Bearing pressurizing device, bearing vibration measuring device, method for measuring vibration of ball bearings, method for manufacturing ball bearings, method for manufacturing vehicles, and method for manufacturing mechanical devices.

Abstract

This invention provides a bearing pressurizing device that can easily handle vibration measurement and inspection of ball bearings of different dimensions. [Solution] The bearing pressurizing device 1 comprises a plurality of linear actuators 10a, 10b, and a pressurizing jig 11 that is pushed in the axial direction of the radial ball bearing 2 by the plurality of linear actuators 10a, 10b, causing the inner ring 5 of the radial ball bearing 2 to oscillate and / or be translated in the axial direction. The pressurizing jig 11 has a plurality of contact parts 13a, 13b, 13c arranged on the same virtual circle so as to be able to contact a plurality of locations in the circumferential direction of the end face 12 on one axial side of the outer ring 4 of the radial ball bearing 2. The plurality of linear actuators 10a, 10b pressurize the outer ring 4 in the thrust direction via the pressurizing jig 11, causing the outer ring 4 to tilt and / or be translated in the axial direction.

Description

[Technical Field] 【0001】 This disclosure relates to a bearing pressurizing device, a bearing vibration measuring device, a method for measuring vibration of a ball bearing, a method for manufacturing a ball bearing, a method for manufacturing a vehicle, and a method for manufacturing a mechanical device. [Background technology] 【0002】 Radial ball bearings are incorporated into the rotating support sections of vehicles and various types of machinery. 【0003】 A radial ball bearing comprises an outer ring having an outer ring raceway on its inner circumference, an inner ring having an inner ring raceway on its outer circumference, and a plurality of balls positioned between the outer ring raceway and the inner ring raceway. 【0004】 During the operation of a radial ball bearing, multiple balls repeatedly pass over the raceway surfaces of both the outer and inner rings. Therefore, if there are defects such as scratches or delamination on the raceway surface of either the outer or inner ring, the abnormal noise and vibration generated during the operation of the radial ball bearing will increase, degrading the acoustic performance of the radial ball bearing. 【0005】 Therefore, inspections are conducted to determine whether defects exist on the raceway surface of the outer or inner ring of a radial ball bearing. Specifically, as shown in Figure 14, while the inner ring 100 is rotated, the entire circumferential surface of the outer ring 101 is uniformly pressed in the thrust direction, and the radial vibration of the outer ring 101 is measured while the outer ring 101 is displaced axially relative to the inner ring 100. If a defect exists in the area of ​​the raceway surface of the outer ring raceway 102 or inner ring raceway 103 where the ball 104 rolls, the radial vibration of the outer ring 101 will increase. Thus, it is possible to inspect whether or not defects exist on the raceway surface. [Prior art documents] [Patent Documents] 【0006】 [Patent Document 1] Publication No. 52-114737 [Overview of the Initiative] [Problems that the invention aims to solve] 【0007】 Conventional vibration measurement methods for radial ball bearings involve applying uniform pressure to the axial end face of the outer ring in the thrust direction. As a result, the area in which defects can be inspected on the raceway surfaces of the outer and inner rings is limited to a small area that is in strong contact with the rolling surface of the balls. Therefore, it is not possible to accurately inspect the raceway surfaces for defects. 【0008】 In light of these circumstances, Japanese Utility Model Publication No. 114737 (Showa 52) describes a vibration measurement method in which a moment load is applied to the outer ring while the inner ring is rotating, and the radial vibration of the outer ring is measured while the outer ring is tilted relative to the inner ring. 【0009】 This vibration measurement method allows for the modification of the range of the raceway surface that comes into contact with the ball's rolling surface, thereby expanding the inspection range. Consequently, it is possible to accurately inspect the raceway surface for defects. 【0010】 Japanese Utility Model Publication No. 52-114737 discloses the use of a bearing vibration measuring device comprising a rotating shaft for rotating the inner ring, a vibration sensor for measuring radial vibration of the outer ring, and a bearing pressurizing device for applying pressure to the outer ring in the thrust direction, in order to carry out the vibration measurement method described above. 【0011】 The bearing pressurizing device for a bearing vibration measuring device described in Japanese Utility Model Publication No. 52-114737 has a configuration in which the outer ring is pressurized in the thrust direction by a piston pressing multiple load bars, each with its tip in contact with the axial end face of the outer ring, via an inclined plate. For this reason, in order to perform vibration measurement inspection of radial ball bearings of different dimensions, it is necessary to change the radial position of the multiple load bars. However, since it is not easy to change the radial position of multiple load bars supported on a slide, it is difficult to accommodate radial ball bearings of different dimensions. 【0012】 Also, according to the bearing vibration measuring device described in Japanese Patent Publication No. 52-114737, it is possible to inspect the presence or absence of defects on the raceway surface, but it is not possible to specify at which position on the raceway surface the defects are present. 【0013】 An object of the present disclosure is to realize a structure of a bearing pressurizing device that can easily cope with vibration measurement inspections of ball bearings having different dimensions. 【Means for Solving the Problems】 【0014】 A bearing pressurizing device according to one aspect of the present disclosure includes a plurality of linear actuators each having a linear motion part, a pressurizing jig disposed between the plurality of linear actuators and the ball bearing, and pushed in the axial direction of the ball bearing by the respective linear motion parts of the plurality of linear actuators, and rocking displacement or / and translational displacement in the axial direction with respect to one of the pair of raceway rings constituting the ball bearing, and is provided with. 【0015】 The pressurizing jig has a plurality of contact parts arranged on the same virtual circle so as to be able to contact a plurality of circumferential positions on the end face on one axial side facing the pressurizing jig among the other raceway ring of the pair of raceway rings. 【0016】 The plurality of linear actuators pressurize the other outer ring in the thrust direction via the pressurizing jig, and tilt the other raceway ring with respect to the one raceway ring or / and translate it in the axial direction. 【0017】 In the bearing pressurizing device according to one aspect of the present disclosure, the one raceway ring can be an inner ring and the other raceway ring can be an outer ring. Alternatively, in the bearing pressurizing device according to one aspect of the present disclosure, the one raceway ring can be an outer ring and the other raceway ring can be an inner ring. 【0018】 A bearing pressurizing device according to one aspect of the present disclosure may include a plurality of displacement sensors for measuring the inclination and / or axial displacement of the other raceway relative to the one raceway, and a controller for feedback-controlling the plurality of linear actuators based on the output signals of the plurality of displacement sensors. 【0019】 In a bearing pressurizing device according to one aspect of the present disclosure, the plurality of displacement sensors can measure the inclination and / or axial displacement of the other raceway with respect to the other axial end face of the other raceway. 【0020】 In a bearing pressurizing device according to one aspect of the present disclosure, the plurality of displacement sensors can be supported in a manner that allows for adjustment of their radial position relative to the ball bearing. 【0021】 In a bearing pressurizing device according to one aspect of the present disclosure, the plurality of displacement sensors can measure the inclination and / or axial displacement of the other raceway with respect to a portion of the other raceway whose phase in the circumferential direction coincides with the plurality of contact portions. 【0022】 In a bearing pressurizing device according to one aspect of the present disclosure, the pressurizing jig has a substrate that is pressurized by the plurality of linear actuators, and the plurality of contact portions can be fixed to the substrate so as to be able to change the radial position of the ball bearing and / or the circumferential position of the ball bearing. 【0023】 In a bearing pressurizing device according to one aspect of the present disclosure, the plurality of contact portions can be arranged at equal intervals in the circumferential direction of the ball bearing. 【0024】 In a bearing pressurizing device according to one aspect of the present disclosure, the plurality of linear actuators are composed of two linear actuators, and the two linear actuators can be arranged on opposite sides of the central axis of the ball bearing. 【0025】 A bearing vibration measuring device according to one aspect of this disclosure is: A rotating shaft that rotates one of the pair of raceway rings that make up a ball bearing, A bearing pressurizing device that pressurizes the other of the pair of raceway rings in the thrust direction, A vibration sensor for measuring radial vibration of the other raceway, Equipped with, The bearing pressurizing device described above may be a bearing pressurizing device according to one embodiment of the present disclosure. 【0026】 A method for measuring the vibration of a ball bearing according to one aspect of the present disclosure is a method for measuring the vibration of a ball bearing using a bearing vibration measuring device according to one aspect of the present disclosure, While rotating one of the raceways with the aforementioned rotating shaft, the linear motion portion of each of the plurality of linear actuators pushes the pressure jig toward the other axial direction, causing the pressure jig to oscillate and / or translate axially relative to the one raceway, thereby applying thrust pressure to the end face on one axial side of the other raceway with the plurality of contact portions, thereby tilting the other raceway with respect to the one raceway and / or changing its axial position, and measuring the radial vibration of the other raceway with the vibration sensor. 【0027】 A vibration measurement method for a ball bearing according to one aspect of the present disclosure may include the step of selecting a pressure jig from among a plurality of pressure jigs, each having a different diameter for the virtual circle passing through a plurality of contact portions, such that the diameter of the virtual circle is of an appropriate size in relation to the outer diameter of the other raceway ring of the ball bearing to be measured for vibration. 【0028】 In a method for manufacturing a ball bearing according to one aspect of the present disclosure, the vibration measurement step of the ball bearing is performed by a vibration measurement method for a ball bearing according to one aspect of the present disclosure. 【0029】 In a method for manufacturing a vehicle equipped with a ball bearing according to one aspect of the present disclosure, the ball bearing is manufactured by a method for manufacturing a ball bearing according to one aspect of the present disclosure. 【0030】 In a method for manufacturing a mechanical device equipped with a ball bearing according to one aspect of the present disclosure, the ball bearing is manufactured by a method for manufacturing a ball bearing according to one aspect of the present disclosure. [Effects of the Invention] 【0031】 According to one embodiment of the bearing pressurizing device of this disclosure, it is possible to easily handle vibration measurement and inspection of ball bearings of different dimensions. [Brief explanation of the drawing] 【0032】 [Figure 1] Figure 1 is a schematic cross-sectional view showing a bearing vibration measurement inspection of a radial ball bearing using a bearing vibration measuring device equipped with a bearing pressurizing device according to a first example of an embodiment of the present disclosure. [Figure 2] Figure 2 is a partially cutaway perspective view of the radial ball bearing that will be subjected to pressure. [Figure 3] Figure 3(A) is a schematic diagram showing the state in which the pressurizing jig is displaced by translation using a linear actuator, and Figure 3(B) is a schematic diagram showing the state in which the pressurizing jig is displaced by oscillation using a linear actuator. [Figure 4] Figure 4(A) is an end view of the pressurizing jig as seen from the other side in the axial direction, Figure 4(B) is a side view of the pressurizing jig, and Figure 4(C) is an end view of the pressurizing jig as seen from one side in the axial direction. [Figure 5] Figures 5(A) and 5(B) are end views showing two types of pressure jigs with different diameters of virtual circles passing through the contact area. Figure 5(A) is an end view showing a pressure jig with a large diameter of virtual circle passing through the contact area, and Figure 5(B) is an end view showing a pressure jig with a small diameter of virtual circle passing through the contact area. [Figure 6] Figures 6(A) and 6(B) are schematic diagrams illustrating two types of linear actuators. [Figure 7] Figure 7 is a schematic diagram showing a displacement sensor and a radial ball bearing. [Figure 8] Figure 8 is a flowchart illustrating feedback control by a controller. [Figure 9]Figures 9(A) to 9(C) are schematic cross-sectional diagrams of a radial ball bearing. Figure 9(A) shows the outer ring tilted significantly relative to the inner ring, Figure 9(B) shows the outer ring tilted slightly relative to the inner ring, and Figure 9(C) shows the outer ring translated axially relative to the inner ring. [Figure 10] Figure 10 is a cross-sectional view of a motor showing an example of use of a radial ball bearing manufactured by the first example of a radial ball bearing manufacturing method of the embodiments of this disclosure. [Figure 11] Figures 11(A) and 11(B) are end views showing a pressurizing jig used in a second embodiment of the present disclosure, where Figure 11(A) shows the contact portion attached to the radially outer mounting portion, and Figure 11(B) shows the contact portion attached to the radially inner mounting portion. [Figure 12] Figures 12(A) and 12(B) are end views showing a pressurizing jig used in a third embodiment of the present disclosure. Figure 12(A) shows the contact portion attached to mounting parts arranged at equal intervals in the circumferential direction, and Figure 12(B) shows the contact portion attached to mounting parts arranged at unequal intervals in the circumferential direction. [Figure 13] Figures 13(A) and 13(B) are end views showing a pressurizing jig used in a fourth embodiment of the present disclosure. Figure 13(A) shows the jig mounted on a mounting section with three contact points evenly spaced in the circumferential direction, while Figure 13(B) shows the jig mounted on a mounting section with two contact points on opposite sides in the diametrical direction. [Figure 14] Figure 14 is a cross-sectional view of a radial ball bearing, shown to illustrate a conventional vibration measurement method. [Modes for carrying out the invention] 【0033】 [First example of an embodiment] A first example of an embodiment of this disclosure will be described with reference to Figures 1 to 10. 【0034】 [Bearing pressurizing device] The bearing pressurizing device 1 of this disclosure constitutes a bearing vibration measuring device 3 for inspecting whether there are defects in the raceway surface of a radial ball bearing 2, and is a device for applying thrust pressure to the other raceway ring while rotating one of the pair of raceway rings constituting the radial ball bearing 2 by a rotating shaft 22. Specifically, the bearing pressurizing device 1 is a device for tilting and / or axially translating displacement of the other raceway ring relative to the one raceway ring constituting the radial ball bearing 2 by applying thrust pressure to the other raceway ring. 【0035】 As shown in Figure 2, the radial ball bearing 2 to be pressurized comprises an outer ring 4 and an inner ring 5 corresponding to a pair of raceways, and a plurality of balls 6. The outer ring 4 has an outer ring raceway 7 on its inner circumferential surface, which has an arc-shaped cross-section. The inner ring 5 has an inner ring raceway 8 on its outer circumferential surface, which also has an arc-shaped cross-section. The plurality of balls 6 are arranged between the outer ring raceway 7 and the inner ring raceway 8. 【0036】 In this example, one of a pair of raceways will be described as the inner ring 5 and the other as the outer ring 4. That is, the bearing pressurizing device 1 tilts the outer ring 4 relative to the inner ring 5 and / or causes it to be translated axially by applying pressure to the outer ring 4 in the thrust direction. However, the bearing pressurizing device 1 of this disclosure can also tilt the inner ring 5 relative to the outer ring 4 and / or cause it to be translated axially by applying pressure to the inner ring 5 in the thrust direction, with one raceway being the outer ring 4 and the other being the inner ring 5. 【0037】 The radial ball bearing 2 has an arc-shaped cross-section for both the outer ring raceway 7 and the inner ring raceway 8, and uses balls 6 as rolling elements. By applying thrust pressure to the outer ring 4 with the bearing pressurizing device 1, the outer ring 4 can be tilted and / or axially translated relative to the inner ring 5. By tilting and / or axially translating the outer ring 4 relative to the inner ring 5 in this way, it becomes possible to change the range within the raceway surfaces of the outer ring raceway 7 and the inner ring raceway 8 where the balls 6 make strong contact. Therefore, by using the bearing pressurizing device 1 in the vibration measurement method for the radial ball bearing 2, it becomes possible to expand the inspection range of the raceway surface. 【0038】 The type of radial ball bearing 2 to be pressurized is not particularly limited. The bearing pressurizing device 1 can pressurize deep groove radial ball bearings 2, or angular contact radial ball bearings 2. 【0039】 In the following description, unless otherwise specified, axial, radial, and circumferential directions refer to the axial, radial, and circumferential directions of the radial ball bearing 2 that is to be pressurized. Furthermore, the side on which the bearing pressurizing device 1 is located, as viewed from the radial ball bearing 2 (the right side in Figures 1 and 3), is referred to as the axial side, and the side on the opposite side from which the bearing pressurizing device 1 is located, as viewed from the radial ball bearing 2 (the left side in Figures 1 and 3), is referred to as the other axial side. 【0040】 The following description will first explain the basic configuration of the bearing pressurizing device 1 and the effects obtained by having this basic configuration, and then describe the specific configuration of the bearing pressurizing device 1. 【0041】 The bearing pressurizing device 1 is positioned adjacent to one axial side of the radial ball bearing 2 to be pressurized. 【0042】 The bearing pressurizing device 1 comprises a plurality of linear actuators 10a, 10b, each having linear motion parts 9a, 9b, and a pressurizing jig 11, which is positioned between the plurality of linear actuators 10a, 10b and the radial ball bearing 2, and is pushed in the axial direction of the radial ball bearing 2 by the linear motion parts 9a, 9b of the plurality of linear actuators 10a, 10b, causing it to oscillate and / or be translated in the axial direction relative to the inner ring 5 of the radial ball bearing 2. 【0043】 The linear actuators 10a and 10b are elements for applying pressure to the outer ring 4 in the thrust direction (towards the other axial direction) by pushing the pressurizing jig 11 toward the other axial direction. 【0044】 Multiple linear actuators 10a and 10b independently push the pressure jig 11. Specifically, the multiple linear actuators 10a and 10b are arranged in parallel with respect to the pressure jig 11, and each pushes different parts of the pressure jig 11 toward the opposite axial direction. The linear actuators 10a and 10b are only capable of making contact with the pressure jig 11; they are not connected. 【0045】 Linear actuators 10a and 10b are devices that perform mechanical linear motion when energy such as electricity, mechanical, pneumatic, or hydraulic pressure is input to them. 【0046】 The linear actuators 10a and 10b can have any structure as long as they are devices that perform mechanical linear motion when energy such as electricity, machinery, pneumatics, or hydraulics is input. Specifically, the linear actuators 10a and 10b can be composed of, for example, a piezoelectric actuator that uses a piezoelectric element that can convert electrical energy into linear motion, an air cylinder that can convert pneumatic energy into linear motion of a piston, a ball screw mechanism that can convert rotational motion into linear motion, or a rack and pinion mechanism that can convert the rotational motion of a pinion into linear motion of a rack. 【0047】 The linear motion parts 9a and 9b perform linear motion and come into contact with the pressure jig 11, directly pushing the pressure jig 11 in the other axial direction. The linear motion parts 9a and 9b move linearly from a reference position in the other axial direction, pushing the pressure jig 11. 【0048】 The linear motion parts 9a and 9b are arranged parallel to the central axis O2 of the radial ball bearing 2 and move in a linear fashion. That is, the linear motion parts 9a and 9b move in a linear fashion in the axial direction of the radial ball bearing 2. The linear motion parts 9a and 9b are not arranged on the central axis O2 of the radial ball bearing 2, but are arranged in a portion radially off from the central axis O2 of the radial ball bearing 2. 【0049】 When linear actuators 10a and 10b are constructed using piezo actuators, components such as pistons that are pressed by the piezo element and move in a linear motion correspond to the linear motion sections 9a and 9b. When linear actuators 10a and 10b are constructed using air cylinders, pistons that are pressed by air pressure correspond to the linear motion sections 9a and 9b. When linear actuators 10a and 10b are constructed using ball screw mechanisms, the components of the nut and screw shaft that move in a linear motion correspond to the linear motion sections 9a and 9b. When linear actuators 10a and 10b are constructed using rack and pinion mechanisms, the rack corresponds to the linear motion sections 9a and 9b. 【0050】 Multiple linear actuators 10a and 10b each have linear parts 9a and 9b and can independently push the pressurizing jig 11. The system can be composed of two linear actuators or three or more linear actuators. 【0051】 The pressurizing jig 11 is displaced by being pushed in the other axial direction by the respective linear parts 9a and 9b of the multiple linear actuators 10a and 10b, and is an element for applying thrust pressure to the outer ring 4 that constitutes the radial ball bearing 2. 【0052】 The pressurizing jig 11 is positioned coaxially with the radial ball bearing 2 in a neutral state, not being pushed axially by the linear motion parts 9a and 9b. That is, the central axis of the pressurizing jig 11 is O 11 In its neutral position, it is positioned coaxially with the central axis O2 of the radial ball bearing 2. The pressurizing jig 11 cannot be displaced by itself, but is pushed axially by the linear motion parts 9a and 9b, which enables oscillating displacement and / or axial translational displacement of the inner ring 5 of the radial ball bearing 2. 【0053】 The pressure jig 11 is said to oscillate relative to the inner ring 5 of the radial ball bearing 2, meaning that the pressure jig 11 moves along its own central axis O 11 This refers to the displacement such that it is tilted with respect to the central axis O2 of the radial ball bearing 2. The pivoting central axis O2 when the pressurizing jig 11 is oscillating. sThe central axis O2 of the radial ball bearing 2 and the central axis O of the pressurizing jig 11 are 11 They are arranged in directions perpendicular to each of them. 【0054】 The pressurizing jig 11 undergoes displacement corresponding to the axial movement of the linear motion parts 9a and 9b. Specifically, as shown in Figure 3(A), when the axial movement of the linear motion parts 9a and 9b from their reference positions is the same, the pressurizing jig 11 undergoes translational displacement in the axial direction. In contrast, as shown in Figure 3(B), when the axial movement of the linear motion parts 9a and 9b from their reference positions is not the same, the pressurizing jig 11 undergoes oscillating displacement relative to the inner ring 5 of the radial ball bearing 2. Furthermore, the oscillation angle of the pressurizing jig 11 changes according to the difference in the axial movement of the linear motion parts 9a and 9b. 【0055】 The pressurizing jig 11 is directly or indirectly supported by a fixed part, such as the bearing pressurizing device body, allowing for oscillating displacement and axial translational displacement of the inner ring 5 of the radial ball bearing 2. Specifically, the pressurizing jig 11 is supported by a fixed part, for example, using a ball joint and a linear guide, allowing for oscillating displacement and axial translational displacement of the inner ring 5. Furthermore, the pressurizing jig 11 is supported by components such as a ball joint and a linear guide so that it can be easily attached to and detached. 【0056】 The pressurizing jig 11 has multiple contact portions 13a, 13b, and 13c arranged on the same virtual circle C (see Figure 4(A)) so as to be able to contact multiple locations in the circumferential direction of the end face 12 on one axial side of the outer ring 4 that constitutes the radial ball bearing 2, which faces the pressurizing jig 11. 【0057】 The multiple contact points 13a, 13b, and 13c are elements for applying pressure to a portion of the circumferential direction of one end face 12 on the axial side of the outer ring 4. The pressurizing jig 11 does not come into contact with the outer ring 4 in any part other than the contact points 13a, 13b, and 13c. 【0058】 The center of the virtual circle C passing through the central axes of each of the multiple contact points 13a, 13b, and 13c is the central axis O of the pressurizing jig 11. 11It is located at the top. 【0059】 The diameter D of the virtual circle C 13 The size of the outer ring D is arbitrary, as long as it is smaller than the outer diameter of the outer ring 4 to be pressurized and larger than the inner diameter of the outer ring 4. However, the diameter D 13 It is preferable that the size is about half the sum of the outer diameter and inner diameter of the outer ring 4. 【0060】 The number of contact points 13a, 13b, and 13c on the pressurizing jig 11 is arbitrary. The pressurizing jig may have two contact points or three or more contact points. 【0061】 The circumferential arrangement of the multiple contact portions 13a, 13b, and 13c is arbitrary, as long as the multiple contact portions 13a, 13b, and 13c can tilt the outer ring 4 relative to the inner ring 5 and cause the outer ring 4 to be translated in the axial direction. The multiple contact portions 13a, 13b, and 13c can be arranged at equal intervals in the circumferential direction or at unequal intervals in the circumferential direction. 【0062】 Specifically, for example, if a pressure jig has two contact points, the two contact points are equally spaced at 180 degrees in the circumferential direction. If a pressure jig has three or more contact points, the three or more contact points can be equally spaced in the circumferential direction or unequally spaced in the circumferential direction, as long as the central angle between any two adjacent contact points in the circumferential direction is 180 degrees or less. 【0063】 The contact portions 13a, 13b, and 13c are preferably made of a material that is resistant to elastic deformation. Specifically, the contact portions 13a, 13b, and 13c are preferably made of metal or a resin that is resistant to elastic deformation. 【0064】 The contact portions 13a, 13b, and 13c may be integrally configured with other parts of the pressurizing jig 11 that are not pressed axially by the linear motion parts 9a, 9b, or they may be configured separately from the other parts and fixed to the other parts. When the contact portions 13a, 13b, and 13c are fixed to the other parts, they may be fixed in a removable manner or in a non-removable manner. When the contact portions 13a, 13b, and 13c are fixed in a removable manner to the other parts, it becomes possible to replace the contact portions 13a, 13b, and 13c when they wear out. 【0065】 Multiple linear actuators 10a and 10b apply pressure to the outer ring 4 in the thrust direction via a pressurizing jig 11 having the configuration described above, causing the outer ring 4 to tilt and / or be translated in the axial direction relative to the inner ring 5. 【0066】 Therefore, the bearing pressurizing device 1 of this disclosure can pressurize the outer ring 4 of radial ball bearings 2 of different dimensions in the thrust direction simply by changing the pressurizing jig 11 according to the outer diameter of the outer ring 4 of the radial ball bearing 2 to be pressed. Specifically, the bearing pressurizing device 1 of this disclosure can pressurize the outer ring 4 in the thrust direction without changing any parts other than the pressurizing jig 11 by selecting and using a pressurizing jig 11 from among a plurality of pressurizing jigs 11 with different diameters of virtual circles passing through a plurality of contact portions 13a, 13b, and 13c, the diameter of which is suitable for the outer diameter of the outer ring 4 of the radial ball bearing 2 to be pressed. 【0067】 For example, if you have eight pressurizing jigs 11x with a diameter Dx of a virtual circle C passing through multiple contact points 13a, 13b, and 13c, as shown in Figure 5(A), and eight pressurizing jigs 11y with a diameter Dy of a virtual circle C passing through multiple contact points 13a, 13b, and 13c, as shown in Figure 5(B), then you can select and use one of the two pressurizing jigs 11a and 11b that is suitable for the outer diameter of the outer ring 4 of the radial ball bearing 2 to be pressed. 【0068】 Therefore, the bearing pressurizing device 1 of this disclosure can easily handle vibration measurement and inspection of radial ball bearings 2 of different dimensions. Furthermore, by using the bearing pressurizing device 1 of this disclosure, it is possible to change the range in which the balls 6 make strong contact with the raceway surfaces of the outer ring raceway 7 and the inner ring raceway 8. Therefore, by using the bearing vibration measuring device 3 equipped with the bearing pressurizing device 1 of this disclosure, the inspection range of the raceway surfaces of the outer ring raceway 7 and the inner ring raceway 8 can be expanded. As a result, the presence or absence of defects in the raceway surfaces can be inspected with high accuracy. 【0069】 In this example, the pressurizing jig 11 has three contact points 13a, 13b, and 13c. The three contact points 13a, 13b, and 13c are arranged at equal intervals in the circumferential direction. 【0070】 In this example, the pressurizing jig 11 has a substrate 14 in addition to the three contact parts 13a, 13b, and 13c. 【0071】 The substrate 14 is an element that is pushed in the axial direction by the linear parts 9a and 9b of the multiple linear actuators 10a and 10b. 【0072】 The substrate 14 is configured in a flat plate shape and has a pressed surface 15 on one end face on its axial side that is pressed axially by the linear motion parts 9a and 9b. The pressed surface 15 is on the central axis O of the pressurizing jig 11. 11 It is composed of flat surfaces perpendicular to each other. 【0073】 The contact portions 13a, 13b, and 13c are provided on the other end face of the substrate 14 on the axial side. The contact portions 13a, 13b, and 13c protrude axially from the other end face of the substrate 14 on the axial side. The tips of the contact portions 13a, 13b, and 13c are formed by convex curved surfaces. Therefore, even when the pressurizing jig 11 is oscillating, the contact state between the tips of the contact portions 13a, 13b, and 13c and the end face 12 on one end face of the outer ring 4 on the axial side can be stabilized. 【0074】 The multiple contact portions 13a, 13b, and 13c can be configured integrally with the substrate 14, or they can be configured separately from the substrate 14. If the contact portions 13a, 13b, and 13c are configured separately from the substrate 14, they may be fixed to the substrate 14 in a removable manner, or they may be fixed in a non-removable manner. 【0075】 If the contact portions 13a, 13b, and 13c are to be removably fixed to the substrate 14, for example, the contact portions 13a, 13b, and 13c can be removably fixed to the substrate 14 by screwing the male or female threaded portion provided on the contact portions 13a, 13b, and 13c to the female or male threaded portion provided on the substrate 14. 【0076】 If the contact portions 13a, 13b, and 13c are detachably fixed to the substrate 14, the contact portions 13a, 13b, and 13c can be fixed to the substrate 14 in such a way that their radial position and / or circumferential position of the radial ball bearing 2 can be changed. 【0077】 If the contact portions 13a, 13b, and 13c are permanently fixed to the other axial end face of the substrate 14, the contact portions 13a, 13b, and 13c can be fixed to the other axial end face of the substrate 14, for example, by welding or adhesive bonding. 【0078】 In this example, the contact portions 13a, 13b, and 13c are configured separately from the substrate 14 and are removably fixed to the substrate 14, but the mounting position cannot be changed. That is, the substrate 14 has mounting portions (not shown) equal in number to the contact portions 13a, 13b, and 13c on a virtual circle C centered on the central axis O of the pressing jig 11. The contact portions 13a, 13b, and 13c are removably fixed to the mounting portions. In this example, the contact portions 13a, 13b, and 13c are constituted by pins. 11 The substrate 14 can have an arbitrary contour shape as long as the contact portions 13a, 13b, and 13c are provided at positions where they can contact the end face 12 on one axial side of the outer ring 4. In this example, the substrate 14 has a circular contour shape. For this reason, the substrate 14 is configured in a circular plate shape. 【0079】 In this example, the linear actuators 10a and 10b include stationary portions 16a and 16b in addition to the linear moving portions 9a and 9b. 【0080】 The stationary portions 16a and 16b are fixed to a fixed part and are elements for preventing the portions other than the linear moving portions 9a and 9b of the linear actuators 10a and 10b from moving. The stationary portions 16a and 16b are fixed to, for example, the gantry constituting the bearing pressing device 1. 【0081】 When the linear actuators 10a and 10b are constituted by piezo actuators, components such as a casing for housing piezo elements correspond to the stationary portions 16a and 16b. When the linear actuators 10a and 10b are constituted by air cylinders, the cylinders correspond to the stationary portions 16a and 16b. When the linear actuators 10a and 10b are constituted by ball screw mechanisms, components such as a casing for housing nuts and screw shafts correspond to the stationary portions 16a and 16b. When the linear actuators 10a and 10b are constituted by rack and pinion mechanisms, components such as a casing for housing racks correspond to the stationary portions 16a and 16b. 【0082】 【0083】 ​In this example, the multiple linear actuators 10a and 10b are composed of two linear actuators 10a and 10b. This allows for miniaturization of the bearing pressurizing device 1 and simplification of the control of the linear actuators 10a and 10b. The two linear actuators 10a and 10b are positioned on opposite sides of the radial ball bearing 2 in the diametrical direction, with the central axis O2 of the radial ball bearing 2 in between. In particular, in this example, the two linear actuators 10a and 10b are positioned 180 degrees opposite each other with respect to the central axis O2 of the radial ball bearing 2. Therefore, when the pressurizing jig 11 oscillates, the pressurizing jig 11 moves along its own central axis O 11 The central axis O of the two linear motion parts 9a and 9b is perpendicular to the same direction. 9a , O 9b The oscillation center axis O is perpendicular to the imaginary line passing through it. s It oscillates around this point. 【0084】 When multiple linear actuators are composed of two linear actuators, it is sufficient that the two linear actuators are positioned on opposite sides of the radial ball bearing in the radial direction, with the central axis of the radial ball bearing in between; it is not necessary for them to be positioned 180 degrees opposite each other with respect to the central axis of the radial ball bearing. 【0085】 In this example, as shown in Figure 4(C), the central axis O2 of the linear actuator 10a is located from the central axis O2 of the radial ball bearing 2 to the central axis O2 of the linear actuator 10a. 9a The distance A to the central axis O2 of the radial ball bearing 2 and the central axis O2 of the linear actuator 10b's linear section 9b 9b The distances B to and from point A and point B are equal (A=B). 【0086】 When multiple linear actuators are composed of two linear actuators, the distance from the central axis of the radial ball bearing to the central axis of the linear part of one linear actuator and the distance from the central axis of the radial ball bearing to the central axis of the linear part of the other linear actuator may be different from each other. When tilting the pressurizing jig 11 with multiple linear actuators, the greater the distance from the central axis of the radial ball bearing to the central axis of the linear part of the linear actuator, the more precisely the tilt of the pressurizing jig 11 can be controlled, and the greater the moment force applied to the pressurizing jig 11, which has the advantage of requiring less force from the linear actuators. 【0087】 In this example, the distances A and B are the diameter D of the virtual circle C passing through the three contact points 13a, 13b, and 13c. 13 Equal to 1 / 2 of (A=B=D 13 ( / 2). However, the distance A and the distance B are equal to the diameter D 13 It may be larger than 1 / 2 of the diameter D 13 It can be smaller than half of that. 【0088】 In this example, as shown in Figures 4(A) and 4(C), of the two linear actuators 10a and 10b, the linear actuator 10b located on the lower side of Figure 1 is positioned so that its phase in the circumferential direction coincides with one of the three contact points 13a, 13b, and 13c, which is contact point 13c. In contrast, of the two linear actuators 10a and 10b, the linear actuator 10a located on the upper side of Figure 1 is positioned so that its phase in the circumferential direction coincides with the circumferential center of the remaining two contact points 13a and 13b. 【0089】 In this example, the linear motion parts 9a and 9b have tip pins 17a and 17b. The tip pins 17a and 17b are elements that come into contact with the pressurizing jig 11. 【0090】 The tip pins 17a and 17b are provided at the tip portions (the ends on the other axial side) of the linear motion portions 9a and 9b, and contact the pressed surface 15 of the substrate 14 that constitutes the pressurizing jig 11. The tips of the tip pins 17a and 17b are made of convex curved surfaces. Therefore, even when the pressurizing jig 11 is in a state of oscillating displacement, the contact state between the tips of the tip pins 17a and 17b and the pressed surface 15 of the pressurizing jig 11 can be stabilized. 【0091】 The tip pins 17a and 17b are preferably made from a material that is resistant to elastic deformation. The tip pins 17a and 17b are made from metal or a resin that is resistant to elastic deformation. 【0092】 In this example, the tip pins 17a and 17b are constructed separately from the linear motion sections 9a and 9b and are detachably fixed to the tips of the linear motion sections 9a and 9b. Therefore, when the tip pins 17a and 17b wear out, they can be replaced. 【0093】 In this example, the tip pin 17b provided on the linear motion section 9b that constitutes the linear actuator 10b located on the lower side of Figure 1 consists of one tip pin 17b, as shown in Figure 6(A). In contrast, the tip pin 17a provided on the linear motion section 9a that constitutes the linear actuator 10a located on the upper side of Figure 1 consists of two tip pins 17a, as shown in Figure 6(B). In other words, the tip pin 17a has a bifurcated shape. This prevents the pressurizing jig 11 from tilting so that one of the two contact sections 13a, 13b moves axially to the other side of the other contact section 13b (or contact section 13a) due to the thrust force applied to the pressurizing jig 11 from the linear motion section 9a. However, the tip pins provided on the linear motion sections 9a and 9b that constitute the two linear actuators 10a and 10b can each be made from a single tip pin or from a tip pin with a bifurcated shape. 【0094】 In this example, the linear actuators 10a and 10b are equipped with load cells 18a and 18b as optional components. 【0095】 Load cells 18a and 18b are elements for measuring the magnitude of the thrust load acting on the linear motion parts 9a and 9b. The load cells 18a and 18b are positioned between the linear motion parts 9a and 9b and the stationary parts 16a and 16b, and measure the magnitude of the thrust load applied to the linear motion parts 9a and 9b when the pressurizing jig 11 is pushed in the other axial direction. The output signals from load cells 18a and 18b are transmitted to a controller 20, which will be described later, and the controller 20 determines whether the magnitude of the thrust load applied to the linear motion parts 9a and 9b is within an appropriate range. This prevents excessive thrust force from being applied to the rotating shaft 22 that rotatably supports the inner ring 5 of the radial ball bearing 2. 【0096】 In this example, the bearing pressurizing device 1 includes, in addition to the linear actuators 10a and 10b and the pressurizing jig 11, a plurality of displacement sensors 19a, 19b, and 19c, and a controller 20. 【0097】 Multiple displacement sensors 19a, 19b, and 19c are elements for measuring the inclination and / or axial displacement of the outer ring 4 relative to the inner ring 5. Specifically, the multiple displacement sensors 19a, 19b, and 19c measure the inclination and / or axial displacement of the outer ring 4 relative to the inner ring 5, with the outer ring 4 of the radial ball bearing in a neutral state where it is not pressurized by the pressurizing jig 11. 【0098】 The displacement sensors 19a, 19b, and 19c can have any structure as long as they can measure the tilt and / or axial displacement of the outer ring 4. The displacement sensors 19a, 19b, and 19c can be composed of non-contact displacement sensors such as optical displacement sensors, or contact displacement sensors such as electric macrometers. Non-contact displacement sensors have a fast response speed and are suitable for feedback control, thus reducing the inspection time of the radial ball bearing 2. Contact displacement sensors require periodic replacement of the contacts because the contacts of the contact sensor wear out due to repeated contact with the outer ring 4, but they are less susceptible to changes in the external environment, allowing for accurate inspection of the radial ball bearing 2 in harsh factory environments. 【0099】 If the multiple displacement sensors 19a, 19b, and 19c can measure the inclination and / or axial displacement of the outer ring 4, they may measure the inclination and / or axial displacement of the outer ring 4 with respect to the axial end face of the outer ring 4, or the outer or inner circumferential surface of the outer ring 4. In this example, the multiple displacement sensors 19a, 19b, and 19c are arranged on the other axial side of the radial ball bearing 2, with their respective detection units facing the other axial end face of the outer ring 4. That is, the multiple displacement sensors 19a, 19b, and 19c measure the inclination and / or axial displacement of the outer ring 4 with respect to the other axial end face of the outer ring 4. 【0100】 Furthermore, the detection positions of the multiple displacement sensors 19a, 19b, and 19c in the circumferential direction of the outer ring 4 are also arbitrary. In this example, the multiple displacement sensors 19a, 19b, and 19c measure the inclination and / or axial displacement of the outer ring 4 at the portion of the end face 12 on one axial side of the outer ring 4 where the contact portions 13a, 13b, and 13c make contact and where their phases in the circumferential direction coincide. 【0101】 The multiple displacement sensors 19a, 19b, and 19c can consist of two displacement sensors or three or more displacement sensors. In this example, the multiple displacement sensors 19a, 19b, and 19c are composed of the same number of displacement sensors as the multiple contact parts 13a, 13b, and 13c provided on the pressurizing jig 11. That is, in this example, the multiple displacement sensors 19a, 19b, and 19c are composed of three displacement sensors. 【0102】 In this example, multiple displacement sensors 19a, 19b, and 19c are supported in a way that allows for adjustment of their position relative to the radial direction (radial direction) of the radial ball bearing 2. Therefore, the radial positions of the displacement sensors 19a, 19b, and 19c can be changed according to the outer diameter of the outer ring 4 of the radial ball bearing 2 to be pressed, making it easy to perform vibration measurement inspections of radial ball bearings 2 of different dimensions. 【0103】 The specific structure for adjusting the radial positions of the displacement sensors 19a, 19b, and 19c is arbitrary. The radial positions of the displacement sensors 19a, 19b, and 19c can be adjusted using, for example, a lead screw mechanism or a linear guide. In this example, as shown in Figure 7, the radial positions of the displacement sensors 19a, 19b, and 19c can be adjusted using the same number of lead screw mechanisms 21a, 21b, and 21c as the displacement sensors 19a, 19b, and 19c. 【0104】 The controller 20 is an element for feedback control of multiple linear actuators 10a and 10b based on the output signals of multiple displacement sensors 19a, 19b, and 19c. 【0105】 The controller 20 is electrically connected to multiple displacement sensors 19a, 19b, and 19c, and multiple linear actuators 10a and 10b, respectively. In this example, in addition to the displacement sensors 19a, 19b, and 19c, and the linear actuators 10a and 10b, the controller 20 is also electrically connected to a vibration sensor 23 and load cells 18a and 18b. 【0106】 The feedback control by controller 20 will be explained using the flowchart in Figure 8. 【0107】 In step 1, the controller 20 first sends command signals to the multiple linear actuators 10a and 10b, respectively, to move the linear units 9a and 9b to the commanded positions. That is, it moves each of the linear units 9a and 9b linearly by a predetermined amount toward the other axial direction. 【0108】 This causes the pressurizing jig 11 to oscillate and / or be translated axially, thereby applying thrust pressure to the outer ring 4 of the radial ball bearing 2 to be pressed by the multiple contact points 13a, 13b, and 13c of the pressurizing jig 11. This also causes the outer ring 4 to tilt and / or be translated axially relative to the inner ring 5. 【0109】 Next, in step 2, the controller 20 reads the output signal values ​​of each of the multiple displacement sensors 19a, 19b, and 19c. 【0110】 Next, in step 3, the controller 20 calculates the tilt and axial displacement (axial position) of the outer ring 4 relative to the inner ring 5 based on the output signal values ​​of the multiple displacement sensors 19a, 19b, and 19c. 【0111】 Next, in step 4, the controller 20 calculates the difference between the calculated values ​​of the tilt and axial displacement of the outer ring 4 and the target values ​​of the tilt and axial displacement of the outer ring 4. 【0112】 Next, in step 5, the controller 20 determines whether the difference between the calculated value and the target value is zero (including substantially zero). If the difference between the calculated value and the target value is zero, the feedback control is terminated. On the other hand, if the difference between the calculated value and the target value is not zero, the process proceeds to the following step 6. 【0113】 Next, in step 6, the controller 20 determines the correction amounts for the multiple linear actuators 10a and 10b from the difference between the calculated values ​​and the target values. Specifically, it determines the axial displacement amounts of the linear units 9a and 9b, which are necessary to bring the tilt and axial displacement amounts of the outer ring 4 to the target values. 【0114】 Next, in step 7, the controller 20 sends correction command signals to each of the linear actuators 10a and 10b, causing each of the linear actuators 9a and 9b to be displaced axially by the correction amount. 【0115】 Then, return to step 2, and in step 5, repeat steps 2 through 7 until the difference between the calculated value and the target value is determined to be zero. 【0116】 By performing this type of feedback control, the inclination and axial displacement of the outer ring 4 relative to the inner ring 5 can be set to target values, allowing for a correlation between the presence or absence of defects and the inspection range of the raceway surface. Therefore, the location of the defect on the raceway surface can be identified. 【0117】 [Vibration measuring device] The bearing pressurizing device 1 is combined with a rotating shaft 22 that rotates the inner ring 5 and a vibration sensor 23 that measures radial vibrations of the outer ring 4 to form a bearing vibration measuring device 3. 【0118】 The bearing vibration measuring device 3 rotates the inner ring 5 of the radial ball bearing 2 by a rotating shaft 22, and pressurizes the outer ring 4 of the radial ball bearing 2 in the thrust direction by a bearing pressurizing device 1, thereby tilting the outer ring 4 relative to the inner ring 5 and / or displacing it in the axial direction. The device measures the radial vibration of the outer ring 4 using a vibration sensor 23 and inspects whether there are any defects such as scratches or delamination on the raceway surfaces of the outer ring raceway 7 and the inner ring raceway 8. 【0119】 The rotating shaft 22 is an element for rotating the inner ring 5. The rotating shaft 22 has a fitting shaft portion 24 into which the inner ring 5 is fitted and fixed. The rotating shaft 22 is positioned coaxially with the pressurizing jig 11 in the neutral position and rotates around its own central axis. The rotating shaft 22 is connected to, for example, the output shaft of a drive motor and is driven to rotate at a predetermined rotational speed. In this example, the rotating shaft 22 is composed of a spindle. 【0120】 The vibration sensor 23 is an element for measuring radial vibration of the outer ring 4. The structure of the vibration sensor 23 is arbitrary as long as it can measure radial vibration of the outer ring 4. The vibration sensor 23 can be composed of, for example, a velocity sensor, an acceleration sensor, a displacement sensor, etc. In this example, the vibration sensor 23 is composed of a velocity sensor and is detachably fixed to one or more locations in the circumferential direction on the outer surface of the outer ring 4. 【0121】 The vibration sensor 23 detects radial vibrations that occur when the ball 6 passes over a defect present on the raceway surface. Therefore, based on the detection signal from the vibration sensor 23, it is possible to inspect whether or not a defect exists on the raceway surface. 【0122】 [Vibration Measurement Method] This section describes a method for measuring the vibration of a radial ball bearing 2 using a bearing vibration measuring device 3. 【0123】 First, as a first preparation step, one pressure jig 11 suitable for the radial ball bearing 2 to be inspected is selected from among a plurality of pressure jigs 11. Specifically, from among a plurality of pressure jigs 11 with different diameters of virtual circles passing through a plurality of contact portions 13a, 13b, and 13c, one pressure jig 11 is selected in which the diameter of the virtual circle is suitable for the outer diameter of the outer ring 4 of the radial ball bearing 2 to be measured for vibration. More specifically, one pressure jig 11 is selected in which the diameter of the virtual circle is smaller than the outer diameter of the outer ring 4 and larger than the inner diameter of the outer ring 4. Then, the selected pressure jig 11 is supported with respect to the fixed part of the bearing pressurizing device 1, for example, using a ball joint and a linear guide, so that the oscillating displacement and axial translational displacement of the inner ring 5 of the radial ball bearing 2 can be controlled. 【0124】 Furthermore, as a second preparation step, the inner ring 5 of the radial ball bearing 2 is fitted onto the mating shaft portion 24 of the rotating shaft 22. The inner ring 5 of the radial ball bearing 2 can be fitted onto the mating shaft portion 24 either by clearance fitting or by interference fitting. Even when the inner ring 5 of the radial ball bearing 2 is fitted onto the mating shaft portion 24 by clearance fitting, the outer ring 4 is pressurized in the thrust direction by the bearing pressurizing device 1, causing the other axial end face of the inner ring 5 to come into contact with a part of the rotating shaft 22. Due to the frictional force acting between the other axial end face of the inner ring 5 and a part of the rotating shaft 22, the inner ring 5 does not rotate relative to the mating shaft portion 24. When the inner ring 5 of the radial ball bearing 2 is fitted onto the mating shaft portion 24 by clearance fitting, the workability of attaching and detaching the radial ball bearing 2 to and from the mating shaft portion 24 can be improved. 【0125】 Furthermore, as a third preparation step, the radial positions of the multiple displacement sensors 19a, 19b, and 19c constituting the bearing pressurizing device 1 are adjusted using the lead screw mechanisms 21a, 21b, and 21c. Specifically, the radial positions of the displacement sensors 19a, 19b, and 19c are adjusted so that the detection parts of each of the displacement sensors 19a, 19b, and 19c face the other axial end face of the outer ring 4 of the radial ball bearing 2. 【0126】 The order of the first preparation step, the second preparation step, and the third preparation step can be changed as appropriate. 【0127】 Next, as an inspection step, the inner ring 5 is rotated by the rotating shaft 22 while the outer ring 4 is pressed in the thrust direction by the bearing pressurizing device 1. Specifically, the linear parts 9a and 9b of the multiple linear actuators 10a and 10b push the pressurizing jig 11 toward the other axial direction, causing the pressurizing jig 11 to oscillate and / or be translated axially relative to the inner ring 5. Then, the multiple contact parts 13a, 13b, and 13c of the pressurizing jig 11 pressurize the end face 12 on one axial side of the outer ring 4 in the thrust direction. This causes the outer ring 4 to tilt and / or be translated axially relative to the inner ring 5. Note that the outer ring 4 does not rotate because it is pressed in the thrust direction by the pressurizing jig 11, and is not pulled along by the inner ring 5. When the inner ring is pressed in the thrust direction by the bearing pressurizing device while the outer ring is rotated by the rotating shaft as an inspection step, the inner ring does not rotate because it is pressed in the thrust direction by the pressurizing jig, and is not pulled along by the outer ring. 【0128】 In this manner, while the inner ring 5 is rotated, the outer ring 4 is tilted relative to the inner ring 5 and / or its axial position is changed, and the radial vibration of the outer ring 4 is measured by the vibration sensor 23. 【0129】 In this example, during the inspection process, the controller 20 provides feedback control to the linear actuators 10a and 10b based on the output signals of multiple displacement sensors 19a, 19b, and 19c. 【0130】 Such a vibration measurement method for radial ball bearings 2 can constitute a part of the manufacturing process for radial ball bearings 2, as a vibration measurement step for radial ball bearings 2. Specifically, it can be performed as part of the pre-shipment inspection process for radial ball bearings 2. Radial ball bearings 2 manufactured by this manufacturing method are used by being incorporated into motors 25, as shown in Figure 10, as well as by being incorporated into rotating support parts of vehicles such as electric vehicles where high acoustic performance is required, and various mechanical devices such as air conditioning systems and pulley systems. 【0131】 The bearing vibration measuring device 3 of this disclosure can measure the vibration of the outer ring 4 while the outer ring 4 is tilted and / or translated in the axial direction relative to the inner ring 5 by applying pressure to the outer ring 4 in the thrust direction using the bearing pressurizing device 1. This makes it possible to widen the inspection range of the raceway surfaces of the outer ring raceway 7 and the inner ring raceway 8. 【0132】 Specifically, as shown in Figure 9(A), when the outer ring 4 is tilted significantly relative to the inner ring 5, the X1 range of the outer ring raceway 7 and the Y1 range of the inner ring raceway 8 can be inspected. Also, as shown in Figure 9(B), when the outer ring 4 is tilted slightly relative to the inner ring 5, the X2 range of the outer ring raceway 7 and the Y2 range of the inner ring raceway 8 can be inspected. Furthermore, as shown in Figure 9(C), when the outer ring 4 is axially displaced relative to the inner ring 5, the X3 range of the outer ring raceway 7 and the Y3 range of the inner ring raceway 8 can be inspected. Therefore, the bearing vibration measuring device 3 of this disclosure can measure the presence or absence of defects over a wide range of the raceway surface. As a result, the acoustic performance of the radial ball bearing 2 can be improved. It should be noted that, as is clear from Figures 9(A) to 9(C), the range of the raceway surface that can be inspected with the radial ball bearing 2 set up is X1 to X3 and Y1 to Y3. Therefore, if you need to inspect a range beyond that, you can simply reverse the radial ball bearing 2 axially, reset it, and perform the measurement. 【0133】 In particular, the bearing vibration measuring device 3 of this disclosure can perform vibration measurement and inspection on radial ball bearings 2 of different dimensions simply by changing the pressure jig 11 according to the outer diameter of the outer ring 4 of the radial ball bearing to be pressed. Specifically, the bearing vibration measuring device 3 of this disclosure can pressurize the outer ring 4 in the thrust direction without changing any parts other than the pressure jig 11 by selecting and using a pressure jig 11 from among several pressure jigs 11 with different diameters of virtual circles passing through multiple contact portions 13a, 13b, and 13c, the diameter of which is suitable for the outer diameter of the outer ring 4 of the radial ball bearing 2 to be pressed. Therefore, the bearing vibration measuring device 3 of this disclosure can easily handle vibration measurement and inspection of radial ball bearings 2 of different dimensions. 【0134】 The bearing vibration measuring device 3 of this disclosure can perform vibration inspections while feedback-controlling the linear actuators 10a and 10b based on the output signals of the displacement sensors 19a, 19b, and 19c. Therefore, it is possible to correlate the presence or absence of defects with the inspection range of the raceway surface, and to identify the location of the defects on the raceway surface. 【0135】 The vibration measurement method for radial ball bearings described above can be applied to the process of manufacturing radial ball bearings in the manufacturing method of a vehicle equipped with radial ball bearings, and to the process of manufacturing radial ball bearings in the manufacturing method of a mechanical device equipped with radial ball bearings. 【0136】 [Second example of an embodiment] A second example of the embodiments of this disclosure will be described with reference to Figures 11(A) and 11(B). 【0137】 In this example, the structure of the pressure jig 11a that constitutes the bearing pressurizing device 1 is different from the structure of the pressure jig 11 in the first example. 【0138】 In this example, the pressure jig 11a has its central axis O on the other axial end face of the substrate 14a. 11 Multiple mounting parts 26a are arranged on a first virtual circle C1 centered on and the central axis O 11It has a center and a plurality of mounting parts 26b arranged on a second virtual circle C2 which has a different diameter from the first virtual circle C1. The mounting parts 26a and 26b have a structure that allows the contact parts 13a, 13b, and 13c to be detachably fixed. 【0139】 In this example, the mounting portions 26a and 26b are provided in the same number as the contact portions 13a, 13b, and 13c. Furthermore, the mounting portions 26a and 26b are arranged at equal intervals in the circumferential direction. 【0140】 Figure 11(A) shows the state in which the contact portions 13a, 13b, and 13c are fixed to multiple mounting portions 26a arranged on the first virtual circle C1. Figure 11(B) shows the state in which the contact portions 13a, 13b, and 13c are fixed to multiple mounting portions 26b arranged on the second virtual circle C2. 【0141】 The pressurizing jig 11a in this example allows for changing the radial positions of the contact portions 13a, 13b, and 13c. Therefore, using a single pressurizing jig 11a, it is possible to apply thrust pressure to the outer ring 4 of radial ball bearings 2 of different dimensions. Consequently, in this example, only the positions of the contact portions 13a, 13b, and 13c need to be changed, eliminating the need to replace the pressurizing jig 11a itself. This reduces the preparation time required. 【0142】 In this example, the substrate 14a has multiple mounting parts 26a and 26b on two first virtual circles C1 and a second virtual circle C2 arranged concentrically. However, the substrate constituting the pressurizing jig may also have multiple mounting parts on three or more virtual circles arranged concentrically. 【0143】 The composition and effects of the other parts of the second example are the same as those of the first example. 【0144】 [Third example of an embodiment] A third example of the embodiments of this disclosure will be described with reference to Figures 12(A) and 12(B). 【0145】 In this example, the structure of the pressure jig 11b that constitutes the bearing pressurizing device 1 is different from the structure of the pressure jig 11 in the first example and the pressure jig 11a in the second example. 【0146】 In this example, the pressure jig 11b has its central axis O on the other axial end face of the substrate 14b. 11 It has multiple mounting parts 26c, 26d arranged on a virtual circle C centered on [the specified point]. Specifically, the pressurizing jig 11b in this example has a total of five mounting parts 26c, 26d. Three of the mounting parts 26c are arranged at equal intervals in the circumferential direction. In contrast, the remaining two mounting parts 26d are arranged between two adjacent mounting parts 26c in the circumferential direction. 【0147】 Figure 12(A) shows the state in which the three contact parts 13a, 13b, and 13c are fixed to three mounting parts 26c that are arranged at equal intervals in the circumferential direction. Figure 12(B) shows the three contact parts 13a, 13b, and 13c being fixed to two mounting parts 26d and the central axis O of the pressurizing jig 11a. 11 This shows the device fixed to one mounting part 26c, which is located on the opposite side of the two mounting parts 26d that are sandwiched between them. 【0148】 In this example, the pressurizing jig 11b allows for easy modification of the pressurizing position of the outer ring 4 because the circumferential positions of the contact portions 13a, 13b, and 13c can be changed. Therefore, even if the bearing size to be pressurized changes, only the positions of the contact portions 13a, 13b, and 13c need to be changed, eliminating the need to replace the pressurizing jig 11b itself. Consequently, set changes are made easier, and the preparation time can be reduced. Furthermore, the number of contact portions 13a, 13b, and 13c can be increased or decreased. 【0149】 The composition and effects of the other parts of the third example are the same as those of the first example. 【0150】 [Fourth example of an embodiment] A fourth example of the embodiments of this disclosure will be described with reference to Figures 13(A) and 13(B). This example is a modification of the third example. 【0151】 In this example, the pressure jig 11c has its central axis O on the other axial end face of the substrate 14c. 11 It has multiple mounting parts 26c, 26d arranged on a virtual circle C centered on [the specified point]. Specifically, the pressurizing jig 11b in this example has a total of four mounting parts 26c, 26d. Three of the mounting parts 26c are arranged at equal intervals in the circumferential direction. In contrast, the remaining mounting part 26d is positioned in the circumferential center of two adjacent mounting parts 26c in the circumferential direction. 【0152】 Figure 13(A) shows the state in which the three contact parts 13a, 13b, and 13c are fixed to three mounting parts 26c that are arranged at equal intervals in the circumferential direction. Figure 13(B) shows the state in which the two contact parts 13a and 13b are fixed to the central axis O of the pressurizing jig 11a. 11 This shows the device fixed to mounting portion 26d and one mounting portion 26c, which are located on opposite sides in the diametrical direction, with the other mounting portion in between. 【0153】 In this example, the pressure jig 11c allows for easy adjustment of the pressure position of the outer ring 4 because the circumferential positions of the contact portions 13a, 13b, and 13c can be changed. Therefore, simply changing the positions of the contact portions 13a, 13b, and 13c eliminates the need to replace the pressure jig 11c itself. Consequently, the preparation time can be reduced. Furthermore, the number of contact portions 13a, 13b, and 13c can be increased or decreased as needed. 【0154】 The composition and effects of the other parts of the fourth example are the same as those of the first example. 【0155】 The first to fourth embodiments of this disclosure can be combined as appropriate, as long as they do not create any inconsistencies. [Explanation of Symbols] 【0156】 1. Bearing pressurizing device 2 Radial ball bearings 3 Bearing vibration measuring device 4 Outer ring 5. Inner Ring 6 balls 7 Outer ring track 8. Inner track 9a, 9b Linear motion section 10a, 10b Linear Actuators 11, 11a, 11b, 11c, 11x, 11y Pressurizing jig 12 End face 13a, 13b, 13c contact area 14 circuit boards 15 Pressed surface 16a, 16b Stationary part 17a, 17b tip pins 18a, 18b load cells 19a, 19b, 19c Displacement sensors 20 Controllers 21a, 21b, 21c Lead screw mechanism 22 Rotation axis 23 Vibration Sensor 24 Fitting shaft 25 Motor 26a~26d Mounting section 100 inner ring 101 Outer ring 102 Outer Ring Track 103 Inner track 104 balls

Claims

[Claim 1] Multiple linear actuators, each having a linear motion section that moves in a straight line, A pressurizing jig is positioned between the plurality of linear actuators and the ball bearing, and is pushed in the axial direction of the ball bearing by the linear portion of each of the plurality of linear actuators, causing it to oscillate and / or translate in the axial direction relative to one of the pair of raceways constituting the ball bearing, Equipped with, The pressurizing jig has multiple contact points arranged on the same virtual circle so as to be able to contact multiple locations in the circumferential direction of the end face on one axial side of the other raceway of the pair of raceway rings that is facing the pressurizing jig, The plurality of linear actuators apply pressure to the other raceway in the thrust direction via the pressurizing jig, causing the other raceway to tilt and / or axially translate and displace relative to the one raceway. Bearing pressurizing device. [Claim 2] The bearing pressurizing device according to claim 1, wherein one of the raceways is an inner ring and the other raceway is an outer ring. [Claim 3] A plurality of displacement sensors for measuring the inclination and / or axial displacement of the other raceway relative to the one raceway, The system includes a controller that provides feedback control of the plurality of linear actuators based on the output signals of the plurality of displacement sensors. The bearing pressurizing device according to claim 1. [Claim 4] The bearing pressurizing device according to claim 3, wherein the plurality of displacement sensors measure the inclination and / or axial displacement of the other raceway with respect to the other end face of the other raceway on the axial side of the other raceway. [Claim 5] The bearing pressurizing device according to claim 3, wherein the plurality of displacement sensors are supported so as to be able to adjust the radial position of the ball bearing. [Claim 6] The bearing pressurizing device according to claim 3, wherein the plurality of displacement sensors measure the inclination and / or axial displacement of the other raceway with respect to the portion of the other raceway in which the plurality of contact portions make contact and the portion of the other raceway in which the phase in the circumferential direction coincides. [Claim 7] The pressurizing jig has a substrate that is pressed by the linear motion part, The plurality of contact portions are fixed to the substrate so that their position relative to the radial direction of the ball bearing and / or their position relative to the circumferential direction of the ball bearing can be changed. The bearing pressurizing device according to claim 1. [Claim 8] The bearing pressurizing device according to claim 1, wherein the plurality of contact portions are arranged at equal intervals in the circumferential direction of the ball bearing. [Claim 9] The aforementioned plurality of linear actuators are composed of two linear actuators, The two linear actuators are positioned on opposite sides of the central axis of the ball bearing. The bearing pressurizing device according to claim 1. [Claim 10] A rotating shaft that rotates one of the pair of raceway rings that make up a ball bearing, A bearing pressurizing device that pressurizes the other of the pair of raceway rings in the thrust direction, A vibration sensor for measuring radial vibration of the other raceway, Equipped with, The bearing pressurizing device is the bearing pressurizing device described in any one of claims 1 to 9. Bearing vibration measurement device. [Claim 11] A method for measuring the vibration of a ball bearing using the bearing vibration measuring device described in claim 10, While rotating one of the raceways by the rotation shaft, the linear motion portion of each of the plurality of linear actuators pushes the pressure jig toward the other axial direction, causing the pressure jig to oscillate and / or translate axially relative to the one raceway, thereby applying thrust pressure to one axial end face of the other raceway by the plurality of contact portions, thereby tilting the other raceway with respect to the one raceway and / or changing its axial position, and measuring the radial vibration of the other raceway with the vibration sensor. Method for measuring vibration in ball bearings. [Claim 12] The method for measuring vibration of a ball bearing according to claim 11, further comprising the step of selecting one of the pressurizing jigs from among a plurality of pressurizing jigs, each having a different diameter for the virtual circle passing through the plurality of contact portions, such that the diameter of the virtual circle is suitable for the outer diameter of the other raceway ring of the ball bearing to be measured for vibration. [Claim 13] A method for manufacturing a ball bearing, A method for manufacturing a ball bearing, wherein the vibration measurement step of the ball bearing is performed by the vibration measurement method of the ball bearing described in claim 11. [Claim 14] A method for manufacturing a vehicle equipped with ball bearings, A method for manufacturing a vehicle, wherein the ball bearing is manufactured by the method for manufacturing a ball bearing described in claim 13. [Claim 15] A method for manufacturing a mechanical device equipped with ball bearings, A method for manufacturing a mechanical device, wherein the ball bearing is manufactured by the method for manufacturing a ball bearing described in claim 13.

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