JP2008180353A - Rolling bearing device having fixing structure by toothed washer - 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 direct drive motor 100 is composed of a cross roller bearing 14 having an inner race 14a and an outer race 14b, a housing inner 22 which is fitted in the inner circumferential surface of the inner race 14a with a clearance and is supported by the inner race 14a, a rotor 12 which is fitted on the outer circumferential surface of the outer race 14b with a clearance and is supported by the outer race 14b, and a resolver 30 in which the reluctance between the housing inner 22 and the rotor 12 varies according to the position of the rotor 12. Further, toothed washers 56a, 56b are arranged on the fitting surface of the housing inner 22 to be fitted to the lower surface of the inner race 14a, and on the fitting surface of the rotor 12 to be fitted to the lower surface of the outer race 14b respectively. <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 with a toothed washer that is 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. 4 is a sectional view in the axial direction of a conventional rolling bearing device.
As shown in FIG. 4, 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. It is an object of the present invention to provide a rolling bearing device having a fixing structure with a toothed washer suitable for the above.

  [Invention 1] In order to achieve the above object, a rolling bearing device having a fixed structure with a toothed washer 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. The inner ring supported body to be supported, the outer ring supported body that is fitted to the outer peripheral surface of the outer ring and supported by the outer ring, and the reluctance between the inner ring supported body and the outer ring supported body are in their relative positions. In the rolling bearing device including a resolver that changes depending on the condition, a toothed washer is provided on one of the fitting surface of the inner ring supported body with the inner ring and the fitting surface of the inner ring with the inner ring supported body.

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, a toothed washer is provided on one of the fitting surface of the inner ring supported body with the inner ring and the fitting surface of the inner ring with the inner ring supported body. The inner ring supported body and the inner ring are less likely to slip due to the meshing of the washers, and a change in the distance between the inner ring supported body and the inner ring is suppressed.

  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 fixed structure with the toothed washer of the invention 3.

Further, the fitting surface of the inner ring supported body with the inner ring means a surface that contacts or faces the inner ring among the surfaces of the inner ring supported body in a state where the inner ring supported body and the inner ring are fitted. This includes, for example, a fitting surface with the inner peripheral surface of the inner ring of the inner ring supported body or a fitting surface with the lower surface of the inner ring of the inner ring supported body.
Further, the fitting surface of the inner ring with the inner ring supported body refers to a surface that contacts or faces the inner ring supported body among the surfaces of the inner ring in a state where the inner ring supported body and the inner ring are fitted. This includes, for example, a fitting surface of the inner ring with the outer peripheral surface of the inner ring supported body, or a fitting surface with the inner ring supported body on the lower surface of the inner ring.

[Invention 2] Furthermore, the rolling bearing device having a fixing structure with a toothed washer according to Invention 2 is the rolling bearing device having a fixing structure with a toothed washer according to Invention 1, in which the inner ring supported body is connected to the lower surface of the inner ring. The toothed washer was provided on a part of the fitting surface.
With such a configuration, the mounting accuracy of the rolling bearing can be ensured by leaving a surface for pressing the original rolling bearing in part, instead of using a toothed washer on the entire fitting surface.

  [Invention 3] Further, a rolling bearing device having a fixed structure with a toothed washer according to Invention 3 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 a resolver in which reluctance between the inner ring supported body and the outer ring supported body varies depending on their relative positions. In the rolling bearing device provided, a toothed washer is provided on one of a fitting surface of the outer ring supported body with the outer ring and a fitting surface of the outer ring with the outer ring supported body.

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, a toothed washer is provided on one of the fitting surface of the outer ring supported body with the outer ring and the fitting surface of the outer ring with the outer ring supported body. The outer ring supported body and the outer ring are less likely to slip due to the meshing of the washers, and the change in the distance between the outer ring supported body and the outer ring is suppressed.

Here, the fitting surface of the outer ring supported body with the outer ring means a surface that contacts or faces the outer ring among the surfaces of the outer ring supported body when the outer ring supported body and the outer ring are fitted. This includes, for example, a fitting surface of the outer ring supported body with the outer peripheral surface of the outer ring or a fitting surface of the outer ring supported body with the lower surface of the outer ring.
The fitting surface of the outer ring with the outer ring supported body refers to a surface that contacts or faces the outer ring supported body in the outer ring surface in a state where the outer ring supported body and the outer ring are fitted. This includes, for example, a fitting surface of the outer ring with the inner peripheral surface of the outer ring supported body, or a fitting surface with the outer ring supported body on the lower surface of the outer ring.

[Invention 4] Furthermore, the rolling bearing device having a fixing structure with a toothed washer according to Invention 4 is the rolling bearing device having a fixing structure with a toothed washer according to Invention 3, in which the outer ring supported body is connected to the lower surface of the outer ring. The toothed washer was provided on a part of the fitting surface.
With such a configuration, the mounting accuracy of the rolling bearing can be ensured by leaving a surface for pressing the original rolling bearing in part, instead of using a toothed washer on the entire fitting surface.

  [Invention 5] Furthermore, the rolling bearing device having a fixing structure with a toothed washer according to Invention 5 is the rolling bearing device having a fixing structure with a toothed washer according to any one of Inventions 1 to 4, 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 6] Further, the rolling bearing device having a fixing structure with a toothed washer according to Invention 6 is the rolling bearing device having a fixing structure with a toothed washer according to any one of Inventions 1 and 3, and is further preloaded in the axial direction. Is provided with an inner ring fixing means for fixing the inner ring to the inner ring supported body, the inner ring fixing means is made of a material having a higher thermal expansion coefficient than the inner ring supported body, and the inner ring supported body is The inner ring fixing means and the inner ring supported body were fitted with each other by forming an inlay portion at their axial ends so that the inner ring fixing means was fitted from the outside in the radial direction.

With such a configuration, when the temperature rises, the inner ring fixing means 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. The Therefore, it is possible to prevent a radial gap between the inner ring supported body and the inner ring fixing means.
Here, the inlay portion is a concave and convex step portion for fitting the inner ring fixing means and the inner ring supported body into an inlay, and a concave step portion is provided on one of the inner ring fixing means and the inner ring supported body, and a convex step portion on the other side. May be provided. Further, the inlay portion may be provided on the inner peripheral surface side of the inner ring fixing means and the inner ring supported body, or may be provided on the outer peripheral surface side.

  [Invention 7] Further, the rolling bearing device having a fixing structure with a toothed washer according to Invention 7 is the rolling bearing device having a fixing structure with a toothed washer according to Invention 6, wherein the inner ring fixing means and the inner ring supported body are: In a state where the inner ring fixing means is in contact with the inner ring, an axial gap is formed between the convex step portion and the concave step portion constituting the spigot portion in the axial direction between the inner ring fixing means and the inner ring supported body. The gap is set such that the gap is formed within the operating temperature range.

  With such a configuration, even if the inner ring fixing means and the inner ring supported body expand in the axial direction within the operating temperature range, the convex step portion and the concave step portion, and the inner ring fixing means and the inner ring supported body come into contact with each other. Therefore, the inner ring fixing means and the inner ring supported member can always maintain the state in which the inner ring fixing means fixes the inner ring with respect to the axial fitting of the inner ring fixing means and the inner ring supported body.

  [Invention 8] Furthermore, the rolling bearing device having a fixing structure with a toothed washer according to Invention 8 is the rolling bearing device having a fixing structure with a toothed washer according to any one of Inventions 6 and 7, wherein the inner ring fixing means 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 fixing means.

  With such a configuration, even if the inner ring fixing means and the inner ring supported body expand within the operating temperature range, the inner ring and the inner ring fixing means do not come into contact with each other. With regard to the fitting in the radial direction, it is always possible to maintain the state where the inner ring supported body fixes the inner ring.

  [Invention 9] Furthermore, the rolling bearing device having a fixing structure with a toothed washer according to Invention 9 is the rolling bearing device having a fixing structure with a toothed washer according to any one of Inventions 1 and 3, and is further preloaded in the axial direction. And an outer ring fixing means for fixing the outer ring to the outer ring supported body, and the outer ring fixing means is made of a material having a higher thermal expansion coefficient than the outer ring supported body. The outer ring fixing means and the outer ring supported body were fitted with each other by forming an inlay portion at an end portion in the axial direction so that the outer ring fixing means was fitted from the outside in the radial direction.

With such a configuration, when the temperature rises, the outer ring fixing means 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. The Therefore, it is possible to prevent a radial gap from being generated between the outer ring supported body and the outer ring fixing means.
Here, the inlay part is an uneven step part for fitting the outer ring fixing means and the outer ring supported body into the inlay, and one of the outer ring fixing means and the outer ring supported body has a concave step part, and the other is a convex step part. May be provided. Further, the inlay portion may be provided on the inner peripheral surface side of the outer ring fixing means and the outer ring supported body, or may be provided on the outer peripheral surface side.

  [Invention 10] Further, the rolling bearing device having a fixing structure with a toothed washer according to Invention 10 is the rolling bearing device having a fixing structure with a toothed washer according to Invention 9, wherein the outer ring fixing means and the outer ring supported body are: In a state where the outer ring fixing means is in contact with the outer ring, an axial gap is formed between the convex step portion and the concave step portion constituting the inlay portion, and an axial direction is provided between the outer ring fixing means and the outer ring supported body. The gap is set such that the gap is formed within the operating temperature range.

  With such a configuration, even if the outer ring fixing means 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 fixing means and the outer ring supported body come into contact with each other. Therefore, the outer ring fixing means and the outer ring supported body can be kept in a state where the outer ring fixing means fixes the outer ring at all times in the axial direction.

  [Invention 11] Furthermore, the rolling bearing device having a fixing structure with a toothed washer according to Invention 11 is the rolling bearing device having a fixing structure with a toothed washer according to any one of Inventions 9 and 10, wherein the outer ring fixing means includes: The clearance is set such that a radial clearance is formed within the operating temperature range between the outer ring and the outer ring fixing means.

  With such a configuration, even if the outer ring fixing means and the outer ring supported body expand within the operating temperature range, the outer ring and the outer ring fixing means do not come into contact with each other. With respect to the fitting in the radial direction, the outer ring supported body can always maintain the state in which the outer ring is fixed.

  As described above, according to the rolling bearing device having the fixed structure with the toothed washer according to 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 fixing structure with the toothed washer of the invention 2 or 4, the entire fitting surface is not made into the toothed washer, but the surface for pressing the original rolling bearing is left in a part. Thus, the effect that the mounting accuracy of the rolling bearing can be ensured can be obtained.
Furthermore, according to the rolling bearing device having the fixed structure with the toothed washer according to the third aspect, 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 fixing structure with the toothed washer according to the sixth aspect of the invention, it is possible to prevent a radial gap from being generated between the inner ring supported body and the inner ring fixing means even when the temperature rises. The effect that it can be obtained.
Furthermore, according to the rolling bearing device having the fixing structure with the toothed washer according to the seventh aspect, the inner ring fixing means always maintains the state in which the inner ring fixing means fixes the inner ring with respect to the inner ring fixing means and the inner ring supported body. The effect that it can do is acquired.

Further, according to the rolling bearing device having the fixing structure with the toothed washer according to the eighth aspect, the inner ring supported body always fixes the inner ring with respect to the fitting of the inner ring, the inner ring fixing means and the inner ring supported body in the radial direction. The effect that a state can be maintained is acquired.
Furthermore, according to the rolling bearing device having the fixing structure with the toothed washer according to the ninth aspect, it is possible to prevent the occurrence of a radial gap between the outer ring supported body and the outer ring fixing means even when the temperature rises. The effect that it can be obtained.

Furthermore, according to the rolling bearing device having the fixing structure with the toothed washer according to the tenth aspect, the outer ring fixing means and the outer ring supported body always maintain the state in which the outer ring fixing means fixes the outer ring in the axial fitting. The effect that it can do is acquired.
Furthermore, according to the rolling bearing device having the fixing structure with the toothed washer according to the eleventh aspect, the outer ring supported body always fixes the outer ring with respect to the radial fitting of the outer ring, the outer ring fixing means and the outer ring supported body. The effect that a state can be maintained is acquired.

[First Embodiment]
Hereinafter, a first embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a view showing a first embodiment of a rolling bearing device having a fixing structure with a toothed washer 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 so that the inner ring 14a is pressed against the housing inner 22 in the axial direction. 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.
A housing hole 54a for housing the toothed washer 56a is formed in the fitting surface of the housing inner 22 with the lower surface of the inner ring 14a, and the tooth surface of the toothed washer 56a faces the inner ring 14a in the housing hole 54a. A toothed washer 56a is inserted. The plate thickness of the toothed washer 56a is smaller than the axial length of the accommodation hole 54a.

On the other hand, an accommodation hole 54b for accommodating the toothed washer 56b is formed in the fitting surface of the rotor 12 with the lower surface of the outer ring 14b, and the tooth surface of the toothed washer 56b is connected to the outer ring 14b side in the accommodation hole 54b. A toothed washer 56b is inserted toward the end. The plate thickness of the toothed washer 56a is smaller than the axial length of the accommodation hole 54a.
Usually, the fitting surface is manufactured with a very good surface roughness by machining, but there is a problem that the housing inner 22 and the inner ring 14a, the rotor 12 and the outer ring 14b become slippery. In the present embodiment, in order to prevent this, the toothed washers 56a and 56b are provided on the fitting surface to make it difficult to slip. Moreover, the fitting accuracy of the cross roller bearing 14 can also be ensured by leaving a surface for pressing the original cross roller bearing 14 in part, instead of using the entire surface of the fitting with the toothed washers 56a and 56b. .

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, the toothed washer 56a is provided on the inner ring 14a on the fitting surface with the lower surface of the inner ring 14a of the housing inner 22, so that the toothed washer 56a is engaged. The housing inner 22 and the inner ring 14a are less likely to slip, and a change in the distance between the housing inner 22 and the inner ring 14a is suppressed. On the outer ring 14b side, the toothed washer 56b is provided on the mating surface of the rotor 12 with the lower surface of the outer ring 14b. Therefore, the engagement of the toothed washer 56b makes it difficult for the rotor 12 and the outer ring 14b to slip. Change in the distance between the outer ring 14b and the outer ring 14b is suppressed. As a result, the change in the resolver gap 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. And the rotor 12 supported by the outer ring 14b and the resolver 30 in which the reluctance between the housing inner 22 and the rotor 12 varies depending on the position of the rotor 12, and is fitted to the lower surface of the inner ring 14a of the housing inner 22 A toothed washer 56a was provided on the surface.

  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, the toothed washer 56b is provided on the fitting surface of the rotor 12 with the lower surface of the outer ring 14b.
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.

Further, in the present embodiment, the toothed washer 56a is provided on a part of the fitting surface of the housing inner 22 with the lower surface of the inner ring 14a.
As a result, the fitting accuracy of the cross roller bearing 14 can be ensured by leaving a part of the fitting surface that presses the original cross roller bearing 14 instead of using the toothed washer 56a as a whole.

Further, in the present embodiment, the toothed washer 56b is provided on a part of the fitting surface with the lower surface of the outer ring 14b of the rotor 12.
As a result, the fitting accuracy of the cross roller bearing 14 can be ensured by leaving a part of the fitting surface that presses the original cross roller bearing 14 instead of using the toothed washer 56b as a whole.

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 5, the housing inner 22 corresponds to the inner ring supported body of the invention 1 to 3 or 5, and the rotor 12 The resolver rotor 18 corresponds to the detected body of the fifth aspect, corresponding to the outer ring supported body of the first, third, or fifth aspect. The position detector 20 corresponds to the detection means of the fifth aspect.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to the drawings. 2 and 3 are views showing a second embodiment of a rolling bearing device having a fixing structure with a toothed washer 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. 2 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. 2, 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 so that the inner ring 14a is pressed against the housing inner 22 in the axial direction. 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. 3 is a diagram showing a case where the arrangement at the spigot fitting portion is reversed.
As shown in FIG. 3 (a), when an arrangement opposite to that shown in FIG. 2 in which the inner ring retainer 26 is disposed radially outward at the inner joint portion of the housing inner 22 and the inner ring retainer 26 is employed, the temperature is When raised, 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.

Further, as shown in FIG. 2, the inner ring retainer 26 and the housing inner 22 are provided with a protruding step portion 34a in a state in which the pressing portion 26b of the inner ring retainer 26 is in contact with and fixed to 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. Thereby, 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 come into contact with each other. 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. 3A, the temperature rises when an arrangement opposite to that shown in FIG. 2 in which the outer ring presser 28 is arranged radially outside is adopted in the inlay fitting portion of the rotor 12 and the outer ring presser 28. 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. 2, the outer ring retainer 28 and the rotor 12 are formed on the convex step portion 36a in a state where the pressing portion 28b of the outer ring retainer 28 is in contact with and fixed to the upper surface of the outer ring 14b by fastening the bolt 28a. 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 fitting of the inner ring retainer 26 and the housing inner 22 in the axial direction, the state in 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 6 or 7, the inner ring presser 26 corresponds to the inner ring fixing means of the invention 6 to 8, and the rotor 12 corresponds to the invention 9. Alternatively, the outer ring presser 28 corresponds to the outer ring fixing member of the ninth to eleventh aspects.

  In the first and second embodiments, the toothed washers 56a and 56b are provided on the fitting surface of the housing inner 22 with the lower surface of the inner ring 14a and the fitting surface of the outer ring 14b of the rotor 12 with the lower surface. Although it provided and comprised, it is not restricted to this, A toothed washer can also be provided and comprised only in one fitting surface. Further, not only the fitting surface with the lower surface of the inner ring 14a or the outer ring 14b, but a fitting surface with the inner ring 14a or the outer ring 14b, for example, fitting with the inner circumferential surface of the inner ring 14a or the outer circumferential surface of the outer ring 14b. Toothed washers 56a and 56b may be provided on the surface.

  Further, in the first and second embodiments, the housing hole 22a is formed in the fitting surface with the lower surface of the inner ring 14a of the housing inner 22, and the toothed washer 56a is fitted into the housing hole 54a. However, the present invention is not limited to this, and a housing hole 54a may be formed on the lower surface of the inner ring 14a, and a toothed washer 56a may be fitted into the housing hole 54a. In this case, the tooth surface of the toothed washer 56a is directed to the housing inner 22 side. Moreover, the point which may be provided only in one fitting surface and the point which is not restricted to the lower surface of the inner ring | wheel 14a or the outer ring | wheel 14b are the same as the above.

  In the first and second embodiments, the housing hole 54b is formed in the fitting surface with the lower surface of the outer ring 14b of the rotor 12, and the toothed washer 56b is fitted into the housing hole 54b. However, the present invention is not limited to this, and a housing hole 54b may be formed in the lower surface of the outer ring 14b, and a toothed washer 56b may be inserted into the housing hole 54b. In this case, the tooth surface of the toothed washer 56b faces the rotor 12 side.

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 with the toothed washer according to the present invention is applied to the structure for rotatably supporting 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. 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 a spigot 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 gaps 54a, 54b receiving holes 56a, 56b toothed washers 12a, 22a flanges 26b, 28b pressing portions 18a, 20a, 26a, 28a bolts

Claims (11)

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 a rolling bearing device comprising a resolver in which the reluctance between the inner ring supported body and the outer ring supported body varies depending on their relative positions.
A rolling structure having a fixing structure with a toothed washer, wherein a toothed washer is provided on one of a fitting surface of the inner ring supported body with the inner ring and a fitting surface of the inner ring with the inner ring supported body. Bearing device. In claim 1,
A rolling bearing device having a fixed structure with a toothed washer, wherein the toothed washer is provided on a part of a fitting surface of the inner ring supported body with a lower surface of 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 And a rolling bearing device comprising a resolver in which the reluctance between the inner ring supported body and the outer ring supported body varies depending on their relative positions.
A rolling structure having a fixing structure with a toothed washer, wherein a toothed washer is provided on one of a fitting surface of the outer ring supported body with the outer ring and a fitting surface of the outer ring with the outer ring supported body. Bearing device. In claim 3,
A rolling bearing device having a fixed structure with a toothed washer, wherein the toothed washer is provided on a part of a fitting surface of the outer ring supported body with a lower surface of the outer ring. In any one of Claims 1 thru | or 4,
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 toothed washer. In any one of Claim 1 and 3,
Furthermore, it comprises an inner ring fixing means for applying an axial preload to fix the inner ring to the inner ring supported body,
The inner ring fixing means and the inner ring are configured such that the inner ring fixing means is made of a material having a higher coefficient of thermal expansion than the inner ring supported body, and the inner ring supported body fits the inner ring fixing means from the outside in the radial direction. A rolling bearing device having a fixed structure with a toothed washer, characterized in that an inlay portion is formed at an end portion in the axial direction of the supported body and the inlay is fitted. In claim 6,
In the state where the inner ring fixing means is in contact with the inner ring, the inner ring fixing means and the inner ring supported body have an axial gap between the convex step portion and the concave step portion constituting the spigot portion. A rolling bearing device having a fixed structure with a toothed washer, wherein a gap is set so that an axial gap is formed within the operating temperature range between the means and the inner ring supported body. In any one of Claim 6 and 7,
The inner ring fixing means is a rolling structure having a fixing structure with a toothed washer, characterized in that a gap is set between the inner ring and the inner ring fixing means so that a radial gap is formed within an operating temperature range. Bearing device. In any one of Claim 1 and 3,
Furthermore, it comprises an outer ring fixing means for applying an axial preload to fix the outer ring to the outer ring supported body,
The outer ring fixing means and the outer ring are configured such that the outer ring fixing means is made of a material having a higher thermal expansion coefficient than the outer ring supported body, and the outer ring supported body fits the outer ring fixing means from the radially outer side. A rolling bearing device having a fixed structure with a toothed washer, characterized in that an inlay portion is formed at an end portion in the axial direction of the supported body and the inlay is fitted. In claim 9,
The outer ring fixing means and the outer ring supported body are configured such that, in a state where the outer ring fixing means is in contact with the outer ring, an axial gap is formed between the convex step portion and the concave step portion constituting the spigot portion. A rolling bearing device having a fixed structure with a toothed washer, wherein a clearance is set so that an axial clearance is formed within the operating temperature range between the means and the outer ring supported body. In any one of Claims 9 and 10,
The outer ring fixing means is a rolling structure having a fixing structure with a toothed washer, characterized in that a gap is set between the outer ring and the outer ring fixing means so that a radial gap is formed within an operating temperature range. Bearing device.

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