a rolling bearing, comprising a tilt imparting mechanism for tilting the outer ring with a predetermined angle.   The inclination imparting mechanism for inclining the inner ring by a predetermined angle with respect to the outer ring is such that the end face that directly or indirectly contacts the end face of the inner ring is inclined with respect to a virtual plane perpendicular to the axial direction of the outer ring. The rolling device for measuring characteristics of a rolling bearing according to claim 1, comprising a bush arranged concentrically with the outer ring and a pressing mechanism for pressing the bush toward the inner ring in the axial direction of the outer ring.   A rotation transmission unit that can freely transmit a rotational force to the rolling bearing, a rotation drive unit that rotationally drives an outer ring that constitutes the rolling bearing via the rotation transmission unit, and a measurement unit that measures characteristics of the rolling bearing; A rolling bearing characteristic measuring apparatus comprising: the rotation transmitting portion according to any one of claims 1 to 2, wherein the rolling bearing characteristic measuring rotating apparatus includes: an inner ring constituting the rolling bearing; A rolling bearing characteristic measuring device for measuring characteristics generated in the rolling bearing when the outer ring is rotated while being inclined with respect to the outer ring.   4. The rolling bearing characteristic measuring device according to claim 3, wherein the rolling bearing is a small diameter ball bearing, and the characteristic to be measured is a dynamic torque of the small diameter ball bearing alone.   The main shaft that constitutes the measuring part and supports the inner ring is rotatably supported by a hydrostatic gas bearing. When the outer ring is rotated, the accompanying rotational force acting on the inner ring is measured via this main shaft. The rolling bearing characteristic measuring device according to claim 4, wherein the dynamic torque of the rolling bearing is measured by doing so.   The rolling bearing characteristics measuring device according to any one of claims 4 to 5, which measures the acoustic characteristics of the rolling bearing in addition to the dynamic torque of the rolling bearing.   The rolling bearing characteristic measuring device according to claim 3, wherein the characteristic to be measured is an acoustic characteristic of the rolling bearing.   Characteristics of a rolling bearing comprising an outer ring having an outer ring raceway on an inner peripheral surface, an inner ring having an inner ring raceway on an outer peripheral surface, and a plurality of rolling elements provided between the outer ring raceway and the inner ring raceway so as to be freely rollable. A bush whose one end surface is inclined with respect to a virtual plane perpendicular to the axial direction of the outer ring is disposed concentrically with the outer ring, and the one end surface is directly or indirectly applied to the end surface of the inner ring. When the bushing is pressed against the inner ring with respect to the axial direction of the outer ring, the inner ring is inclined at a predetermined angle with respect to the outer ring, and the rolling is performed when the outer ring is rotated. A method for measuring the characteristics of rolling bearings, which measures the characteristics of bearings.   9. The method for measuring characteristics of a rolling bearing according to claim 8, wherein the rolling bearing is a small diameter ball bearing, and the characteristic to be measured is a dynamic torque of the small diameter ball bearing alone.   The method for measuring characteristics of a rolling bearing according to claim 9, wherein in addition to the dynamic torque of the rolling bearing, the acoustic characteristics of the rolling bearing are measured.   The method for measuring characteristics of a rolling bearing according to claim 8, wherein the characteristic to be measured is an acoustic characteristic of the rolling bearing.

Images