JP2008180347A - Rolling bearing device having fixing structure by tapered member - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling bearing device which is suitable for preventing the erroneous detection of a resolver when a radial load has been applied on the rolling bearing device. <P>SOLUTION: A tapered groove 90a is formed on the fitting surface of a housing inner 22 to be fitted in an inner race 14a such that the inside diameter of the tapered groove increases axially toward a contact surface 76a. A tapered member 92a is inserted into the tapered groove 90a in a compressed state by mounting an inner race presser 26. Further, a tapered groove 90b is formed on the fitting surface of a rotor 12 to be fitted on an outer race 14b such that the inside diameter of the tapered groove 90b increases axially toward a contact surface 76b. A tapered member 92b is inserted into the tapered groove 90b in a compressed state by mounting an outer race presser 28. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a rolling bearing device including a rolling bearing and a resolver, and more particularly to a fixing structure using a tapered member suitable for preventing erroneous detection of a resolver when a radial load is applied to the rolling bearing device. The present invention relates to a rolling bearing device.

Conventionally, a rolling bearing device including a rolling bearing and a resolver is known as a rolling bearing device.
FIG. 5 is an axial sectional view of a conventional rolling bearing device.
As illustrated in FIG. 5, the rolling bearing device 200 rotatably supports the rotor 12 by being interposed between a housing inner 22 that is a stator, a rotor 12 that is a rotor, and the rotor 12 and the housing inner 22. And a cross roller bearing 14.

  The cross roller bearing 14 has an inner ring 14a and an outer ring 14b. The inner ring 14 a is fitted to the outer peripheral surface of the housing inner 22 and is fixed to the housing inner 22 in a state where it is pressed in the axial direction by the inner ring presser 26. The outer ring 14 b is fitted to the inner peripheral surface of the rotor 12 and is fixed to the rotor 12 while being pressed in the axial direction by the outer ring presser 28. Here, the fitting between the housing inner 22 and the inner ring 14 a and the fitting between the rotor 12 and the outer ring 14 b are set so as not to apply stress to the cross roller bearing 14.

A resolver 30 for detecting the rotation angle of the rotor 12 is provided between the rotor 12 and the housing inner 22.
The resolver 30 is disposed so as to be opposed to the resolver rotor 18 at a predetermined interval with an annular resolver rotor 18 having an inner periphery that is eccentric with respect to the axis of the cross roller bearing 14, and the reluctance between the resolver rotor 18 and the resolver rotor 18. And a position detector 20 for detecting a change. The resolver rotor 18 is integrally attached to the inner peripheral surface of the rotor 12, and the position detector 20 is integrally attached to the outer peripheral surface of the housing inner 22. By resolving the resolver rotor 18 eccentrically and changing the distance between the resolver rotor 18 and the position detector 20 in the circumferential direction, the reluctance changes according to the position of the resolver rotor 18. Therefore, since the fundamental wave component of the reluctance change per rotation of the rotor 12 is one cycle, the resolver 30 outputs a resolver signal that changes according to the rotation angle position of the rotor 12.

For example, a bearing device described in Patent Document 1 is known as a rolling bearing device that applies an axial preload to fix the inner ring 14a and the outer ring 14b.
JP 2005-69252 A

  However, in the conventional rolling bearing device 200, the inner ring 14a and the outer ring 14b are fixed by applying a preload in the axial direction, but the inner ring 14a and the outer ring 14b are fitted in the radial direction by fitting with a clearance. Since the structure is fixed, when a radial load is applied to the rolling bearing device 200, the distance between the housing inner 22 and the inner ring 14a is the gap, and the distance between the rotor 12 and the outer ring 14b is the gap. And the gap of the resolver 30 changes accordingly. Therefore, there has been a problem that the rotational angle position of the rotor 12 cannot be accurately detected.

Further, in this case, since the internal preload is applied to the cross roller bearing 14, shrink fitting cannot be performed.
Therefore, the present invention has been made paying attention to such an unsolved problem of the conventional technology, and prevents a misdetection of the resolver when a radial load is applied to the rolling bearing device. An object of the present invention is to provide a rolling bearing device having a fixing structure with a tapered member suitable for the above.

  [Invention 1] In order to achieve the above object, a rolling bearing device having a fixing structure with a tapered member according to Invention 1 is fitted to a rolling bearing having an inner ring and an outer ring, and an inner peripheral surface of the inner ring, and is attached to the inner ring. A supported inner ring supported body, an outer ring supported body fitted to the outer peripheral surface of the outer ring and supported by the outer ring, and a state where one end is brought into contact with the inner ring supported body and the inner ring is pressed in the axial direction. In a rolling bearing device comprising an inner ring presser fixed by a resolver and a resolver in which the reluctance between the inner ring supported body and the outer ring supported body changes depending on their relative positions, the inner circumference of the inner ring of the inner ring supported body A tapered groove formed of an elastic body that can be inserted into the tapered groove is formed in the fitting surface with the surface by forming a tapered groove whose inner diameter increases in the axial direction toward the contact surface of the inner ring supported body and the inner ring presser. The inner ring It was fitted to the tapered groove in a compressed state by attachment of e.

With such a configuration, the inner ring supported body and the outer ring supported body are relatively rotatably supported by the rolling bearing.
When a radial load is applied to the rolling bearing device, since the tapered member is inserted into the tapered groove in a compressed state, the distance between the inner ring supported body and the inner ring changes due to the elastic force of the tapered member. Is suppressed.

In addition, the taper groove has a shape in which the inner diameter increases in the axial direction toward the contact surface of the inner ring supported body and the inner ring presser, so that the inner ring can be accurately fixed by the tapered member by attaching the inner ring presser. it can.
Here, the inner ring supported body and the outer ring supported body only need to be relatively rotatably supported by the rolling bearing, and the inner ring supported body is fixed and the outer ring supported body is rotatably supported. Alternatively, the outer ring supported body may be fixed and the inner ring supported body may be rotatably supported, or both may be rotatably supported. Hereinafter, the same applies to the rolling bearing device having the fixing structure by the tapered member of the invention 4.
The tapered groove may be formed over the entire circumference of the inner ring supported body or may be formed in a part of the inner ring supported body.

[Invention 2] Furthermore, the rolling bearing device having a fixing structure with a tapered member according to Invention 2 is the rolling bearing device having a fixing structure with a tapered member according to Invention 1, wherein a plurality of the tapered grooves are formed in the circumferential direction. The tapered member is inserted into each tapered groove in a compressed state by attaching the inner ring presser.
With such a configuration, since the tapered member is inserted into each tapered groove formed in the circumferential direction in a compressed state, the elastic force of each tapered member causes a gap between the inner ring supported body and the inner ring. It is further suppressed that the distance is changed.

[Invention 3] Furthermore, the rolling bearing device having a fixing structure with a tapered member according to Invention 3 is the rolling bearing device having a fixing structure with a tapered member according to any one of Inventions 1 and 2, wherein the thickness of the tapered member is as follows. The length is smaller than the distance between the end portion of the maximum diameter of the tapered groove and the inner ring.
With such a configuration, since the thickness of the tapered member is smaller than the distance between the end of the maximum diameter of the tapered groove and the inner ring, the elastically deformed tapered member overflows from the gap between the tapered groove and the inner ring. Thus, it is possible to prevent the mounting accuracy of the inner ring presser from being lowered.

  [Invention 4] Further, a rolling bearing device having a fixing structure with a tapered member according to Invention 4 includes a rolling bearing having an inner ring and an outer ring, and an inner ring supported that is fitted to the inner peripheral surface of the inner ring and supported by the inner ring. A body, an outer ring supported body that is fitted to the outer peripheral surface of the outer ring and supported by the outer ring, and an outer ring presser that fixes one end of the outer ring supported body in an axial direction while contacting one end of the outer ring supported body. In a rolling bearing device comprising a resolver in which the reluctance between the inner ring supported body and the outer ring supported body changes depending on their relative positions, a fitting surface of the outer ring supported body with the outer peripheral surface of the outer ring is provided. A tapered groove having an inner diameter expanding in the axial direction toward a contact surface of the outer ring supported body and the outer ring presser, and a tapered member formed of an elastic body that can be inserted into the taper groove is provided on the outer ring presser. Pressure by mounting It was fitted to the tapered groove in the state.

With such a configuration, the inner ring supported body and the outer ring supported body are relatively rotatably supported by the rolling bearing.
When a radial load is applied to the rolling bearing device, since the tapered member is inserted into the tapered groove in a compressed state, the distance between the outer ring supported body and the outer ring changes due to the elastic force of the tapered member. Is suppressed.

In addition, since the taper groove has a shape in which the inner diameter increases in the axial direction toward the contact surface of the outer ring supported body and the outer ring presser, the outer ring can be accurately fixed by the tapered member by attaching the outer ring presser. it can.
Here, the taper groove may be formed over the entire circumference of the outer ring supported body, or may be formed in a part of the outer ring supported body.

[Invention 5] Furthermore, the rolling bearing device having a fixing structure with a tapered member according to Invention 5 is the rolling bearing device having a fixing structure with a tapered member according to Invention 4, wherein a plurality of the tapered grooves are formed in the circumferential direction. The tapered member is inserted into each tapered groove in a compressed state by attaching the outer ring presser.
With such a configuration, since the tapered member is inserted into each tapered groove formed in the circumferential direction in a compressed state, the elastic force of each tapered member causes a gap between the outer ring supported body and the outer ring. It is further suppressed that the distance is changed.

[Invention 6] Further, the rolling bearing device having a fixing structure with a tapered member according to Invention 6 is the rolling bearing device having the fixing structure with a tapered member according to any one of Inventions 4 and 5, wherein the thickness of the tapered member is as follows. The length is smaller than the distance between the end of the maximum diameter of the tapered groove and the outer ring.
With such a configuration, since the thickness of the tapered member is smaller than the distance between the end of the maximum diameter of the tapered groove and the outer ring, the elastically deformed tapered member overflows from the gap between the tapered groove and the outer ring. Thus, it is possible to prevent the mounting accuracy of the outer ring presser from being lowered.

  [Invention 7] Furthermore, the rolling bearing device having a fixing structure with a tapered member according to Invention 7 is the rolling bearing device having the fixing structure with a tapered member according to any one of Inventions 1 to 6, wherein the resolver has an inner circumference. And an annular detection object in which one of the outer circumferences is decentered with respect to the axis of the rolling bearing, and detection means for detecting a change in reluctance between the detection object and the detection object. The detected body is provided on one of the inner ring supported body and the outer ring supported body, and the detecting means is provided on the other side so that the eccentric side of the inner circumference and the outer circumference faces the detecting means.

With such a configuration, when the inner ring supported body and the outer ring supported body are relatively rotated, the detection means and the detected body are also relatively rotated. And since the side which opposes a detection means is eccentric among the inner periphery and outer periphery of a to-be-detected body, a reluctance change arises by rotation and the reluctance change is detected by a detection means.
As described above, in the type of resolver in which the fundamental wave component of the reluctance change per rotation is one cycle, the influence of the gap change due to the load is large. Therefore, the suppression of the gap change is effective in preventing erroneous detection.

  Here, regarding the detected body and the detecting means, the detected body may be provided on the inner ring supported body, and the detecting means may be provided on the outer ring supported body, or vice versa. In the former case, the detected object and the detecting means are provided by decentering the outer periphery of the detected object and causing the outer periphery of the detected object to face the detecting means. In the latter case, the detected object and the detecting means are provided by decentering the inner periphery of the detected object and making the inner periphery of the detected object face the detecting means.

  [Invention 8] Further, the rolling bearing device having a fixing structure with the tapered member according to Invention 8 is the rolling bearing device having the fixing structure with the tapered member according to any one of Inventions 1 and 4, wherein the inner ring presser is used as the inner ring. The inner ring retainer and the inner ring supported body are made of a material having a higher thermal expansion coefficient than the supported body, and the inner ring supported body and the inner ring supported body are axially arranged so that the inner ring supported body is fitted to the inner ring retainer from the radially outer side. A spigot portion was formed at the end of the spigot and fitted with a spigot.

With such a configuration, when the temperature rises, the inner ring presser tends to expand more than the inner ring supported body, but is suppressed by the inner ring supported body because the inner ring supported body is disposed radially outward. . Therefore, it is possible to prevent a radial gap between the inner ring supported body and the inner ring presser.
Here, the inlay portion is an uneven step portion for fitting the inner ring retainer and the inner ring supported body into the inlay, and a concave step portion is provided on one of the inner ring retainer and the inner ring supported body, and a convex step portion is provided on the other. Just do it. The inlay portion may be provided on the inner peripheral surface side of the inner ring presser and the inner ring supported body, or may be provided on the outer peripheral surface side.

[Invention 9] Furthermore, the rolling bearing device having a fixing structure with a tapered member according to Invention 9 is the rolling bearing device having a fixing structure with a tapered member according to Invention 8, wherein the inner ring presser and the inner ring supported body are In the state where the inner ring presser is in contact with the inner ring, there is an axial gap between the convex step portion and the concave step portion constituting the spigot portion, and there is an axial gap between the inner ring presser and the inner ring supported body. The gap is set so as to be formed within the operating temperature range.
With such a configuration, even if the inner ring presser and the inner ring supported body expand in the axial direction within the operating temperature range, the convex stepped portion and the concave stepped portion, and the inner ring presser and the inner ring supported body may contact each other. Therefore, the inner ring presser and the inner ring supported body can always be kept in a state where the inner ring presser fixes the inner ring with respect to the axial fitting of the inner ring presser and the inner ring supported body.

[Invention 10] Furthermore, the rolling bearing device having a fixing structure with a tapered member according to Invention 10 is the rolling bearing device having a fixing structure with a tapered member according to any one of Inventions 8 and 9, wherein the inner ring presser includes: The clearance is set so that a radial clearance is formed within the operating temperature range between the inner ring and the inner ring presser.
With such a configuration, even if the inner ring presser and the inner ring supported body expand within the operating temperature range, the inner ring and the inner ring presser do not come into contact with each other. With respect to the fitting, it is always possible to maintain the state where the inner ring supported body fixes the inner ring.

[Invention 11] Furthermore, the rolling bearing device having a fixing structure with a tapered member according to Invention 11 is the rolling bearing device having a fixing structure with a tapered member according to any one of Inventions 1 and 4, wherein the outer ring presser is used as the outer ring. The outer ring presser and the outer ring supported body are made of a material having a higher coefficient of thermal expansion than the supported body, and the outer ring supported body and the outer ring supported body are axially arranged so that the outer ring supported body fits the outer ring presser from the radially outer side. A spigot portion was formed at the end of the spigot and fitted with a spigot.
With such a configuration, when the temperature rises, the outer ring presser tends to expand more than the outer ring supported body, but is suppressed by the outer ring supported body because the outer ring supported body is disposed radially outside. . Therefore, it is possible to prevent the occurrence of a radial gap between the outer ring supported body and the outer ring presser.

  Here, the inlay portion is an uneven step portion for fitting the outer ring retainer and the outer ring supported body into the inlay, and a concave step portion is provided on one of the outer ring retainer and the outer ring supported body, and a convex step portion is provided on the other. Just do it. Further, the inlay portion may be provided on the inner peripheral surface side of the outer ring presser and the outer ring supported body, or may be provided on the outer peripheral surface side.

[Invention 12] Furthermore, the rolling bearing device having a fixing structure with a tapered member according to Invention 12 is the rolling bearing device having a fixing structure with a tapered member according to Invention 11, in which the outer ring presser and the outer ring supported body are In a state where the outer ring presser contacts the outer ring, an axial gap is formed between the convex step portion and the concave step portion constituting the spigot portion, and an axial gap is provided between the outer ring presser and the outer ring supported body. The gap is set so as to be formed within the operating temperature range.
With such a configuration, even if the outer ring presser and the outer ring supported body expand in the axial direction within the operating temperature range, the convex stepped portion and the concave stepped portion, and the outer ring presser and the outer ring supported body may contact each other. Therefore, the outer ring retainer and the outer ring supported body can be always kept in a state where the outer ring retainer fixes the outer ring with respect to the axial fitting of the outer ring retainer.

  [Invention 13] Furthermore, the rolling bearing device having a fixing structure with a tapered member according to Invention 13 is the rolling bearing device having a fixing structure with a tapered member according to any one of Inventions 11 and 12, wherein the outer ring presser includes The clearance is set so that a radial clearance is formed within the operating temperature range between the outer ring and the outer ring presser.

  With such a configuration, even if the outer ring presser and the outer ring supported body expand within the operating temperature range, the outer ring and the outer ring presser do not come into contact with each other. As for the fitting, the outer ring supported body can always maintain the state of fixing the outer ring.

  As described above, according to the rolling bearing device having the fixing structure with the tapered member of the first aspect, even when a radial load is applied to the rolling bearing device, the inner ring supported body and the inner ring are compared with the conventional one. Since the change in the distance between them is suppressed, the change in the gap of the resolver due to the load is suppressed, and the possibility that the possibility of erroneous detection by the resolver can be reduced is obtained. Further, since the inner ring supported body and the inner ring can be disassembled, an effect that the maintainability can be improved is also obtained.

Furthermore, according to the rolling bearing device having the fixed structure by the tapered member of the invention 2, since the distance between the inner ring supported body and the inner ring is further suppressed, the possibility of erroneous detection by the resolver is further increased. The effect that it can reduce is acquired.
Furthermore, according to the rolling bearing device having the fixing structure with the tapered member of the invention 3, it is possible to prevent the taper member that has been elastically deformed from overflowing from the gap between the tapered groove and the inner ring, thereby reducing the mounting accuracy of the inner ring presser. The effect that it can be obtained.

  Furthermore, according to the rolling bearing device having the fixing structure by the tapered member of the invention 4, even if a radial load is applied to the rolling bearing device, the distance between the outer ring supported body and the outer ring is larger than that in the conventional case. Since the change is suppressed, the change in the gap of the resolver due to the load is suppressed, and an effect that the possibility of the false detection by the resolver can be reduced is obtained. In addition, since the outer ring supported body and the outer ring can be disassembled, an effect that the maintainability can be improved is also obtained.

Furthermore, according to the rolling bearing device having the fixed structure with the tapered member of the fifth aspect, the distance between the outer ring supported body and the outer ring is further suppressed, and therefore the possibility that the resolver misdetects further. The effect that it can reduce is acquired.
Furthermore, according to the rolling bearing device having the fixing structure with the tapered member of the invention 6, it is possible to prevent the taper member that has been elastically deformed from overflowing from the gap between the tapered groove and the outer ring, thereby reducing the mounting accuracy of the outer ring presser. The effect that it can be obtained.

Furthermore, according to the rolling bearing device having the fixing structure by the tapered member of the eighth aspect, it is possible to prevent a radial gap from being generated between the inner ring supported body and the inner ring presser even when the temperature rises. The effect is obtained.
Furthermore, according to the rolling bearing device having the fixing structure by the tapered member of the ninth aspect, the inner ring presser and the inner ring supported body always maintain the state in which the inner ring presser fixes the inner ring with respect to the axial fitting of the inner ring presser and the inner ring supported body. The effect of being able to be obtained.

Furthermore, according to the rolling bearing device having the fixing structure with the tapered member of the invention 10, the inner ring supported body always fixes the inner ring with respect to the inner ring, the inner ring presser and the inner ring supported body in the radial direction. Can be maintained.
Furthermore, according to the rolling bearing device having the fixing structure with the tapered member of the eleventh aspect, it is possible to prevent a radial gap from being generated between the outer ring supported body and the outer ring presser even when the temperature rises. The effect is obtained.

Furthermore, according to the rolling bearing device having the fixing structure with the tapered member according to the twelfth aspect, the outer ring presser and the outer ring supported body always maintain the state in which the outer ring presser fixes the outer ring with respect to the axial fitting of the outer ring presser and the outer ring supported body. The effect of being able to be obtained.
Further, according to the rolling bearing device having the fixing structure by the tapered member of the thirteenth aspect, the outer ring supported body always fixes the outer ring with respect to the outer ring, the outer ring presser and the outer ring supported body fitting in the radial direction. The effect that can be maintained is obtained.

[First Embodiment]
Hereinafter, a first embodiment of the present invention will be described with reference to the drawings. FIG. 1 and FIG. 2 are views showing a first embodiment of a rolling bearing device having a fixing structure with a tapered member according to the present invention.
First, the configuration of a direct drive motor to which the present invention is applied will be described.

FIG. 1 is a sectional view of the direct drive motor 100 in the axial direction.
As shown in FIG. 1, the direct drive motor 100 supports a rotor 12 rotatably by being interposed between a housing inner 22 that is a stator, a rotor 12 that is a rotor, and the rotor 12 and the housing inner 22. And a cross roller bearing 14.
Between the rotor 12 and the housing inner 22, a coil 16 that applies rotational torque to the rotor 12 and a resolver 30 for detecting the rotational angle of the rotor 12 are provided.

  The resolver 30 is disposed so as to be opposed to the resolver rotor 18 at a predetermined interval with an annular resolver rotor 18 having an inner periphery that is eccentric with respect to the axis of the cross roller bearing 14, and the reluctance between the resolver rotor 18 and the resolver rotor 18. And a position detector 20 for detecting a change. The resolver rotor 18 is integrally attached to the inner peripheral surface of the rotor 12 by bolts 18a, and the position detector 20 is integrally attached to the outer peripheral surface of the housing inner 22 by bolts 20a. By resolving the resolver rotor 18 eccentrically and changing the distance between the resolver rotor 18 and the position detector 20 in the circumferential direction, the reluctance changes according to the position of the resolver rotor 18. Therefore, since the fundamental wave component of the reluctance change per rotation of the rotor 12 is one cycle, the resolver 30 outputs a resolver signal that changes according to the rotation angle position of the rotor 12.

When the coil 16 is energized, the rotor 12 and the resolver rotor 18 rotate together, the position detector 20 detects a change in reactance, and the controller (not shown) controls the rotational speed and positioning. It has become.
In the present embodiment, the outer rotor type in which the outer side of the motor rotates is described, but there is no problem even if it is adopted in the inner rotor type in which the inner side of the motor rotates. Since the direct drive motor 100 has the same well-known configuration as the conventional direct drive motor except for the bearing components, the bearing configuration which is a characteristic part of the present invention will be described below. The configuration excluding the bearing component of the direct drive motor 100 is not particularly limited to the illustrated example, and other well-known configurations can be appropriately modified within the scope of the present invention.

The cross roller bearing 14 includes an inner ring 14a, an outer ring 14b, and a plurality of cross rollers (rollers) 14c provided so as to be able to roll between the inner ring 14a and the outer ring 14b. The cross roller 14c has a substantially cylindrical shape whose diameter is slightly larger than the length, and the even-numbered rotation shaft on the track and the odd-numbered rotation shaft on the track are inclined by 90 °.
A flange 22a projecting radially outward is formed on the outer peripheral surface of the housing inner 22, and the inner ring 14a is fitted to the outer peripheral surface of the housing inner 22 with the lower surface of the inner ring 14a contacting the flange 22a. Then, the inner ring retainer 26 is brought into contact with the upper surface of the inner ring 14a, and the inner ring retainer 26 is fastened to the housing inner 22 with a bolt 26a. It is fixed to the housing inner 22.

  On the other hand, a flange 12a protruding radially inward is formed on the inner peripheral surface of the rotor 12, and the outer ring 14b is fitted to the inner peripheral surface of the rotor 12 with the lower surface of the outer ring 14b contacting the flange 12a. Then, the outer ring retainer 28 is brought into contact with the upper surface of the outer ring 14 b and the outer ring retainer 28 is fastened to the rotor 12 with a bolt 28 a, so that the outer ring 14 b is pressed against the rotor 12 in the axial direction. Fixed to.

The fitting between the housing inner 22 and the inner ring 14 a and the fitting between the rotor 12 and the outer ring 14 b are set so as not to apply stress to the cross roller bearing 14.
FIG. 2 is a perspective view of the tapered groove 90a and the tapered member 92a.
As shown in FIG. 2A, a taper whose inner diameter expands in the axial direction toward the contact surface 76a of the housing inner 22 and the inner ring retainer 26 is formed on the fitting surface of the housing inner 22 with the inner peripheral surface of the inner ring 14a. A groove 90a is formed. A plurality of tapered grooves 90a are formed in the circumferential direction. As shown in FIG. 2B, a tapered member 92a made of an elastic body having a shape that can be inserted into the tapered groove 90a is inserted into each tapered groove 90a in a compressed state. The tapered member 92a is inserted into the tapered groove 90a in a compressed state by attaching the inner ring presser 26 from above. At this time, since the inner diameter of the tapered groove 90a is enlarged toward the contact surface 76a in the axial direction, the inner ring 14a can be accurately fixed by the tapered member 92a by attaching the inner ring retainer 26. Further, the thickness of the tapered member 92a is smaller than the distance between the end portion of the tapered groove 90a having the maximum diameter and the inner ring 14a. Therefore, it is possible to prevent the taper-shaped member 92a that has been elastically deformed from overflowing from the gap between the taper groove 90a and the inner ring 14a and the mounting accuracy of the inner ring presser 26 from being lowered.

  On the other hand, a taper groove 90b whose inner diameter increases in the axial direction toward the contact surface 76b of the rotor 12 and the outer ring retainer 28 is formed on the fitting surface of the rotor 12 with the outer peripheral surface of the outer ring 14b. A plurality of tapered grooves 90b are formed in the circumferential direction. A tapered member 92b made of an elastic body having a shape that can be inserted into the tapered groove 90b is inserted into each tapered groove 90b in a compressed state. The tapered member 92b is inserted into the tapered groove 90b in a compressed state by attaching the outer ring presser 28 from above. At this time, since the taper groove 90b has a shape in which the inner diameter increases in the axial direction toward the contact surface 76b, the outer ring 14b can be accurately fixed by the tapered member 92b by attaching the outer ring retainer 28. Further, the thickness of the tapered member 92b is smaller than the distance between the end portion of the maximum diameter of the tapered groove 90b and the outer ring 14b. Therefore, it is possible to prevent the taper-shaped member 92b that has been elastically deformed from overflowing from the gap between the taper groove 90b and the outer ring 14b, and the mounting accuracy of the outer ring presser 28 from being lowered.

The tapered members 92a and 92b only need to be made of a material that deforms with a weaker force than a metal and follows the mating member. For example, the tapered members 92a and 92b can be made of plastic or high hardness rubber. Moreover, in order to improve adhesiveness, as shown in FIG.2 (b), it becomes a shape which can be inserted only in the upper half of taper groove 90a, 90b, and does not have a part equivalent to a lower half.
Next, the operation of the present embodiment will be described.

When the coil 16 is energized, rotational torque is applied to the rotor 12 and the rotor 12 rotates. A change in reluctance between the position detector 20 and the resolver rotor 18 that rotates integrally with the rotor 12 is detected, and a controller (not shown) controls rotation speed and positioning.
When a radial load is applied to the direct drive motor 100, since the tapered members 92a and 92b are inserted into the tapered grooves 90a and 90b formed in the circumferential direction in a compressed state, the tapered members 92a and 92b are inserted. Due to the elastic force, the distance between the housing inner 22 and the inner ring 14a and the distance between the rotor 12 and the outer ring 14b are suppressed from changing. As a result, the gap change of the resolver 30 is suppressed.

  Thus, in the present embodiment, the cross roller bearing 14 having the inner ring 14a and the outer ring 14b, the housing inner 22 fitted to the inner peripheral surface of the inner ring 14a and supported by the inner ring 14a, and the outer peripheral surface of the outer ring 14b. The inner ring retainer 26 which is fixed to the rotor 12 which is fitted to the outer ring 14b and supported by the outer ring 14b, the inner ring 14a being pressed in the axial direction, and the reluctance between the housing inner 22 and the rotor 12. And a resolver 30 that varies depending on the position of the rotor 12, and a tapered groove 90a having an inner diameter that increases in the axial direction toward the contact surface 76a is formed on the fitting surface with the inner peripheral surface of the inner ring 14a of the housing inner 22. The tapered member 92a was inserted into the tapered groove 90a in a compressed state by attaching the inner ring retainer 26.

  As a result, even if a radial load is applied to the direct drive motor 100, the distance between the housing inner 22 and the inner ring 14a is suppressed from changing as compared with the conventional case, so that the gap change of the resolver 30 due to the load is suppressed. Is suppressed, and the possibility that the resolver 30 erroneously detects can be reduced. Moreover, since the housing inner 22 and the inner ring 14a can be disassembled, the maintainability can be improved.

Further, in the present embodiment, a plurality of tapered grooves 90a are formed in the circumferential direction, and the tapered member 92a is inserted into each tapered groove 90a in a compressed state by attaching the inner ring retainer 26.
Thereby, since the change between the distance between the housing inner 22 and the inner ring 14a is further suppressed, the possibility that the resolver 30 erroneously detects can be further reduced.
Further, in the present embodiment, the thickness of the tapered member 92a is smaller than the distance between the end portion of the tapered groove 90a having the maximum diameter and the inner ring 14a.

Accordingly, it is possible to prevent the taper-shaped member 92a that has been elastically deformed from overflowing from the gap between the taper groove 90a and the inner ring 14a, and the mounting accuracy of the inner ring presser 26 from being lowered.
Further, in the present embodiment, the rotor 12 is provided with an outer ring presser 28 that is in contact with one end and fixed in a state where the outer ring 14b is pressed in the axial direction, and is in contact with the fitting surface of the outer ring 14b of the rotor 12 with the outer peripheral surface. A tapered groove 90b whose inner diameter is increased in the axial direction toward the surface 76b is formed, and the tapered member 92b is fitted into the tapered groove 90b in a compressed state by attaching the outer ring retainer 28.

  As a result, even if a radial load is applied to the direct drive motor 100, a change in the distance between the rotor 12 and the outer ring 14b is suppressed, so that a change in the gap of the resolver 30 due to the load is suppressed. The possibility of erroneous detection can be further reduced. Further, since the rotor 12 and the outer ring 14b can be disassembled, the maintainability can be improved.

Furthermore, in the present embodiment, a plurality of tapered grooves 90b are formed in the circumferential direction, and the tapered member 92b is fitted and inserted into each tapered groove 90b in a compressed state by attaching the outer ring retainer 28.
Thereby, since the change between the rotor 12 and the outer ring 14b is further suppressed, the possibility that the resolver 30 erroneously detects can be further reduced.
Further, in the present embodiment, the thickness of the tapered member 92b is smaller than the distance between the end portion of the tapered groove 90b having the maximum diameter and the outer ring 14b.

Thereby, it is possible to prevent the taper-shaped member 92b that has been elastically deformed from overflowing from the gap between the taper groove 90b and the outer ring 14b and the mounting accuracy of the outer ring presser 28 from being lowered.
Furthermore, in the present embodiment, the resolver 30 is disposed to face the annular resolver rotor 18 having an inner periphery that is eccentric with respect to the axis of the cross roller bearing 14, and the resolver rotor 18 at a predetermined interval. And a position detector 20 that detects a change in reluctance with the resolver rotor 18.

Thus, in the resolver 30 of the type in which the fundamental wave component of the reluctance change per rotation is one cycle, the influence of the gap change due to the load is large, and thus the suppression of the gap change is effective in preventing erroneous detection.
In the first embodiment, the cross roller bearing 14 corresponds to the rolling bearing of the invention 1 to 7, the housing inner 22 corresponds to the inner ring supported body of the invention 1, 4 or 7, and the rotor 12 Corresponding to the outer ring supported body of the invention 1, 4 or 7, the resolver rotor 18 corresponds to the detected body of the invention 7. The position detector 20 corresponds to the detection means of the seventh aspect.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to the drawings. 3 and 4 are diagrams showing a second embodiment of a rolling bearing device having a fixing structure with a tapered member according to the present invention.
In the present embodiment, the inner ring retainer 26 and the housing inner 22, and the outer ring retainer 28 and the rotor 12 are made of materials having different coefficients of thermal expansion, and they are inlay-fitted to the first embodiment. The point is different.
First, the configuration of a direct drive motor to which the present invention is applied will be described.
FIG. 3 is a partial cross-sectional view of the direct drive motor 100 in the axial direction.

  The rotor 12 and the housing inner 22 are made of a material (for example, iron) having a lower coefficient of thermal expansion than the inner ring retainer 26 and the outer ring retainer 28. On the other hand, the inner ring retainer 26 and the outer ring retainer 28 are made of a material (for example, aluminum) having a higher coefficient of thermal expansion than the rotor 12 and the housing inner 22. When there is a difference in the coefficient of thermal expansion in this way, the amount of thermal expansion of the rotor 12 and the housing inner 22 is smaller than the amount of thermal expansion of the inner ring retainer 26 and the outer ring retainer 28. Therefore, in the present embodiment, when the temperature rises, a difference in the amount of thermal expansion is used to prevent a radial gap from occurring in the spigot fitting portion.

On the inner peripheral surface side of the lower surface of the inner ring retainer 26, as shown in FIG. 3, a convex step 34 a for engaging with the housing inner 22 is formed protruding in the axial direction. On the peripheral surface side, a recessed step portion 34b for fitting with the inner ring presser 26 with an inlay is formed.
Then, the inner ring retainer 26 is brought into contact with the upper surface of the inner ring 14a, and the inner ring retainer 26 is fastened to the housing inner 22 with a bolt 26a. While being fixed to the housing inner 22, the inner ring presser 26 and the housing inner 22 are inlay-fitted in the axial direction at the convex step 34a and the concave step 34b.

  In the inlay fitting portion (the portion where the convex step portion 34a and the concave step portion 34b are fitted), the housing inner 22 having a low coefficient of thermal expansion is arranged to fit the inner ring presser 26 having a high coefficient of thermal expansion from the outside in the radial direction. ing. Therefore, when the temperature rises, the inner ring presser 26 tends to expand more than the housing inner 22, but is restrained by the housing inner 22 because the housing inner 22 is disposed radially outward. Accordingly, it is possible to prevent a radial gap from being generated between the housing inner 22 and the inner ring presser 26.

FIG. 4 is a diagram illustrating a case where the arrangement at the spigot fitting portion is reversed.
As shown in FIG. 4A, when an arrangement opposite to that shown in FIG. 3 in which the inner ring retainer 26 is disposed radially outward at the inner joint of the housing inner 22 and the inner ring retainer 26 is employed, the temperature is When it rises, the inner ring retainer 26 expands more than the housing inner 22, thereby creating a radial gap between the housing inner 22 and the inner ring retainer 26 as shown in FIG. 4 (b).

Further, as shown in FIG. 3, the inner ring retainer 26 and the housing inner 22 are provided with a protruding step portion 34a in a state where the pressing portion 26b of the inner ring retainer 26 is fixed in contact with the upper surface of the inner ring 14a by fastening the bolt 26a. A gap h ₁ in the axial direction is formed between the lower surface of the concave step 34b and the upper surface of the recessed step portion 34b, and an axial gap h ₂ is formed between the lower surface of the inner ring retainer 26 and the upper surface of the housing inner 22 within the operating temperature range. The gap is set to. As a result, even if the inner ring presser 26 and the housing inner 22 expand in the axial direction within the operating temperature range, the lower surface of the convex step 34a and the upper surface of the concave step 34b, and the lower surface of the inner ring presser 26 and the upper surface of the housing inner 22 Therefore, the inner ring presser 26 and the housing inner 22 can always be kept in a state where the inner ring presser 26 fixes the inner ring 14a. That is, the axial fitting is performed based on the position where the pressing portion 26b of the inner ring presser 26 and the upper surface of the inner ring 14a are in contact with each other regardless of the temperature change.

Further, the inner ring presser 26 is set so that a radial gap w ₁ is formed within the operating temperature range between the side surface of the inner ring 14 a and the side surface of the inner ring presser 26. As a result, even if the inner ring retainer 26 and the housing inner 22 expand within the operating temperature range, the side surface of the inner ring 14a and the side surface of the inner ring retainer 26 do not contact each other, so the inner ring 14a, the inner ring retainer 26, and the housing inner 22 About the fitting of radial direction, the state which the housing inner 22 fixes the inner ring | wheel 14a can always be maintained. That is, the radial fitting is performed based on the position where the housing inner 22 and the inner ring 14a are in contact with each other regardless of the temperature change.

On the other hand, on the inner peripheral surface side of the lower surface of the outer ring retainer 28, a convex step portion 36a for fitting with the rotor 12 in an inlay is projected in the axial direction, and on the inner peripheral surface side of the upper surface of the rotor 12, the outer ring A recessed step portion 36b for fitting the presser 28 with the inlay is formed.
Then, the outer ring retainer 28 is brought into contact with the upper surface of the outer ring 14 b and the outer ring retainer 28 is fastened to the rotor 12 with a bolt 28 a, so that the outer ring 14 b is pressed against the rotor 12 in the axial direction. The outer ring presser 28 and the rotor 12 are inlay-fitted in the axial direction at the convex step portion 36a and the concave step portion 36b.

  In the inlay fitting portion (the portion where the convex step portion 36a and the concave step portion 36b are fitted), the rotor 12 having a low coefficient of thermal expansion is arranged to fit the outer ring presser 28 having a high coefficient of thermal expansion from the outside in the radial direction. Yes. For this reason, when the temperature rises, the outer ring presser 28 tends to expand more than the rotor 12, but is suppressed by the rotor 12 because the rotor 12 is disposed radially outward. Accordingly, it is possible to prevent a radial gap from being generated between the rotor 12 and the outer ring presser 28.

As shown in FIG. 4 (a), when the arrangement opposite to that in FIG. 3 in which the outer ring retainer 28 is disposed radially outward is adopted in the inlay fitting portion between the rotor 12 and the outer ring retainer 28, the temperature rises. As a result, the outer ring retainer 28 expands more than the rotor 12, thereby creating a radial gap between the rotor 12 and the outer ring retainer 28 as shown in FIG.
Further, as shown in FIG. 3, the outer ring retainer 28 and the rotor 12 are arranged so that the protruding portion 36 a is in a state where the pressing portion 28 b of the outer ring retainer 28 is in contact with and fixed to the upper surface of the outer ring 14 b by fastening the bolt 28 a. A gap h ₃ in the axial direction is formed between the lower surface and the upper surface of the recessed step portion 36b, and a gap is formed so that an axial gap h ₄ is formed between the lower surface of the outer ring retainer 28 and the upper surface of the rotor 12 within the operating temperature range. Is set. Thereby, even if the outer ring presser 28 and the rotor 12 expand in the axial direction within the operating temperature range, the lower surface of the convex step portion 36a and the upper surface of the concave step portion 36b, and the lower surface of the outer ring presser 28 and the upper surface of the rotor 12 contact each other. Therefore, the outer ring presser 28 and the rotor 12 can always be kept in a state in which the outer ring presser 28 fixes the outer ring 14b with respect to the axial engagement of the outer ring presser 28 and the rotor 12. That is, the fitting in the axial direction is performed based on the position where the pressing portion 28b of the outer ring presser 28 and the upper surface of the outer ring 14b are in contact with each other regardless of the temperature change.

Further, the outer ring retainer 28 is set so that a radial gap w ₂ is formed within the operating temperature range between the side surface of the outer ring retainer 14 b and the side surface of the outer ring retainer 28. Thereby, even if the outer ring presser 28 and the rotor 12 expand within the operating temperature range, the side surface of the outer ring 14b and the side surface of the outer ring presser 28 do not come into contact with each other. As for the fitting, the state in which the rotor 12 fixes the outer ring 14b can always be maintained. That is, the radial fitting is performed based on the position where the rotor 12 and the outer ring 14b are in contact with each other regardless of the temperature change.

Thus, in the present embodiment, the inner ring retainer 26 is made of a material having a higher thermal expansion coefficient than the housing inner 22, and the inner ring retainer 26 is fitted so that the housing inner 22 fits the inner ring retainer 26 from the radially outer side. And the housing inner 22 was inlay-fitted in the axial direction.
Thereby, even if the temperature rises, it is possible to prevent a radial gap from being generated between the housing inner 22 and the inner ring presser 26.

Further, in the present embodiment, the inner ring retainer 26 and the housing inner 22 are arranged between the lower surface of the convex step portion 34a and the upper surface of the concave step portion 34b in a state where the pressing portion 26b of the inner ring retainer 26 is in contact with the upper surface of the inner ring 14a. Further, the axial gap h ₁ is set so that the axial gap h ₂ is formed within the operating temperature range between the lower surface of the inner ring presser 26 and the upper surface of the housing inner 22.

Thereby, about the axial fitting of the inner ring retainer 26 and the housing inner 22, the state which the inner ring retainer 26 fixes the inner ring 14a can always be maintained.
Furthermore, in the present embodiment, the inner ring presser 26 is set so that a radial gap w ₁ is formed within the operating temperature range between the side surface of the inner ring 14 a and the side surface of the inner ring presser 26.
Thereby, about the radial fitting of the inner ring 14a, the inner ring retainer 26, and the housing inner 22, the state in which the housing inner 22 fixes the inner ring 14a can always be maintained.

Further, in the present embodiment, the outer ring retainer 28 is made of a material having a higher thermal expansion coefficient than the rotor 12, and the outer ring retainer 28 and the rotor 12 are pivoted so that the rotor 12 fits the outer ring retainer 28 from the radially outer side. Inlay fitted in the direction.
Thereby, even if the temperature rises, it is possible to prevent a radial gap from being generated between the rotor 12 and the outer ring presser 28.

Further, in the present embodiment, the outer ring retainer 28 and the rotor 12 are disposed between the lower surface of the convex step portion 36a and the upper surface of the concave step portion 36b in a state where the pressing portion 28b of the outer ring retainer 28 is in contact with the upper surface of the outer ring 14b. The gap h ₃ in the axial direction is set so that the gap h ₄ in the axial direction is formed within the operating temperature range between the lower surface of the outer ring retainer 28 and the upper surface of the rotor 12.
As a result, the outer ring presser 28 and the rotor 12 can always be kept in a state where the outer ring presser 28 fixes the outer ring 14b in the axial direction.

Further, in the present embodiment, the outer ring presser 28 is set so that a radial gap w ₂ is formed within the operating temperature range between the side surface of the outer ring 14 b and the side surface of the outer ring presser 28.
Thereby, about the fitting of the outer ring 14b, the outer ring retainer 28, and the rotor 12 in the radial direction, the state where the rotor 12 fixes the outer ring 14b can always be maintained.
In the second embodiment, the housing inner 22 corresponds to the inner ring supported body of the invention 8 or 9, and the rotor 12 corresponds to the outer ring supported body of the invention 11 or 12.

  In the first and second embodiments, the tapered member 92a is fitted on the inner ring 14a side and the tapered member 92b is fitted on the outer ring 14b side. A tapered member may be inserted and configured only on one side on the outer ring 14b side. In this case, the tapered groove 90a or the tapered groove 90b may be formed only on the side where the tapered member is inserted.

In the first and second embodiments, the plurality of tapered grooves 90a are formed in the circumferential direction. However, the present invention is not limited to this, and only one tapered groove 90a is formed in the circumferential direction. It can also be configured.
In the first and second embodiments, the plurality of tapered grooves 90b are formed in the circumferential direction. However, the present invention is not limited to this, and only one tapered groove 90b is formed in the circumferential direction. It can also be configured.

In the first and second embodiments, the cross roller bearing 14 is applied. However, the present invention is not limited to this, and an angular ball bearing, a deep groove ball bearing, a cylindrical roller bearing, a tapered roller bearing, or the like is applied. May be.
In the first and second embodiments, the rolling bearing device having the fixed structure by the tapered member according to the present invention is applied to the structure that rotatably supports the housing inner 22 and the rotor 12. The present invention is not limited to this, and any structure can be applied as long as it is interposed between two members and supports them relatively rotatably.

FIG. 3 is a cross-sectional view of the direct drive motor 100 in the axial direction. It is a perspective view of the taper groove | channel 90a and the taper-shaped member 92a. FIG. 2 is a partial cross-sectional view of the direct drive motor 100 in the axial direction. It is a figure which shows the case where arrangement | positioning in an inlay fitting part is reversed. It is sectional drawing of the axial direction of the conventional rolling bearing apparatus.

Explanation of symbols

100 direct drive motor 12 rotor 14 cross roller bearing 14a inner race 14b outer race 14c cross roller 16 coil 18 resolver rotor 20 position detector 22 housing inner 26 inner retainer 28 outer ring retainer 34a, 36a convex stepped portion 34b, 36b recessed step h ₁ ~ h ₄ , w ₁ , w ₂ , 32a, 32b Clearance 76a, 76b Contact surface 90a, 90b Taper groove 92a, 92b Tapered member 12a, 22a Flange 26b, 28b Press part 18a, 20a, 26a, 28a Bolt

Claims (13)

A rolling bearing having an inner ring and an outer ring, an inner ring supported body fitted to the inner circumferential surface of the inner ring and supported by the inner ring, and an outer ring supported body fitted to the outer circumferential surface of the outer ring and supported by the outer ring And an inner ring presser that is fixed in a state where one end is brought into contact with the inner ring supported body and the inner ring is pressed in an axial direction, and reluctance between the inner ring supported body and the outer ring supported body is determined by their relative positions. In a rolling bearing device comprising a changing resolver,
A taper groove whose inner diameter is increased in the axial direction toward the contact surface of the inner ring supported body and the inner ring presser is formed on a fitting surface of the inner ring supported body with the inner peripheral surface of the inner ring, and the tapered groove A rolling bearing device having a fixed structure with a taper member, wherein a taper member made of an elastic body that can be inserted into the taper is inserted into the taper groove in a compressed state by attaching the inner ring presser. In claim 1,
A rolling bearing having a fixed structure with a tapered member, wherein a plurality of the tapered grooves are formed in a circumferential direction, and the tapered member is inserted into each tapered groove in a compressed state by attaching the inner ring presser. apparatus. In any one of Claim 1 and 2,
A rolling bearing device having a fixed structure with a tapered member, characterized in that the thickness of the tapered member is smaller than the distance between the end portion of the maximum diameter of the tapered groove and the inner ring. A rolling bearing having an inner ring and an outer ring, an inner ring supported body fitted to the inner circumferential surface of the inner ring and supported by the inner ring, and an outer ring supported body fitted to the outer circumferential surface of the outer ring and supported by the outer ring One end of the outer ring supported body is in contact with the outer ring supported body and the outer ring presser is fixed in a state where the outer ring is pressed in the axial direction, and the reluctance between the inner ring supported body and the outer ring supported body is determined by their relative positions. In a rolling bearing device comprising a changing resolver,
A taper groove whose inner diameter is increased in the axial direction toward the contact surface of the outer ring supported body and the outer ring presser is formed on the fitting surface of the outer ring supported body with the outer peripheral surface of the outer ring, and the tapered groove is formed in the tapered groove. A rolling bearing device having a fixed structure with a tapered member, wherein a tapered member made of an elastic body that can be inserted is inserted into the tapered groove in a compressed state by attaching the outer ring presser. In claim 4,
A rolling bearing having a fixed structure with a tapered member, wherein a plurality of the tapered grooves are formed in a circumferential direction, and the tapered member is inserted into each tapered groove in a compressed state by attaching the outer ring presser. apparatus. In any one of Claims 4 and 5,
A rolling bearing device having a fixed structure with a tapered member, wherein the thickness of the tapered member is smaller than the distance between the end of the maximum diameter of the tapered groove and the outer ring. In any one of Claims 1 thru | or 6,
The resolver includes an annular detection object in which one of an inner periphery and an outer periphery is decentered with respect to the axis of the rolling bearing, and a detection unit that detects a change in reluctance between the detection object. The detected body on one of the inner ring supported body and the outer ring supported body and the detecting means on the other side so that the eccentric side of the inner circumference and outer circumference of the detected body faces the detecting means. A rolling bearing device having a fixed structure with a tapered member. In any one of Claim 1 and 4,
The inner ring retainer and the inner ring supported body are formed of a material having a higher thermal expansion coefficient than the inner ring supported body, and the inner ring supported body is fitted to the inner ring retainer from the radially outer side. A rolling bearing device having a fixing structure with a tapered member, characterized in that an inlay portion is formed at an end portion in the axial direction and the inlay is fitted. In claim 8,
When the inner ring presser and the inner ring supported body are in a state in which the inner ring presser contacts the inner ring, an axial gap is formed between the convex step portion and the concave step portion constituting the spigot portion, and the inner ring presser and the inner ring presser are supported. A rolling bearing device having a fixed structure with a tapered member, wherein a gap is set so that an axial gap is formed within an operating temperature range between inner ring supported bodies. In any one of Claims 8 and 9,
The inner ring presser is a rolling bearing device having a fixed structure with a tapered member, wherein a gap is set so that a radial gap is formed within the operating temperature range between the inner ring and the inner ring presser. . In any one of Claim 1 and 4,
The outer ring presser and the outer ring supported body are made of a material having a higher coefficient of thermal expansion than the outer ring supported body, and the outer ring supported body fits the outer ring presser from the radially outer side. A rolling bearing device having a fixing structure with a tapered member, characterized in that an inlay portion is formed at an end portion in the axial direction and the inlay is fitted. In claim 11,
When the outer ring presser and the outer ring supported body are in a state in which the outer ring presser contacts the outer ring, an axial gap is formed between the convex step portion and the concave step portion constituting the spigot portion, and the outer ring presser and the outer ring support member. A rolling bearing device having a fixed structure with a tapered member, wherein a gap is set so that an axial gap is formed within an operating temperature range between outer ring supported bodies. In any one of Claims 11 and 12,
The outer ring presser is a rolling bearing device having a fixed structure with a tapered member, wherein a gap is set so that a radial gap is formed between the outer ring and the outer ring presser within an operating temperature range. .

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