WO2022044156A1

WO2022044156A1 - Rotary electrical machine

Info

Publication number: WO2022044156A1
Application number: PCT/JP2020/032157
Authority: WO
Inventors: 祐介植野; 亮宏佐久間; 和樹三ツ石
Original assignee: 三菱電機株式会社
Priority date: 2020-08-26
Filing date: 2020-08-26
Publication date: 2022-03-03
Also published as: CN115244830A; JPWO2022044156A1; JP6952931B1

Abstract

Provided is a rotary electrical machine 100a that addresses the problem in which a bearing fixing member 60a easily falls from a shaft 20 or the workability of bearing removal work is poor, and that, with respect to said problem, is characterized by comprising the bearing fixing member 60a provided with a shaft through hole 63 that is closed in the circumferential direction, the bearing fixing member 60a being provided with a notch part 62a having a notched shape from the outer circumference to the inside, and a distance L1 in the radial direction between a central axis AX and a location closest to the central axis AX in the notch part 62a being smaller than a radius L2 of the outer circumference 53 of a bearing 50a, and greater than a distance L3 in the radial direction between the central axis AX and a location farthest from the central axis AX of the inner circumference of the shaft through hole 63.

Description

Rotating machine

This disclosure relates to a rotary electric machine having a bearing.

In a rotary electric machine, a bearing is installed on a bracket attached to the stator via a frame, and the shaft to which the rotor is fixed is rotatably supported by the bearing, and the rotor rotates. In order to prevent the bearing from moving in the direction of the central axis where the central axis of the shaft extends, a bearing fixing member that holds the bearing to the bracket is attached to the bracket. The bearing fixing member is provided with a shaft through hole through which the shaft passes in the center.

The gap between the rotor and the bearing in the central axis direction is often narrow in order to shorten the overall length of the rotary electric machine. Therefore, when the bearing is replaced in the maintenance and inspection of the rotary electric machine, the workability of hooking the claw of the extraction tool, which is a tool for pulling out the bearing from the shaft, on the bearing is poor, and it takes time to replace the bearing.

Patent Document 1 disclosed about a conventional rotary electric machine discloses a bearing fixing member provided with a notch extending from the shaft through hole to the outer periphery in one direction of the shaft through hole. By providing a notch extending to the outer circumference in one direction of the shaft through hole, the bearing fixing member can be attached and detached from the side of the shaft, and the bearing can be removed with the bearing fixing member removed. I am doing it.

Jitsukaisho 51-07714 Gazette

However, the bearing fixing member disclosed in Patent Document 1 is provided with a notch extending to the outer periphery in one direction of the shaft through hole, so that the bearing fixing member is removed when the bearing fixing member is removed during the bearing removal work. There was a problem that it was easy to fall from the shaft.

The present disclosure has been made to solve the above-mentioned problems, and an object of the present invention is to provide a rotary electric machine capable of improving the work efficiency of the bearing removal work without the bearing fixing member falling from the shaft.

The rotary electric machine according to the present disclosure can be rotated by a stator structure having a stator and a stator support portion for supporting the stator, a bracket attached to the stator structure, a bearing arranged on the bracket, and a bearing. A shaft supported by the shaft, a rotor fixed to the shaft, and attached to the bracket placed between the bearing and the rotor, and provided with a shaft through hole closed in the circumferential direction through which the shaft passes, and the bearing is bracketed. The bearing fixing member is provided with a notch portion having a shape notched from the outer periphery of the bearing fixing member toward the inside of the bearing fixing member, and is provided with a notch portion of the shaft of the notch portion. The radial distance between the point closest to the central axis and the central axis is smaller than the radius of the outer circumference of the bearing, and the radial distance between the point farthest from the central axis on the inner circumference of the shaft through hole and the central axis. Is larger than.

According to the rotary electric machine according to the present disclosure, the work efficiency of the bearing removal work can be improved without the bearing fixing member falling from the shaft.

It is sectional drawing which shows the rotary electric machine which concerns on Embodiment 1 of this disclosure. It is an external view of the bearing fixing member which concerns on Embodiment 1 of this disclosure. It is sectional drawing which cut the bearing fixing member which concerns on Embodiment 1 of this disclosure along the line AA of FIG. It is sectional drawing which cut the bearing fixing member which concerns on Embodiment 1 of this disclosure along the line BB of FIG. It is a schematic diagram of the bearing removal work which concerns on Embodiment 1 of this disclosure. It is an external view of the bearing fixing member which concerns on Embodiment 2 of this disclosure. It is an external view of the bearing fixing member which concerns on Embodiment 3 of this disclosure. It is sectional drawing which shows the rotary electric machine which concerns on Embodiment 4 of this disclosure. It is an external view of the bearing fixing member which concerns on Embodiment 4 of this disclosure. It is a schematic diagram of the bearing removal work which concerns on Embodiment 4 of this disclosure.

Hereinafter, the rotary electric machine according to the embodiment of the present disclosure will be described in detail with reference to the drawings. In the embodiment of the present disclosure, an example in which the rotary electric machine is an induction motor will be described.

Embodiment 1.
First, the configuration of the rotary electric machine according to the first embodiment of the present disclosure will be described. FIG. 1 is a cross-sectional view showing a rotary electric machine according to the first embodiment of the present disclosure. In FIG. 1, the upper side of the central axis AX shows a cross section, and the lower side of the central axis AX shows an appearance.

In FIG. 1, the rotary electric machine 100a includes a stator 31, a frame 32,

brackets

40a and 40b,

bearings

50a and 50b, a bearing fixing member 60a, a rotor 10, and a shaft 20. The rotor 10 is rotatably installed with respect to the stator 31 about the central axis AX, which is the center of rotation of the shaft. In the following description, the direction in which the central axis AX extends is described as the central axis direction, the direction in which the central axis AX rotates around the central axis AX is described as the circumferential direction, and the direction perpendicular to the central axis AX is described as the radial direction.

The stator 31 includes a stator core 311 and a coil end 312. The stator 31 is fitted and fixed to a frame 32 which is a stator support portion for supporting the stator 31, and the stator 31 and the frame 32 form a stator structure 30. That is, the rotary electric machine 100a includes a stator structure 30. The stator structure 30 has a stator 31 and a frame 32 which is a stator support portion for supporting the stator.

Brackets

40a and 40b are attached to both sides of the frame 32 which is a part of the stator structure 30. That is, the

brackets

40a and 40b are attached to the stator structure 30.

Bearings

50a and 50b are arranged on the

brackets

40a and 40b. The bearing 50a is a bearing and has an outer ring 51 and an inner ring 52, and the inner ring 52 rotates with respect to the outer ring 51. The bearing 50a is arranged so that the outer ring 51 is in contact with the bracket 40a.

The rotor 10 includes a rotor core 11 and end rings 12 provided on both end faces of the rotor core 11. That is, the rotor core 11 and the end ring 12 are a part of the rotor 10. The rotor 10 is fitted and fixed to the shaft 20. The shaft 20 is rotatably supported around the central axis AX by

bearings

50a and 50b. The rotor 10 can rotate around the central axis AX together with the shaft 20. The shaft end surface 21, which is the end surface of the shaft end in the direction in which the bearing 50a of the shaft 20 is attached, is provided with a center hole 211 which is a bottomed hole at the center where the central shaft AX and the shaft end surface 21 intersect.

The bearing fixing member 60a is arranged between the bearing 50a and the rotor 10 in the central axial direction, and is attached to the bracket 40a. In other words, the bearing fixing member 60a is arranged on the side opposite to the side where the bracket 40a is located with respect to the bearing 50a in the central axial direction, and is attached to the bracket 40a. The bearing fixing member 60a is provided with a shaft through hole 63 that is closed in the circumferential direction, and the shaft 20 passes through the shaft through hole 63. The bearing fixing member 60a holds the bearing 50a against the bracket 40a and fixes it. More specifically, in the bearing fixing member 60a, the outer ring 51 of the bearing 50a is pressed against the bracket 40a from the side where the rotor 10 is arranged to the bracket 40a side in the central axis direction, and the outer ring 51 of the bearing 50a is bracketed. It is fixed to 40a. As a result, the bearing fixing member 60a prevents the bearing 50a from moving in the central axial direction.

Next, the bearing fixing member 60a will be described in detail. FIG. 2 is an external view of the bearing fixing member according to the first embodiment of the present disclosure, and is viewed from the direction of the bearing 50a side in the central axial direction when the bearing fixing member 60a is arranged in the rotary electric machine 100a. It shows the appearance. FIG. 3 is a cross-sectional view of the bearing fixing member 60a according to the first embodiment of the present disclosure cut along the line AA of FIG. FIG. 4 is a cross-sectional view of the bearing fixing member according to the first embodiment of the present disclosure cut along the line BB of FIG. The cross section of the bearing fixing member 60a in FIG. 1 shows a cross section cut along the line CC in FIG. In FIG. 2, the central axis AX is indicated by a point. A part of the outer circumference 53 of the bearing 50a is shown by a dotted line.

In FIG. 2, the bearing fixing member 60a has a disk-like shape having an outer circumference 61a which is an arc centered on the central axis AX when viewed from the central axis direction, and has a shaft through hole 63 and two notches. A portion 62a and four screw holes 64 are provided.

The shaft through hole 63 is provided so that the shaft 20 centered on the central axis AX passes through when the bearing fixing member 60a is arranged in the rotary electric machine 100a. In FIG. 2, the shaft through hole 63 is a circular hole that penetrates in the central axis direction about the central axis AX. The hole diameter of the shaft through hole 63 is larger than the diameter of the shaft 20 at the position where the bearing fixing member 60a is arranged in the rotary electric machine 100a and the shaft 20 passes through the shaft through hole 63. That is, the shaft through hole 63 is larger than the cross section of the shaft 20. As a result, the shaft 20 can rotate without contacting the bearing fixing member 60a attached to the bracket 40a with the shaft 20.

Further, in FIG. 2, the shaft through hole 63 is a hole closed in the circumferential direction. As a result, if the shaft 20 is passed through the shaft through hole 63, the bearing fixing member 60a does not come off from the shaft 20 on the side of the shaft 20, and the bearing fixing member 60a does not fall from the shaft 20.

In the present embodiment, the shaft through hole 63 will be described as an example of a circular hole centered on the central axis AX. In the shaft through hole 63, the shaft 20 passes through and the bearing fixing member 60a is brought into contact with the shaft 20. However, as long as the hole is closed in the circumferential direction, it may be a polygonal hole or a hole whose center is deviated from the central axis AX.

In FIG. 2, the notch portion 62a has a shape notched from the outer circumference 61a of the bearing fixing member 60a, which is an arc centered on the central axis AX, toward the inside of the bearing fixing member 60a. The notch portion 62a is composed of two notch side surfaces 621a and a notch end surface 622a. In the following description, a plane extending in the radial direction including the central axis AX of the shaft and which is a reference plane for the shape of the notch portion 62a will be referred to as a reference plane XR.

The notched side surface 621a is a flat surface extending inward from the outer peripheral 61a of the bearing fixing member 60a. The notch side surface 621a is a plane parallel to the reference plane XR, separated from the reference plane XR by half (H / 2) of the notch width H having a constant length. The two notched side surfaces 621a included in the one notched portion 62a are parallel to each other with a certain distance H apart from each other.

The notch end surface 622a is a surface that connects the two notch side surfaces 621a included in one notch portion 62a at the inner end of the bearing fixing member 60a. In FIG. 2, the notched end surface 622a is a plane that is parallel to the central axis AX and perpendicular to the reference plane XR at a certain radial distance L1 from the central axis AX.

In FIG. 2 when the bearing fixing member 60a is viewed from the central axis direction, the reference plane XR is shown by a straight line extending in the radial direction, which is a projection of the reference plane XR in the central axis direction. The notch side surface 621a is shown as two parallel straight lines separated by half (H / 2) of the notch width H from the straight line which is the projection of the reference plane XR, and the bearing fixing member is shown from the outer circumference 61a. It extends inward of 60a. The notched end surface 622a is shown as a straight line perpendicular to a straight line that is a projection of the reference plane XR at a distance L1 from the central axis AX. The shape of the notch 62a when the bearing fixing member 60a is viewed from the central axis direction is such that two parallel straight lines extending inward from the outer circumference 61a of the bearing fixing member 60a, which is a projection of the notch side surface 621a, are the inner ends of the straight lines. It is a U-shape connected by.

The two notches 62a provided in the bearing fixing member 60a are located at point-symmetrical positions with respect to the point of the central axis AX in the external view of FIG. 2 when viewed from the central axis direction, and are evenly spaced at an angle in the circumferential direction. In position.

The notch end 623a is a portion closest to the central axis AX of the notch portion 62a, and is a line where the notch end surface 622a and the reference plane XR intersect in FIG. The radial distance between the notch end 623a and the central axis AX is the distance L1. The distance L1 is smaller than the radius L2 of the outer circumference 53 of the bearing 50a. That is, the radial distance L1 between the portion of the notch 62a that is closest to the central axis AX of the shaft 20 and the central axis AX is smaller than the radius L2 of the outer circumference 53 of the bearing 50a. This creates an engagement surface region on the end surface of the bearing 50a on the rotor 10 side where the claw 931 of the extraction tool described later can be engaged.

The distance L1 between the notch end 623a, which is the position closest to the central axis AX of the shaft 20 of the notch portion 62a, and the central axis AX is larger than the radius L3 of the shaft through hole 63. In FIG. 2, since the shaft through hole 63 is a circular hole penetrating in the central axis direction about the central axis AX, the radius L3 of the shaft through hole 63 is from the central axis AX of the inner circumference of the shaft through hole 63. This is the radial distance between the farthest point and the central axis AX. That is, the radial distance L1 between the position closest to the central axis AX of the shaft 20 of the notch portion 62a and the central axis AX is the point farthest from the central axis AX on the inner circumference of the shaft through hole 63 and the central axis AX. Greater than the radial distance L3. As a result, since the notch portion 62a does not reach the shaft through hole 63 from the outer peripheral 61a, the shaft through hole 63 is a hole closed in the circumferential direction, and if the shaft 20 is passed through the shaft through hole 63, the bearing is fixed. The member 60a does not come off the shaft 20 to the side of the shaft 20.

The radius of the outer circumference 61a of the bearing fixing member 60a is larger than the radius L2 of the outer circumference 53 of the bearing 50a. In FIG. 2, the distance between the outer peripheral 61a, which is the farthest point from the central axis AX of the bearing fixing member 60a, and the central axis AX is the radius of the outer peripheral 61a of the bearing fixing member 60a, and is larger than the radius L2 of the outer peripheral 53 of the bearing 50a. big.

The screw hole 64 has a female thread on the inner circumference. A mounting screw (not shown) is passed through a screw through hole (not shown) provided in the bracket 40a from the side opposite to the side where the bearing fixing member 60a of the bracket 40a is mounted, and the inner circumference of the screw hole 64 of the bearing fixing member 60a is formed. Screw with a female screw. By tightening the mounting screws, the bearing fixing member 60a presses and fixes the bearing 50a to the bracket 40a, and the bearing fixing member 60a is attached to the bracket 40a.

In FIG. 2, the bearing fixing member 60a is a bearing fitting hole which is a bottomed hole into which the bearing 50a fits, which is cut into a columnar shape so that the bearing 50a can be shallowly inserted into the end surface of the bearing fixing member 60a on the bearing 50a side. 66 is provided. The bearing fixing member 60a has a pressing surface 67 in contact with the bearing 50a in the central axial direction at the bottom of the bearing fitting hole 66. The bearing fixing member 60a pushes the bearing 50a toward the bracket 40a in the central axial direction via the pressing surface 67, presses the bearing 50a against the bracket 40a, and fixes the bearing 50a. Specifically, the pressing surface 67 is in contact with the outer ring 51 of the bearing 50a. Further, the bearing fixing member 60a has an inner peripheral surface 661 in contact with the outer peripheral 53 of the bearing 50a on the inner circumference of the side surface of the bearing fitting hole 66. A contact avoidance step 672 is provided on the inner peripheral side of the pressing surface 67 of the bearing fixing member 60a to prevent the bearing fixing member 60a and the inner ring 52 of the bearing 50a from coming into contact with each other. In the first embodiment, the example in which the bearing fixing member 60a has the bearing fitting hole 66 and the inner peripheral surface 661 will be described, but the bearing fixing member 60a does not have the bearing fitting hole 66 and the inner peripheral surface 661. , The pressing surface 67 may be provided on the end surface of the bearing fixing member 60a on the bearing 50a side.

When the bearing fixing member 60a has an inner peripheral surface 661, when the bearing fixing member 60a is attached to the bracket 40a, the inner peripheral surface 661 is fitted with the outer peripheral 53 of the bearing 50a in the radial direction of the bearing fixing member 60a. Positioning can be easily performed, and the work efficiency of the bearing fixing member 60a mounting work in bearing replacement can be improved. Further, when the bearing fixing member 60a has the notch portion 62a and the inner peripheral surface 661, the notch portion 62a provides the bearing fixing flexibility so that the inner peripheral surface 661 can be slightly expanded in the direction away from the central axis AX. The member 60a is provided, and the fitability between the inner peripheral surface 661 and the bearing 50a is improved, and the work efficiency of the bearing fixing member 60a mounting work in bearing replacement can be further improved.

Next, in the rotary electric machine 100a according to the first embodiment of the present disclosure, the rotary electric machine 100a is disassembled to take out a group of members integrated with the rotor 10, and the bearing 50a is pulled out from the shaft 20 using a drawing tool and removed. Explain the work. This work is performed by replacing the bearing in the maintenance and inspection of the rotary electric machine 100a.

First, a mounting screw (not shown) for fixing the bracket 40a to the stator structure 30 is removed from the assembled rotary electric machine 100a in FIG. 1, and the bearing fixing member 60a is fixed to the bracket 40a. Remove the mounting screws not shown and remove the bracket 40a from the stator structure 30. Further, a group of members integrated with the rotor 10 including the rotor 10, the shaft 20, the bearing 50a, and the bearing fixing member 60a is taken out from the stator structure 30.

Next, pull out the bearing 50a from the shaft 20 and remove it. FIG. 3 is a schematic view of the bearing removing operation according to the first embodiment of the present disclosure. In FIG. 3, the upper side of the central axis AX shows a cross section, and the lower side of the central axis AX shows an appearance. The cross section of the bearing fixing member 60a in FIG. 3 shows a cross section cut along the line AA in FIG.

In FIG. 3, the shaft 20 is fitted and fixed to the rotor 10. Further, the bearing 50a is attached to the shaft 20 by fitting the inner ring 52 of the bearing 50a, which is the state before the bearing 50a is removed. A bearing fixing member 60a is arranged between the rotor 10 and the bearing 50a in the central axial direction, and the shaft 20 passes through a shaft through hole 63 provided in the bearing fixing member 60a.

In FIG. 3, a drawing tool is attached to the shaft end in the direction in which the bearing 50a of the shaft 20 is attached. The extraction tool is a tool for removing a member fitted to the shaft 20 by extracting it from the shaft 20. The extraction tool is also called a puller.

The extraction tool consists of a columnar column 910 arranged in the center of the extraction tool, a beam 920 extending from the column 910 in a direction perpendicular to the longitudinal direction of the column 910, and folding from the beam 920 to two tips of the beam 920. It is equipped with two arms 930 rotatably attached in a bending direction. The tip of the arm 930 has a claw 931 that is perpendicular to the longitudinal direction of the arm 930 and protrudes toward the support 910. One end of the support column 910 has a conical shape, and the conical shape is applied to the center hole 211 of the shaft end surface 21 of the shaft 20, and the support column 910 is rotatable about the central axis AX of the shaft 20 with respect to the shaft 20. A male screw shape is formed on the outer peripheral surface of the side surface of the support column 910. In the center of the beam 920, a hole is provided in which a female screw shape that fits the male screw shape of the support column 910 is formed on the inner circumference. The beam 920 is attached to the column 910 so that the male thread shape of the column 910 and the female thread shape of the hole of the beam 920 match, and when the column 910 rotates, the beam 920 moves in the longitudinal direction of the column 910. On the other end side of the column 910, there is a handle 940 extending in a direction perpendicular to the longitudinal direction of the column 910. The beam 920 is provided with a mechanism for adjusting the length of the beam (not shown), and the length of the beam 920 is adjusted according to the size of the member to be pulled out.

The bearing fixing member 60a is provided with a notch portion 62a having a shape notched from the outer periphery 61a of the bearing fixing member 60a toward the inside of the bearing fixing member 60a. When the claw 931 of the extraction tool is engaged with the end face of the bearing 50a on the rotor 10 side, the two arms 930 of the extraction tool are bent with respect to the beam 920, so that the claw 931 at the tip of the arm 930 is fixed to the bearing. The claw 931 enters the space formed by the notch 62a of the member 60a and the end face of the bearing 50a on the rotor 10 side, and the claw 931 engages with the end face of the bearing 50a on the rotor 10 side. As described above, even if the gap between the rotor 10 and the bearing 50a in the central axial direction is narrow, the notch portion 62a is provided in the shaft fixing member 60a, so that a space for engaging the tool is formed and the extraction tool is drawn. The workability of the work of hanging the claw 931 on the bearing 50a is improved, and the work efficiency of the work of removing the bearing 50a can be improved.

After the claw 931 of the extraction tool is engaged with the bearing 50a, the support 910 is rotated by the handle 940 of the extraction tool, so that the beam 920 and the arm 930 move in the direction away from the rotor 10, and the arm 930 is accompanied by the movement. The bearing 50a to which the claw 931 at the tip is engaged also moves on the shaft 20 in a direction away from the rotor 10, and the bearing 50a is pulled out from the shaft 20 and removed.

The distance L1 between the notch end 623a, which is the closest point to the central axis AX of the notch portion 62a, and the central axis AX is smaller than the radius L2 of the outer circumference 53 of the bearing 50a. As a result, a part of the end surface of the bearing 50a on the bearing fixing member 60a side is exposed in the space formed by the notch portion 62a. This creates a surface area on the end surface of the bearing 50a on the bearing fixing member 60a side on which the claw 931 of the extraction tool can be engaged, and makes it easy to engage the claw 931 of the extraction tool on the bearing 50a. This makes it possible to improve the work efficiency of the bearing 50a removal work.

The distance L1 between the notch end 623a, which is the closest point to the central axis AX of the notch portion 62a, and the central axis AX is larger than the radius L3 of the shaft through hole 63. As a result, since the notch portion 62a does not reach the shaft through hole 63, the shaft through hole 63 is a hole closed in the circumferential direction, and if the shaft 20 is passed through the shaft through hole 63, the bearing fixing member 60a will be formed. The bearing fixing member 60a does not fall from the shaft 20 during the bearing removal work because the shaft 20 does not come off from the side of the shaft 20. Therefore, the work efficiency of the bearing removal work can be improved.

The notch width H of the notch portion 62a of the bearing fixing member 60a is longer than the width of the claw 931 of the drawing tool determined by the size of the bearing 50a.

Further, the number of notches 62a provided in the bearing fixing member 60a is 2. The number of claws 631 of a general drawing tool is often 2, and by reducing the number of notch portions 62a to the minimum necessary 2, the contact area of the pressing surface 67 where the bearing 50a and the bearing fixing member 60a come into contact can be reduced. The number can be increased, and the load per unit area applied to the bearing 50a can be distributed. This makes it possible to improve the reliability of the bearing 50a and the bearing fixing member 60a. Further, by minimizing the number of the notch portions 62a, the processing cost required for processing the notch portions 62a can be suppressed.

In the first embodiment of the present disclosure, as described above, the stator structure 30 having the stator 31 and the frame 32 which is the stator support portion for supporting the stator 31 and the bracket attached to the stator structure 30. 40a, a bearing 50a arranged on the bracket 40a, a shaft 20 rotatably supported by the bearing 50a, a rotor 10 fixed to the shaft 20, and arranged between the bearing 50a and the rotor 10. A shaft through hole 63 attached to the bracket 40a and closed in the circumferential direction through which the shaft 20 passes is provided, and a bearing fixing member 60a for pressing and fixing the bearing 50a to the bracket 40a is provided, and the bearing fixing member 60a is a bearing fixing member 60a. A notch 62a having a shape notched from the outer periphery 61a of the bearing toward the inside of the bearing fixing member 60a is provided, and the portion of the notch 62a closest to the central axis AX of the shaft 20 and the central axis AX are radially located. The distance L1 is smaller than the radius L2 of the outer peripheral 53 of the bearing 50a, and is larger than the radial distance L3 between the portion farthest from the central axis AX on the inner circumference of the shaft through hole 63 and the central axis AX. The work efficiency of the bearing removal work can be improved without the bearing fixing member 60a falling from the shaft.

Further, since the number of notched portions 62a provided in the bearing fixing member 60a is 2, the contact area between the bearing 50a and the bearing fixing member 60a is large, and the load per unit area applied to the bearing 50a can be dispersed. It is possible to improve the reliability of the bearing 50a and the bearing fixing member 60a. Further, the processing cost required for processing the notch portion 62a can be minimized.

Embodiment 2.
FIG. 4 is an external view of the bearing fixing member according to the second embodiment of the present disclosure. In FIG. 4, those having the same reference numerals as those in FIG. 2 indicate the same or corresponding configurations, and the description thereof will be omitted. FIG. 4 shows the appearance seen from the direction of the bearing 50a in the central axis direction when the bearing fixing member 60b is arranged in the rotary electric machine. The bearing fixing member 60a according to the first embodiment of the present disclosure has four notches 62a provided in the bearing fixing member 60b, and the number of notches 62a is such that the bearing fixing member 60b is used as a bracket. The difference is that the number is the same as the number of the plurality of screw holes 64 provided in the bearing fixing member 60b for mounting.

In the bearing fixing member 60b of FIG. 4, four screw holes 64 and four notches 62a having the same number of screw holes 64 are alternately spaced in the circumferential direction at equal intervals in the circumferential direction about the central axis AX. Is placed in.

The force with which the mounting screw presses the bearing fixing member 60b in the screw hole 64 in the direction of the bracket 40a transmits the structure of the bearing fixing member 60b, and the bearing fixing member 60b presses the bearing 50a on the pressing surface 67 in the circumferential direction of the load. Is the distribution of. In the present embodiment in which the number of notches 62a and the number of screw holes 64 are the same, the bearing fixing member 60b is pressed on the pressing surface 67 as compared with the case where the number of notches 62a and the number of screw holes 64 are different. The circumferential distribution of the load holding the bearing 50a does not differ between the adjacent screw holes 64, and the variation in the circumferential distribution of the load can be suppressed.

Even in the rotary electric machine of the second embodiment provided with such a bearing fixing member 60b, the shaft through hole 63 is closed in the circumferential direction as in the first embodiment, and the bearing fixing member 60b is the shaft 20. The bearing fixing member 60b does not fall from the shaft 20 during the bearing removal work because it does not come off from the shaft 20 sideways. Further, the notch 62a provided in the bearing fixing member 60b makes it easy to engage the claw 931 of the extraction tool with the bearing 50a, and the work efficiency of the removal work of the bearing 50a can be improved.

Further, since the bearing fixing member 60b is provided with a plurality of screw holes 64 for attaching to the bracket 40a and the number of notched portions 62a is the same as the number of the screw holes 64, the bearing fixing member 60b is a bearing. The variation in the distribution of the load that presses 50a in the circumferential direction can be suppressed, the bearings can be pressed evenly, and the quality of the rotary electric machine 100a can be improved.

Embodiment 3.
FIG. 5 is an external view of the bearing fixing member according to the third embodiment of the present disclosure. In FIG. 5, those having the same reference numerals as those in FIG. 2 indicate the same or corresponding configurations, and the description thereof will be omitted. FIG. 5 shows the appearance of the bearing fixing member 60c as seen from the direction of the bearing 50a in the central axis direction when the bearing fixing member 60c is arranged in the rotary electric machine. The bearing fixing member 60a according to the first embodiment of the present disclosure has a notch portion 62c outside a polygon formed by a plurality of straight lines connecting the centers of screw holes 64 adjacent to each other in the circumferential direction. That is different. Further, the number of notched portions 62c provided in the bearing fixing member 60c is set to 4.

In FIG. 5, a screw hole reference line 641 which is a straight line connecting the centers of adjacent screw holes 64 in the circumferential direction is shown by a dotted line, and is a polygon composed of a plurality of screw hole reference lines 641. A reference line polygon 642 is shown. In FIG. 5, the bearing fixing member 60c is provided with four screw holes 64, and the reference line polygon 642 is a quadrangle.

The notch portion 62c is located outside the reference line polygon 642 when the bearing fixing member 60c is viewed from the bearing 50a side in the direction in which the central axis AX extends. In other words, the surface constituting the notch portion 62c is on the outside of the reference line polygon 642. That is, the two notch side surfaces 621c and the notch end surface 622c constituting the notch portion 62c are outside the reference line polygon 642.

The cutout portion 62c is located on the outside of the reference line polygon 642 composed of a plurality of screw hole reference lines 641 connecting the centers of the screw holes 64 adjacent to each other in the circumferential direction, so that the cutout portion 62c is formed. The space to be formed does not intersect the inside of the reference line polygon 642. That is, the portion of the bearing fixing member 60c along the screw hole reference line 641 between the adjacent screw holes 64 has a structure in which the material constituting the bearing fixing member 60c is filled without chipping. As a result, the rigidity between the screw holes 64 adjacent to each other in the circumferential direction in the bearing fixing member 60c is increased, the strain of the bearing fixing member 60c is small, and the force applied from the mounting screws is reliably pressed by the plurality of screw holes 64. The bearing 50a can be uniformly and totally pressed by being transmitted to the entire surface 67, and the variation in the distribution of the load in which the bearing fixing member 60c presses the bearing 50a in the circumferential direction can be suppressed.

Even in the rotary electric machine of the third embodiment provided with such a bearing fixing member 60c, the shaft through hole 63 is closed in the circumferential direction as in the first embodiment, and the bearing fixing member 60c is the shaft 20. The bearing fixing member 60c does not fall from the shaft 20 during the bearing removal work because it does not come off from the shaft 20 sideways. Further, the notch 62c provided in the bearing fixing member 60c makes it easy to engage the claw 931 of the extraction tool with the bearing 50a, and the work efficiency of the removal work of the bearing 50a can be improved.

Further, the bearing fixing member 60c is provided with three or more screw holes 64 for attaching to the bracket 40a, and the notch portion 62c is viewed from the bearing 50a side in the direction in which the central axis AX extends in the bearing fixing member 60c. Since it is outside the reference line polygon 642 composed of the reference line 641 between screw holes, which is a plurality of straight lines connecting the centers of the screw holes 64 adjacent to each other in the circumferential direction, the circumferential direction in the bearing fixing member 60c. The rigidity between the adjacent screw holes 64 is increased, the bearing 50a can be pressed evenly as a whole, the variation in the distribution of the load in which the bearing fixing member 60c presses the bearing 50a in the circumferential direction is suppressed, and the rotary electric machine is used. The quality of 100a can be improved.

Embodiment 4.
FIG. 8 is a cross-sectional view showing a rotary electric machine according to the fourth embodiment of the present disclosure. FIG. 9 is an external view of the bearing fixing member according to the fourth embodiment of the present disclosure. FIG. 10 is a schematic view of the bearing removing operation according to the fourth embodiment of the present disclosure. In FIGS. 8 and 10, the upper side of the central axis AX shows the cross section, and the lower side of the central axis AX shows the appearance. In FIGS. 8, 9, and 10, those having the same reference numerals as those in FIGS. 1, 2, and 3 indicate the same or corresponding configurations, and the description thereof will be omitted. With respect to the bearing fixing member 60a according to the first embodiment of the present disclosure, the bearing fixing member 60d is not provided with a notch, and the radius L4 of the outer circumference 61d of the bearing fixing member 60d is the radius of the outer circumference 13 of the rotor 10. The difference is that the protrusion 68 is provided, which is larger than L5 and the radial distance of the bearing fixing member 60d from the central axis is larger than the radius L5 of the outer circumference 13 of the rotor 10. ing.

In FIG. 8, the bearing fixing member 60d of the fourth embodiment of the present disclosure is arranged between the bearing 50a and the rotor 10 in the central axial direction and attached to the bracket 40a, as in the first embodiment. .. The bearing fixing member 60d holds the bearing 50a against the bracket 40a and fixes it. The shaft 20 passes through the shaft through hole 63 provided in the bearing fixing member 60d. The radius L4 of the outer circumference 61d of the bearing fixing member 60d is larger than the radius L5 of the outer circumference 13 of the rotor 10, unlike the first embodiment.

FIG. 9 shows the appearance of the bearing fixing member 60d as seen from the direction of the bearing 50a in the central axis direction when the bearing fixing member 60d is arranged in the rotary electric machine 100d. In FIG. 9, the outer circumference 13 of the rotor 10 is shown by a dotted line. In FIG. 9, the bearing fixing member 60d does not have a shape notched inward from the outer circumference, but has a disk-like shape. The radius L4 of the outer circumference 61d of the bearing fixing member 60d is larger than the radius L5 of the outer circumference 13 of the rotor 10. That is, a protruding portion 68 is provided, which is a portion where the radial distance of the shaft 20 of the bearing fixing member 60d from the central axis AX is larger than the radius L5 of the outer circumference 13 of the rotor 10. In FIG. 9, the bearing fixing member 60d is a protruding portion 68 having a disk-shaped outer circumference covering the entire circumference and a radial distance from the central axis AX larger than the radius L5 of the outer circumference of the rotor 10. Further, the bearing fixing member 60d is provided with a shaft through hole 63 and four screw holes 64. Similar to the first embodiment, the shaft through hole 63 is closed in the circumferential direction, the bearing fixing member 60d does not come off from the shaft 20 on the side of the shaft 20, and the bearing fixing member 60d is in the middle of the bearing removal work. It does not fall from the shaft 20.

In FIG. 10, the bearing fixing member 60d is arranged between the bearing 50a and the rotor 10 in the central axial direction, and the shaft 20 passes through the shaft through hole 63 of the bearing fixing member 60d. The protruding portion 68, which is a portion where the radial distance from the central axis AX is larger than the radius L5 of the outer peripheral portion 13 of the rotor 10, protrudes outward from the rotor 10 in the radial direction. Since the protruding portion 68 protrudes radially outward from the rotor 10, even if the gap between the bearing fixing member 60d and the rotor 10 is narrow, the end face of the protruding portion 68 on the rotor 10 side is the radial direction of the rotor 10. It is exposed in the outer space.

In FIG. 10, a drawing tool is attached to the shaft end in the direction in which the bearing 50a of the shaft 20 is attached.

In the fourth embodiment of the present disclosure, in the work of pulling out the bearing 50a from the shaft 20 using the pulling tool, the claw 931 of the pulling tool engages with the end face of the protrusion 68 of the bearing fixing member 60d on the rotor 10 side. Let me. The pulling force from the pulling tool is transmitted from the engaged protrusion 68 to the bearing 50a via the bearing fixing member 60d, and the bearing 50a is pulled out and removed together with the bearing fixing member 60d. When the claw 931 of the extraction tool is engaged with the protrusion 68, the claw 931 at the tip of the arm 930 forms the end surface of the bearing fixing member 60a on the rotor 10 side of the protrusion 68 and the outer peripheral surface of the rotor 10. Entering the space, the claw 931 engages with the end face of the protrusion 68 on the rotor 10 side. As described above, even if the gap between the rotor 10 and the bearing 50a in the central axial direction is narrow, the protrusion 68 is provided on the shaft fixing member 60d, so that a space for engaging the tool is formed, and the extraction tool can be used. The workability of the work of hanging the claw 931 is improved, and the work efficiency of the work of removing the bearing 50a can be improved.

After the claw 931 of the extraction tool is engaged with the bearing fixing member 60d, the column 910 is rotated by the handle 940 of the extraction tool, so that the beam 920 and the arm 930 move in the direction away from the rotor 10 in the central axial direction. Along with this, the bearing fixing member 60d on which the claw 931 at the tip of the arm 930 is engaged and the bearing 50a adjacent to the bearing fixing member 60d move in a direction away from the rotor 10 in the central axial direction with respect to the shaft 20. The bearing 50a is pulled out from the shaft 20 and removed.

In the fourth embodiment of the present disclosure, as described above, the stator structure 30 having the stator 31 and the frame 32 which is the stator support portion for supporting the stator 31 and the bracket attached to the stator structure 30. 40a, a bearing 50a arranged on the bracket 40a, a shaft 20 rotatably supported by the bearing 50a, a rotor 10 fixed to the shaft 20, and arranged between the bearing 50a and the rotor 10. A shaft through hole 63 attached to the bracket 40a and closed in the circumferential direction through which the shaft 20 passes is provided, and a bearing fixing member 60d for pressing and fixing the bearing 50a to the bracket 40a is provided. The bearing fixing member 60d is a bearing fixing member. Since the protrusion 68 is provided so that the radial distance of the shaft 20 of the 60d from the central axis AX is larger than the radius L5 of the outer circumference of the rotor 10, the bearing fixing member 60d falls from the shaft 20. It is possible to improve the work efficiency of the bearing removal work.

Further, it is not necessary to provide a notch in the bearing fixing member 60d, and the contact area of the pressing surface 67 in which the bearing 50a and the bearing fixing member 60d come into contact increases, so that the load per unit area applied to the bearing 50a is increased. It can be dispersed and the reliability of the bearing 50a and the bearing fixing member 60d can be improved. Further, it is not necessary to process the notch portion, and the processing cost can be suppressed.

In the fourth embodiment, the outer shape of the bearing fixing member 60d is a disk shape, and the radial distance from the central axis AX over the entire circumference of the disk shape is from the radius L5 of the outer circumference of the rotor 10. Although described in the example of the large protrusion 68, a part of the outer circumference may be a protrusion 68 whose radial distance from the central axis is larger than the radius L5 of the outer circumference of the rotor 10. .. When a part of the outer peripheral portion is the protruding portion 68, the mass of the bearing fixing member 60d is smaller than that when the outer peripheral portion is the protruding portion 68 over the entire circumference, and the weight of the rotary electric machine 100d is reduced. Become. When the outer shape of the bearing fixing member 60d is a disk shape and the outer circumference of the disk shape is a protrusion 68 over the entire circumference, the outer shape of the bearing fixing member 60d can be easily processed, the processing cost can be suppressed, and production can be performed. It is possible to improve the sex.

In each embodiment of the present disclosure, the example in which the stator structure 30 is composed of the stator 31 and the frame 32 has been described, but the stator structure 30 is composed of the stator 31 and the resin that molds the stator 31. The stator 31 may be supported by the molded resin, and the bracket 40a may be attached to the molded resin. Further, the stator structure 30 is composed of only the stator 31, and the bracket 40a may be directly attached to the stator 31. When the stator structure 30 is composed of only the stator 31, the stator 31 is supported by the stator 31 being directly fitted to a device or the like in which a rotary electric machine is used, and the stator 31 is a stator support portion. Also serves as.

In each embodiment of the present disclosure, the rotary electric machine has been described as an example of an induction motor, but it may be a servo motor having a magnet in the rotor, a reluctance motor driven by a reluctance torque, or the like.

In each embodiment of the present disclosure, the outer shape of the

bearing fixing members

60a, 60b, 60c, 60d has a disk-like shape having an outer circumference which is an arc centered on the central axis AX when viewed from the central axis AX direction. As described by example, in the bearing fixing member, the distance between the part farthest from the central axis AX on the outer circumference and the central axis AX is larger than the radius L2 of the outer circumference 53 of the bearing 50a, and the bearing 50a is pressed by the bracket 40a to form the bearing. As long as the fixing member has a shape that can be attached to the bracket 40a, the outer circumference may be a polygonal plate shape when viewed from the central axis direction. When the outer shape of the bearing fixing member when viewed from the central axis direction is arcuate, deformation distortion on the outer circumference of the bearing fixing member is suppressed, and variation in the circumferential direction of the force distribution of the bearing fixing member holding the bearing 50a is suppressed. be able to.

In each embodiment of the present disclosure, the bearing 50a has been described as an example of a bearing, but a slide bearing or the like may be used.

In each of the embodiments of the present disclosure, the

bearing fixing members

60a, 60b, 60c, 60d are described in an example in which the

bearing fixing members

60a, 60b, 60c, 60d are installed only in one bearing 50a of the two bearings and not in the other bearing 50b, but both are described. It may be installed in the

bearings

50a and 50b of the above.

It should be noted that, within the scope of the disclosure, the present disclosure can be freely combined with each embodiment, and each embodiment can be appropriately modified or omitted.

10 rotor, 11 rotor core, 12 end ring, 13 rotor outer circumference, 20 shaft, 21 shaft end face, 30 stator structure, 31 stator, 32 frame, 40a, 40b bracket, 50a, 50b bearing, 53 bearing outer circumference , 60a, 60b, 60c, 60d Bearing fixing member, 61a, 61d Bearing fixing member outer circumference, 62a, 62c Notch, 63 Shaft through hole, 64 Screw hole, 66 Bearing fitting hole, 67 Pressing surface, 68 Protruding part, 100a, 100d rotary electric machine, 211 center hole, 621a, 621c notch side surface, 622a, 622c notch end surface, 623a, 623c notch end, 641 screw hole reference line, 642 reference line polygon, 661 inner peripheral surface, 672 Contact avoidance step, 910 support, 920 beam, 930 arm, 931 claw, 940 handle, AX central axis

Claims

A stator structure having a stator and a stator support portion that supports the stator,
The bracket attached to the stator structure and
The bearings placed on the bracket and
A shaft rotatably supported by the bearing and
The rotor fixed to the shaft and
A bearing fixing member which is arranged between the bearing and the rotor and attached to the bracket, has a shaft through hole closed in the circumferential direction through which the shaft passes, and presses and fixes the bearing to the bracket. Prepare,
The bearing fixing member is provided with a notch portion having a shape notched from the outer periphery of the bearing fixing member toward the inside of the bearing fixing member.
The radial distance between the notch portion closest to the central axis of the shaft and the central axis is smaller than the radius of the outer circumference of the bearing and is from the central axis on the inner circumference of the shaft through hole. A rotary electric machine characterized in that it is larger than the radial distance between the farthest point and the central axis.
The bearing fixing member is provided with a plurality of screw holes for attaching to the bracket.
The rotary electric machine according to claim 1, wherein the number of the notches is the same as the number of the plurality of screw holes.
The rotary electric machine according to claim 1, wherein the number of the cutout portions is 2.
The bearing fixing member is provided with three or more screw holes for attaching to the bracket.
The notch is a polygonal shape formed by a plurality of straight lines connecting the centers of the screw holes adjacent to each other in the circumferential direction when the bearing fixing member is viewed from the bearing side in the direction in which the central axis extends. The rotary electric machine according to any one of claims 1 to 3, wherein the rotary electric machine is located on the outside.
A stator structure having a stator and a stator support portion that supports the stator,
The bracket attached to the stator structure and
The bearings placed on the bracket and
A shaft rotatably supported by the bearing and
The rotor fixed to the shaft and
A bearing fixing member which is arranged between the bearing and the rotor and attached to the bracket, has a shaft through hole closed in the circumferential direction through which the shaft passes, and presses and fixes the bearing to the bracket. Prepare,
The bearing fixing member is provided with a protruding portion in which the distance of the bearing fixing member in the radial direction from the central axis of the shaft is larger than the radius of the outer circumference of the rotor. ..