JP2003145409A - Super finishing method and device thereof - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a super finishing device simplified in the structure thereof and capable of finishing with excellent accuracy and roughness at a high working efficiency similarly with a case of super finishing a part to be super finished and having a small curvature. SOLUTION: A grinding wheel holder 3 for holding a grinding wheel 4 is fitted to one end of a rotary shaft 2a of a spindle device 2 possible to move on a base 1 in the x-axis direction, and a disk-like eccentric cam 5 deviated in relation to the rotary shaft 2 is fitted to the other end thereof. Regulating members 6a and 6b are arranged in both sides of the eccentric cam 5, and the regulating member 6a is fixed to the base 1 so that the regulating member 6a abuts on the eccentric cam 5, and the regulating member 6b is energized by a spring member (not expressed in a figure) so that the regulating member 6b is pushed to the eccentric cam 5. When the rotary shaft 2 is rotated at an angle in the condition that the eccentric cam 5 is made to abut on the regulating member 6a and energized by the regulating member 6b, the grinding wheel 4 swings around the rotary shaft 2a, while moving in the x-axis direction.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a superfinishing method and apparatus for a curved surface forming portion of a workpiece.

[0002]

2. Description of the Related Art Conventionally, as a method of superfinishing an outer surface of a drum-shaped workpiece such as a roller of a self-aligning roller bearing, a method for cutting the outer surface of the workpiece has been used. There is one that performs superfinishing of the outer surface of a workpiece by swinging a grindstone around a center position corresponding to the center of curvature of the outer surface of the workpiece.

A device configuration for implementing this method will be specifically described with reference to FIG. FIG. 15 is a front view and a side view showing a main part configuration of a conventional superfinishing apparatus.

The conventional super-finishing device is shown in FIG.
As shown in (b), the column 20 standing upright
2 includes a base 201 that is supported so as to be able to move up and down.
The base 201 is provided with two rotary shafts 205 arranged at intervals from each other, and each rotary shaft 205 includes:
One end of the corresponding vertical link arm 203 is rotatably supported. Each vertical link arm 203
It is connected by two horizontal link arms 204. Each end of each horizontal link arm 204 is rotatably connected to the corresponding vertical link arm 203. Two grindstone holders 206 are connected to each horizontal link arm 204. The grindstone holders 206 are arranged at intervals from each other, and a pressure cylinder 207 is attached to each grindstone holder 206. Each pressurizing cylinder 207 allows the grindstone 208 to be pressed against the workpiece 212 (for example, the rollers of the self-aligning roller bearing).
Holds 08.

One end of the transmission member 209 is connected to one of the vertical link arms 203, and the other end of the transmission member 209 is connected to the drive arm 210 fixed to the output shaft of the drive motor 211. The rotation output of the drive motor 211 is transmitted to the transmission member 209 via the drive arm 210 and drives the transmission member 209. This transmission member 20
By the movement of 9, the vertical link arm 203 on one side swings around the rotary shaft 205 having one end thereof supported. Each horizontal link arm 204 moves in conjunction with the swing of the one vertical link arm 203 to swing the other vertical link arm 203 about the corresponding rotary shaft 205. Then, each grindstone holder 206 has the workpiece 2
The outer surface of 12 rocks around a position corresponding to the center of curvature R. As a result, the grindstone 208 held by the pressurizing cylinder 207 of the grindstone holder 206 is moved to the workpiece 21.
It oscillates along an arc having a curvature equal to the curvature R of the outer surface of No. 2. At this time, the grindstone 208 is pressed against the workpiece 212 with a predetermined pressure by the pressure cylinder 207.

On the other hand, when superfinishing is performed on a portion having a small curvature such as a raceway groove of an inner ring of a ball bearing, the apparatus shown in FIG. 16 is used. FIG. 16 is a front sectional view, a side sectional view, and a sectional view showing a periphery of a tip of a grindstone showing a main part configuration of an apparatus for superfinishing a portion having a small curvature in a conventional workpiece.

This apparatus, as shown in FIGS. 16A and 16B, has a grindstone holder 221 for holding a grindstone 222.
Equipped with. In the grindstone holder 221, a pressurizing piston 224 of a pressurizing mechanism for pressing the grindstone 222 against a finishing target portion (for example, a raceway groove of an inner ring of a ball bearing) of the workpiece 220 having a small curvature R is incorporated. As shown in FIG. 16A, the head portion of the pressurizing piston 224 is
A V-shaped groove is formed. An O-ring 223 is incorporated at the tip of the grindstone holder 221. The grindstone holder 221 is swung around the swing center Os.

When performing superfinishing, the grindstone holder 221
Is positioned so that the swing center Os coincides with the center of the curvature R of the portion to be finished of the workpiece 222. Then, the grindstone 221 is swung at the swing radius R about the swing center Os while the grindstone 220 is pressed against the finishing target portion of the workpiece 220. Thereby, the workpiece 220
The part to be finished will be super-finished.

[0009]

In the case of a device (shown in FIG. 16) for superfinishing a portion of a workpiece having a small curvature, such as a raceway groove of an inner ring of a ball bearing, the structure is simple and the swing radius R is large. Since the (curvature of the work piece) is small, the size can be reduced, and since the rocking speed is usually as high as about 1000 times per minute, the processing efficiency of superfinishing can be increased. Further, by adopting a biaxial structure (balance weight structure) and moving them in opposite directions, it is possible to balance vibrationally. Therefore, it is possible to obtain a finish with good processing accuracy and roughness. In addition, the vibration as a device is small, and processing devices in the vicinity (for example,
It is possible to reduce the effect of vibration on the grinder.

However, when superfinishing a portion having a large curvature R such as the outer surface of a spherical roller, the size adjustment range becomes large for the large curvature R, and the apparatus itself becomes large. In addition, the mass of the grindstone holder increases,
Further, due to the synergistic effect that the curvature R is large, the vibration due to the centrifugal force becomes large.

Further, in the case of a device (shown in FIG. 15) for superfinishing a finishing target portion having a large curvature R, the structure is complicated, the mass of the swinging mechanism as a whole is large, and it is possible to balance vibrationally. Therefore, it is necessary to suppress the rocking speed to about 200 times per minute, resulting in low machining efficiency. In addition, it is impossible to obtain a finish with good accuracy and roughness.

An object of the present invention is to obtain a finish with a high machining efficiency and a good precision and roughness, which can simplify the structure and, like the superfinishing of a portion to be superfinished having a small curvature. It is an object of the present invention to provide a superfinishing apparatus and a method capable of performing the same.

[0013]

According to the present invention, in a method of superfinishing a curved surface forming portion of a work, a rotary shaft supported on a base so as to be movable in a first direction orthogonal to an axis. A grindstone is mounted at a predetermined distance in a second direction orthogonal to the axis of the rotating shaft, an eccentric cam member that is eccentric to the rotating shaft is coaxially mounted, and the regulating member is in contact with the eccentric cam member. And an urging member for urging the eccentric cam member toward the restricting member in the first direction, the eccentric cam being in contact with the restricting member, and the rotary shaft urging the rotating shaft. Characterized in that the grindstone is swung around the rotating shaft while moving the rotating shaft in the first direction by rotationally driving the rotating shaft angularly while being biased by a member. To do.

Further, according to the present invention, in a superfinishing apparatus for a curved surface forming portion of a workpiece, a base and a first unit orthogonal to an axis line.
A rotation axis supported so as to be movable on the base in the direction of, and a second axis orthogonal to the axis of the rotation axis.
With a grindstone attached at a predetermined distance in the direction of
An eccentric cam member that is coaxially attached to the rotation shaft and is eccentric to the rotation shaft, a regulation member that is provided on the base and is in contact with the eccentric cam member, and a regulation member that is provided on the base. A urging member that urges the eccentric cam member toward the regulating member in the first direction, and a drive mechanism that angularly rotationally drives the rotation shaft.

According to the present invention, the eccentric cam is brought into contact with the regulating member, and the rotary shaft is angularly driven while the rotary shaft is biased by the biasing member, thereby moving the rotary shaft in the predetermined direction. While swinging the whetstone around the axis of rotation,
By appropriately setting the linear distance from the axis of the rotating shaft to the tip position of the grindstone and the eccentric amount of the eccentric cam member, the tip of the grindstone is swung along the trajectory of the radius of curvature corresponding to the superfinished part of the workpiece. It is possible to let Further, this swing mechanism can be realized with a simplified structure. Furthermore, since the mass of the entire swing mechanism can be reduced, it is possible to increase the swing speed and improve the machining efficiency.

[0016]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings.

First, the basic structure of an apparatus for realizing the superfinishing method according to the present invention will be described with reference to FIGS. 1 to 4. FIG. 1 is a side view and a front view showing a basic configuration of an apparatus for realizing a superfinishing method according to the present invention, and FIG. 2 is a view showing a locus drawn by a whetstone tip position P in FIG. 1 according to rotation of a rotary shaft. FIG. 3 shows the amount of eccentricity e of the eccentric cam and the radius of curvature (superfinishing radius) R0 when the linear distance r0 from the center of the rotating shaft to the grindstone tip position P in FIG. 1 is used as a variable.
FIG. 4 is a diagram showing the relationship with the eccentric cam eccentricity e of FIG. 1 as a variable, and the straight line distance r0 from the center of the rotary shaft to the grindstone tip position P and the radius of curvature (superfinishing radius) R0 It is a figure which shows the relationship of.

As shown in FIG. 1, the basic construction of the superfinishing apparatus comprises a base 1 provided with a guide rail portion 1a. The spindle device 2 is mounted on the base 1,
The spindle device 2 is configured to be movable in the x-axis direction while being guided by the guide rail portion 1a (FIG. 1).
(See (b)). Spindle device 2 is guide rail 1
It has a rotary shaft 2a extending in a direction orthogonal to the guide direction of a, and a grindstone holder 3 is attached to one end of the rotary shaft 2a. The grindstone holder 3 is composed of a hook-shaped member, and the grindstone 4 is attached to the tip 3a thereof.
An eccentric cam 5 and a pulley 7 are attached to the other end of the rotary shaft 2a. The eccentric cam 5 is composed of a disc eccentrically attached to the rotating shaft 2a. A timing belt 8 for transmitting a driving force of a driving motor (not shown) is wound around the pulley 7. Restricting members 6a and 6b are arranged on both sides of the eccentric cam 5, respectively.
One restricting member 6a is fixed to the base 1 and is positioned so as to contact the side surface of the eccentric cam 5. The other regulating member 6b is attached to the base 1 so as to be movable in the x-axis direction, and is biased by a spring member (not shown) so as to be pressed against the side surface of the eccentric cam 5.

Here, the drive motor shown in FIG.
Consider a case where the rotary shaft 2a is angularly rotated in the direction of the arrow indicated by. First, when the rotating shaft 2a is rotationally driven in one direction (clockwise in FIG. 1B) by the drive motor, the eccentric cam 5 is rotated as the rotating shaft 2a rotates. At this time, the eccentric cam 5 is fixed to the fixed side regulating member 6
Since the eccentric cam 5 rotates while contacting a, the regulating member 6b is moved in the x-axis direction while resisting the biasing force of the spring member. As a result, the rotating shaft 2a is moved in the x-axis direction according to the rotation angle θ while rotating. Further, the rotating shaft 2a is driven by the drive motor.
Is angularly driven in the other direction (counterclockwise in FIG. 1B), the rotary shaft 2a is also moved in the x-axis direction according to the rotation angle θ while rotating.

When the rotary shaft 2a rotates while moving in the x-axis direction, the grindstone holder 3 attached to the rotary shaft 2a rotates around the rotary shaft 2a while moving in the x-axis direction. At this time, the locus P (x, y) drawn by the tip end position P of the grindstone 4 of the grindstone holder 3 is expressed by the following equation (1) when viewed from the origin O of the xy coordinate system as shown in FIG. It will be the ellipse represented.

{X / (r0 + e)} ² + (y / r0) ² = 1 (1) r0: linear distance from the center Os of the rotary shaft 2a to the tip position P of the grindstone e: rotation of the eccentric cam 5 Eccentricity Oc with respect to the shaft 2a: Center of the eccentric cam 5 (moves according to the rotation angle θ of the rotating shaft 2a) Next, the relationship between the eccentricity e of the eccentric cam 5, the distance r0, and the radius of curvature R0 will be considered. The radius of curvature R0 is a radius of curvature when x = 0 in the xy coordinate system, and is used for the superfinishing target portion of the workpiece held at a predetermined position.
The tip end position P of represents the radius of curvature of the trajectory to be drawn. This radius of curvature R0 is expressed by the following equation (2).

R0 = (r0 + e) ² / r0 = (1 + e / r0) ² · r0 (2) First, the eccentricity e of the eccentric cam 5 is set to a fixed value, and the distance r
Consider the relationship between these and the radius of curvature R0 when 0 is a variable. Here, the relationship between the distance r0 and the eccentricity e is r0 =
Assuming that it is represented by γ · e, the ratio R0 / e between the radius of curvature R0 and the eccentricity e is expressed by the following expression (3) from the above expression (2).

R0 / e = (1 + e / r0) ² · (r0 / e) = (1 + 1 / γ) ² · γ = 2 + γ + 1 / γ (3) where R0 / e when γ <1 The relationship with γ is shown in FIG. As can be seen from FIG. 3, although it is nonlinear,
When γ = 0.3 to 0.05, R0 / e is 5.6.
.About.22.0, and a value in the range of about 4 times is obtained. For example, if e = 15 mm and γ = 0.3, r0 =
15 × 0.3 = 4.5 mm, R0 = 5.6 × 15 = 84
mm. When γ = 0.05, r0 = 15 ×
0.05 = 0.75 mm, R0 = 22.0 × 15 = 33
It becomes 0 mm.

The amount of movement xs by which the tip position P of the grindstone 4 moves in the x-axis direction in accordance with the rotation angle θ of the rotary shaft 2a is
It is expressed by the following equation (4).

Xs = (e + r0) sin θ (4) From the above equation (4), the movement amount xs in each of the above cases
Is 19.5 sin θ to 15.75 sin θ, and for example, when the movement amount xs = 3 mm, the rotation angle θ = 0.032
It becomes (pi) (rad) -0.041 (pi) (rad).

Consider the relationship between the radius of curvature R0 and the above r0 when the distance r0 is a fixed value and the eccentric amount e of the eccentric cam 5 is a variable. According to the above equation (2), the relationship shown in FIG. 4 is obtained between the ratio R0 / r0 of the radius of curvature R0 and the distance r0 and the ratio e / r0 of the eccentricity e and the distance r0. can get. As can be seen from FIG. 4, linearly e / r0
= 0.4 to 1.5, R0 / r0 = 2.0 to 6.2
And a value in the range of about 3 times is obtained. For example, r0 =
35 mm, when e / r0 = 0.4, e = 35
× 0.4 = 14 mm, R0 = 35 × 2.0 = 70 mm. When e / r0 = 1.5, e = 35 × 1.
5 = 53.5 mm and R0 = 35 × 6.2 = 218 mm.

The amount of movement xs in each of the above cases is
According to the equation (4), 49sinθ to 88.5sinθ, and for example, when the moving amount xs = 2 mm, the rotation angle θ
= 0.018π (rad) to 0.007π (rad).

Thus, the linear distance r0 from the center Os of the rotary shaft 2a to the tip position P of the grindstone 4 and the eccentric cam 5
By properly setting the eccentricity e of the above, it becomes possible to swing the tip of the grindstone 4 along the trajectory of the radius of curvature corresponding to the superfinished portion of the workpiece within the range of the small rotation angle θ. Further, this swing mechanism can be realized with a simplified structure. Furthermore, since the mass of the entire swing mechanism can be reduced, it is possible to increase the swing speed and improve the machining efficiency. Therefore, according to the present method, it is possible to simplify the structure, and as in the case of superfinishing the superfinishing target portion having a small curvature, it is possible to obtain a finish with high machining efficiency and good precision and roughness. A super finishing device can be provided.

(First Embodiment) Next, a superfinishing apparatus according to a first embodiment of the present invention will be described with reference to FIGS. FIG. 5A is a top view showing the configuration of the superfinishing device according to the first embodiment of the present invention, and FIG.
5B is a vertical cross-sectional view taken along the line AA of FIG. 5A, FIG. 6A is a front view of the eccentric cam of FIG. 5, and FIG.
5 is a side view of the eccentric cam of FIG. 5, FIG. 6 (c) is a perspective view of the eccentric cam of FIG. 5, FIG. 7 (a) is a vertical sectional view showing the structure of the grindstone holder of FIG. 5, and FIG. FIG. 7A is a view seen from the arrow B, FIG. 8A is a front view of another configuration example of the tip portion of the grindstone holder, and FIG. 8B is a CC line of FIG. 8A. It is sectional drawing obtained along with.

The superfinishing device according to the present embodiment is based on the above-mentioned basic structure. However, in the present embodiment, the superfinishing device has a two-axis structure capable of canceling vibrations, and each shaft has one drive motor. It is configured to be driven by.

Specifically, as shown in FIG. 5, the superfinishing apparatus of this embodiment includes a base 11 placed on a supporting surface such as a floor. The base 11 has two sliders 1
2 and 13 are mounted so as to face each other.

The slider 12 has a plurality of linear guides 12a that slide along a pair of guide rails 14a and 14b provided on the upper surface of the base 11, and the plurality of linear guides 12a guide the pair of guide rails 14a and 14a. 1
It is configured to be movable on the base 11 while being guided by 4b. The slider 12 includes guide rails 14a, 1
A spindle 16 extending in a direction orthogonal to 4b is rotatably supported. At one end 16a of the spindle 16,
The link member 32 is attached, and the other end 16b is
The grindstone holder 20 is attached. The detailed configuration of the grindstone holder 20 will be described later.

The spindle 16 has an eccentric cam 18
Is attached. As shown in FIG. 6, the eccentric cam 18 is composed of a ring portion 18a and a cam portion 18b that is eccentric to the ring portion 18a and is continuous with the ring portion 18a. The cam portion 18b is a hole portion of the ring portion 18a. It consists of a disc with a cutout corresponding to. The eccentric cam 18 is fitted to the spindle 16 so that the ring portion 18a is coaxial with the spindle 16. As a result, the eccentric cam 1
The cam portion 18b of No. 8 is attached to the spindle 16 with its center eccentric to the center of the spindle 16 by an eccentric amount e.

As shown in FIG. 7, the grindstone holder 20 has a base portion 40 attached to the other end 16b of the spindle 16, and the base portion 40 has a pair of guides for guiding the holder portion 47. Rails 41 are provided.
The holder part 47 has a hook shape and its base part 4
A ball screw mechanism 42 and a pair of linear guides 46 slidably engaged with the respective guide rails 41 are provided at a portion facing 0. The ball screw mechanism 42 includes a screw shaft 44 and a nut portion 45 fixed to the holder portion 47.
The screw shaft 44 is rotationally driven by a drive motor 43 fixed to the base portion 40. Since the nut portion 45 moves along the screw shaft 44 with the rotational movement of the screw shaft 44, the holder portion 47 moves relatively to the base portion 40. A holding member 48 is attached to the tip portion 47a of the holder portion 47, and a grindstone 49 is held between the holding member 48 and the tip portion 47a. Whetstone 49
Indicates that the distance between the tip position and the center of the spindle 16 is r
Positioned to be 0. It is swung with a curvature R0 that matches the radius of curvature R of the workpiece 50 (e.g., corresponding to a spherical roller). Here, when superfinishing with the grindstone 49, the workpiece 50 is sandwiched between a pair of rollers 51 and positioned with respect to the tip of the grindstone 49, and the workpiece 51 is rotated by the rotation of the rollers 51. To be done.

By using the grindstone holder having such a structure, it becomes possible to press the grindstone 49 against the workpiece 50 with a predetermined pressing force by the relative movement of the holder portion 47. In addition, due to wear of the grindstone 49, etc.
When the tip position of 9 changes in the vertical direction with respect to the workpiece 50, the tip position of the grindstone 49 and the vertical position of the workpiece 50 can be adjusted.

The slider 13 is similar to the slider 12 in that
A pair of guide rails 15 provided on the upper surface of the base 11.
a plurality of linear guides 13a sliding along a and 15b
And is configured to be movable on the base 11 while being guided by the pair of guide rails 15a and 15b by the plurality of linear guides 13a. A spindle 17 extending in a direction orthogonal to the guide rails 15a and 15b is rotatably supported by the slider 13. The link member 33 is attached to one end 17a of the spindle 17, and the grindstone holder 21 is attached to the other end 17b. The grindstone holder 21 has the same structure as the grindstone holder 20 (see FIG. 7), and a description thereof will be omitted here.

Further, the spindle 17 has an eccentric cam 19
Is attached. The eccentric cam 19 is configured similarly to the eccentric cam 18, and has a ring portion 19a and a cam portion 19b.
And (see FIG. 6). As a result, the eccentric cam 19
The center of the cam portion 19b is attached to the spindle 17 so as to be eccentric with respect to the center of the spindle 17 by an eccentric amount e.

Between the slider 12 and the slider 13,
Two restricting members 23 and 24, which are rolling bearings, are provided, and the restricting members 23 and 24 are coaxially supported by the shaft 22. Each end of the shaft 22 is supported by support members 22a and 22b provided on the base 11, respectively. The restricting member 24 has an outer peripheral surface that abuts on the outer peripheral surface of the cam portion 18b of the eccentric cam 18 attached to the spindle 16.
The eccentric cam 19 is attached to the outer peripheral surface of the cam portion 19b.

The slider 12 is biased by the spring member 35 in the direction in which the cam portion 18b of the eccentric cam 18 is pressed against the regulating member 23. The spring member 35 is the base 1
It is held by a holding member 34 which is fixed to 1. Similarly, the slider 13 is biased by the spring member 37 in the direction in which the cam portion 19b of the eccentric cam 19 is pressed against the regulating member 24. The spring member 37 is held by a holding member 36 fixed to the base 11.

The link member 32 of the spindle 16 is shown in FIG.
As shown in (b), it is connected to the arm portion 28 b of the intermediate link 28 via the link member 30. The link member 33 of the spindle 17 is connected to the arm portion 28c of the intermediate link 28 via the link member 31.
The intermediate link 28 is provided with an arm portion 28a together with the arm portions 28b and 28c.
The arm portion 28b and the arm portion 28c project in opposite directions along the same straight line, and the arm portion 28a projects perpendicularly to the arm portion 28b. The intermediate link 28 is
It is supported by the axle box 29. The arm portion 28a of the intermediate link 28 is connected to one end of the link member 27, and the other end of the link member 27 is connected to the conversion member 26 for converting the rotational motion of the drive motor 25 into the swing motion. The conversion member 26 is fixed to the output shaft (not shown) of the drive motor 25, and the connection point of the conversion member 26 with the link member 27 is eccentric to the output shaft of the drive motor 25 by the eccentric amount E1. . This eccentricity E1 is determined by each spindle 1
The maximum value of the rotation angle θ of 6 and 17 is specified.

With such a link mechanism, the rotary motion of the drive motor 25 is converted into the swing motion of the spindles 16 and 17, and the spindles 16 and 17 are angularly rotated in opposite directions. For example, when the spindle 16 is angularly driven in one direction (clockwise in FIG. 5B), the eccentric cam 1 is rotated along with the rotation of the spindle 16.
8 is rotated. At this time, the eccentric cam 18 has the cam portion 1
Since 8b rotates while being in contact with the regulating member 23,
Rotation of the eccentric cam 18 causes the slider 12 to move to the spring member 3
It is moved along the guide rails 14a and 14b while resisting the urging force of No. 5. As a result, the spindle 16 rotates while being guided by the guide rail 14 according to the rotation angle θ.
It is moved in the guiding direction of a and 14b.

When the spindle 16 is rotationally driven in one direction, the spindle 17 is angularly driven in the other direction (counterclockwise). Also in this case, as in the case of the spindle 16, the rotation of the eccentric cam 19 causes the slider 13 to move along the guide rails 15a and 15b while resisting the biasing force of the spring member 37. As a result, the spindle 17 is moved in the guide direction of the guide rails 15a and 15b according to the rotation angle θ while rotating.

When the spindle 16 is rotationally driven in the other direction (counterclockwise direction), the spindle 17 is angularly driven in one direction (clockwise direction). Also in this case, similarly, the spindles 16 and 17 rotate while the guide rails 14a and 1a are rotated according to the rotation angle θ.
It will be moved in the guide direction of 4b, 15a, 15b.

When the spindles 16 and 17 are driven to rotate, the grindstone holders 20 and 21 attached to the spindles 16 and 17 are guided by the guide rails 14a, 14b and 15 respectively.
While moving in the guide direction of a, 15b, the spindle 16,
It will be rotated angularly around 17. At this time, the tip position of the grindstone 49 of the grindstone holders 20 and 21 is determined according to the linear distance r0 from the center of the spindles 16 and 17 to the tip position of the grindstones 20 and 21 and the eccentric amount e of the eccentric cams 16 and 17. It moves along an orbit with a radius of curvature. That is, the grindstone holders 20 and 21 can be swung so that the tip position of the grindstone 49 moves along the radius of curvature of the superfinishing target portion of the workpiece 50 held at a predetermined position.

Therefore, in the present embodiment, by simultaneously driving the two spindles 16 and 17 in opposite directions, vibrational balance can be achieved and the rocking speed can be increased.

In this embodiment, the grindstone 49 is held between the tip portion 47a of the holder portion 47 and the holding member 48. However, this structure has an error in the tilt component of the grindstone 49. However, in the super-finishing, it was obtained in the previous step (grinding step). Since it is desired to improve the roughness of the workpiece 50 without breaking the shape of the superfinishing target portion, the grindstone 49 is replaced with the workpiece 5 instead of the above configuration.
It is preferable to use a profile mechanism capable of following a change in posture of 0.

Specifically, as shown in FIG. 8, the intermediate member 52 is provided at the tip portion 47a of the holder portion 47 of the grindstone holder.
Is attached via a pivot 53, and the intermediate member 5
An O-ring 55 is fitted between 2 and the tip portion 47a. A holding member 54 is attached to the intermediate member 52 by a plurality of screw members 56, and a grindstone 49 is held between the intermediate member 52 and the holding member 54. With this configuration, the grindstone 49 can follow changes in the posture of the workpiece 50, and the workpiece 50 obtained in the previous step (grinding step)
It is possible to surely improve the roughness without breaking the shape of the superfinishing target part.

(Second Embodiment) Next, a second embodiment of the present invention will be described with reference to FIG. Figure 9
FIG. 9A is a top view showing a main part configuration of a superfinishing device according to a second embodiment of the present invention, and FIG. 9B is a D view of FIG. 9A.
It is a longitudinal cross-sectional view taken along line D.

While the rolling bearing is used as the regulating member in the first embodiment described above, the linear guide is used as the regulating member in the present embodiment. The rest of the configuration is the same as that of the above-described first embodiment, and the same members are designated by the same reference numerals, and the description thereof will be omitted or simplified.

Specifically, as shown in FIG. 9, a regulating member 61 is provided between the slider 12 and the slider 13 so as to abut on the cam portions 18b and 19b of the eccentric cams 18 and 19, respectively. . The restriction member 61 is a linear guide that is slidable in the vertical direction while engaging with a guide rail 62 provided on the support column 63. The regulating member 61 is for each spindle 1
When the eccentric cams 18 and 19 are rotated in accordance with the addition of points 6 and 17, the eccentric cams 18 and 19 receive a vertically upward force or a downward force, and they are moved in the direction of the received force.

Thus, by using the linear guide as the regulating member 61, the structure can be further simplified. Further, the eccentric cams 18, 19 of the regulating member 61
Since the contact surface with the cam portions 18b and 19b of is flat,
No error occurs unlike rolling bearings. Furthermore, since the force that the regulating member 61 receives from each eccentric cam 18 and 19 is on the same line of action, it is advantageous to use a linear guide for the regulating member 61 from the viewpoint of load capacity, rigidity, and the like.

(Third Embodiment) Next, a third embodiment of the present invention will be described with reference to FIGS. FIG. 10A is a top view showing the structure of the superfinishing apparatus according to the third embodiment of the present invention, and FIG.
0 (a) is a front view of the superfinishing apparatus, and FIG. 11 is a sectional view showing an example of the structure of the eccentric cam mechanism.

As shown in FIG. 10, the superfinishing apparatus of this embodiment has a base 71 on which two sliders 72 and 73 are mounted so as to face each other.

The slider 72 has a plurality of linear guides 72a that slide along a pair of guide rails 74a and 74b provided on the upper surface of the base 71. The plurality of linear guides 72a guide the pair of guide rails 74a and 74b. It is configured to be movable on the base 71 while being guided. A spindle 76 extending in a direction orthogonal to the guide rails 74a and 74b is rotatably supported by the slider 72. A link member 90 is attached to one end 76a of the spindle 76, and a grindstone holder 80 is attached to the other end 76b. The structure of the grindstone holder 80 is the same as the structure shown in FIG. 7, and the description thereof is omitted here.

The slider 73, like the slider 72,
A pair of guide rails 75 provided on the upper surface of the base 71
A plurality of linear guides 73a sliding along a and 75b
And is configured to be movable on the base 71 while being guided by the pair of guide rails 75a and 75b by the plurality of linear guides 73a. A spindle 77 extending in a direction orthogonal to the guide rails 75a and 75b is rotatably supported by the slider 73. A link member 91 is attached to one end 77a of the spindle 77, and a grindstone holder 81 is attached to the other end 77b. The grindstone holder 81 has the same structure as the grindstone holder 80 (see FIG. 7).

Between the slider 72 and the slider 73,
An eccentric cam mechanism is provided. This eccentric cam mechanism
It has a shaft box 88 fixed to the base 71 and a rotating shaft 87 supported by the shaft box 88. A link member 89 is provided at one end of the rotating shaft 87 and a support plate 86 is provided at the other end. ing. A pair of pedestals 85 (only one of which is shown) is fastened to the support plate 86, and two shafts 82a and 83a arranged at predetermined intervals are attached to each pedestal 85. Here, each pedestal 85 is attached to each shaft 82.
a and 83a are arranged at positions separated from the center of the rotating shaft 87 by a distance e (amount of eccentricity). Axis 8
A disk 82 is rotatably supported by 2a, and a disk 83 having the same diameter as the diameter of the disk 82 is rotatably supported by the shaft 83a. The disk 82 is positioned so that its edge contacts the contact portion 72b provided on the slider 72, and the disk 83 contacts the edge thereof against the contact portion 73b provided on the slider 73.

The spring member 103 causes the slider 72 to move.
The contact portion 72b is urged in the direction in which it is pressed against the disc 82. The spring member 103 is held by the holding member 102 fixed to the base 71. Similarly, the slider 73 is biased by the spring member 105 in the direction in which the contact portion 73b is pressed against the disc 83. The spring member 105 is a holding member 104 fixed to the base 71.
Held in.

The link member 90 of the spindle 76 is connected to the intermediate link member 96 via the link member 97, and the intermediate link member 96 is connected to the link member 89 of the rotating shaft 87 via the link member 94. . Here, the intermediate link member 96 is composed of a disk that rotates around the axis, and the connection point of the intermediate link member 96 with the link member 97 and the connection point with the link member 94 are provided at predetermined positions. The link member 91 of the spindle 77 is connected to the intermediate link member 98 via the link member 99,
The intermediate link member 98 is connected to the link member 89 of the rotating shaft 87 via the link member 95. Here, the intermediate link member 98 is made of a disk that rotates around its axis, and the connection point of the intermediate link member 98 with the link member 99 and the connection point with the link member 95 are provided at predetermined positions. .

The link member 89 of the rotary shaft 87 is
7, which is a disk coaxial with 7
At the same time, one end of the link member 93 is connected. The other end of the link member 93 is connected to a conversion member (not shown) for converting the rotary motion of the drive motor 92 into a swing motion. This conversion member is fixed to the output shaft (not shown) of the drive motor 92, and the link member 93 in the conversion member is provided.
The connection point with is at a position eccentric by the eccentric amount E2 with respect to the output shaft of the drive motor 92. The amount of eccentricity E2 defines the maximum value of the rotation angle θ of each spindle 76, 77 and the rotation shaft 87.

With such a link mechanism, the rotary motion of the drive motor 92 is converted into the swing motion of the spindles 76, 77 and the rotary shaft 87. The rotary shaft 87 is rotationally moved angularly, and the spindles 76, 77 are interlocked with the rotary shaft 87.
Are angularly rotated in opposite directions. For example, when the rotating shaft 87 is angularly rotated clockwise (in FIG. 10B), the spindle 76 is angularly rotated counterclockwise and the spindle 77 is angularly rotated clockwise. Further, as the rotary shaft 87 rotates, the support plate 86 is angularly rotated clockwise around the rotary shaft 87. When each of the disks 82 and 83 swings clockwise around the rotation shaft 87 as the support plate 86 rotates, the abutting portion 72b of the slider 72 contacts the disk 82 by the urging force of the spring member 103. In the contacted state, it is moved toward the disc 82 along the guide rails 74a and 74b. The slider 73 is moved by the biasing force of the spring member 105 toward the disc 83 along the guide rails 75a and 75b with the abutting portion 73b being in contact with the disc 83.

Further, the rotary shaft 87 is rotated counterclockwise (see FIG. 10).
The same applies when rotated angularly to (in (b)).

With this structure, the spindles 76, 7
The grindstone holders 80, 81 attached to the No. 7 rotate around the spindles 76, 77 while moving in the guide directions of the guide rails 74a, 74b, 75a, 75b. At this time, the tip position of the grindstone of the grindstone holders 80, 81 is a trajectory having a radius of curvature determined according to the linear distance r0 from the center of the spindles 76, 77 to the tip position of the grindstone and the eccentric amount e of the eccentric cam mechanism. Move along. That is, the grindstone holders 80 and 81 can be swung so that the tip position of the grindstone moves along the radius of curvature of the superfinishing target portion of the workpiece held at a predetermined position.

In the present embodiment, the two spindles 76 and 77 are simultaneously driven in opposite directions,
The vibration can be balanced, and the rocking speed can be increased.

Further, in the present embodiment, when the eccentricity e of the eccentric cam mechanism can be adjusted, an eccentric cam mechanism as shown in FIG. 11 may be used. As shown in FIG. 11, this eccentric cam mechanism has a support plate 116 provided on the rotary shaft 87, and this support plate 116 has a dovetail groove 116.
a is formed. The support plate 116 includes a pair of pedestals 1.
15 are fastened with corresponding set screws 119 through dovetail grooves 116a, and each pedestal 115 has a shaft 113
Is attached. The disk 8 is attached to each shaft 113.
Rolling bearings 111 corresponding to 2,83 are supported. In each pedestal 115, each shaft 113 has a rotating shaft 87.
Are arranged at positions separated by a distance e (amount of eccentricity) from the center. Further, each pedestal 115 has a position adjusting hole 115 for receiving the set screw 119.
A is formed, and the distance between the pedestals 115, that is, the eccentricity e can be adjusted by the reference plug 117. The reference plug 117 is fitted in a hole formed in the support plate 116 so that its axis is coaxial with the rotation shaft 87. For example, a plurality of reference plugs 117 having different widths are prepared, and the reference plugs 117 having widths corresponding to the eccentricity e are attached to the support plate 116, whereby the distance between the pedestals 115, that is, the shaft 1
The distance (eccentricity) e between the rotation shaft 13 and the rotary shaft 87 can be adjusted. When the relative position of each pedestal 115 with respect to the support plate 116 changes due to the adjustment of the spacing, the position of the set screw 119 on each pedestal 115 changes with the position change, but the position adjusting hole 115a is provided. Therefore, even after the adjustment of the relative position of each pedestal 115, each pedestal 115 is fixed to the support plate 116 in the same manner as before the adjustment.
It can be attached by 9.

By providing the eccentric cam mechanism having such a structure, the eccentricity e can be easily adjusted.
As a result, the radius of curvature of the locus drawn by the tip position of the grindstone can be easily changed, and it becomes possible to deal with superfinishing of a plurality of workpieces having different curvatures.

Further, the superfinishing device of this embodiment can be applied not only to spherical rollers but also to superfinishing raceway grooves of inner and outer rings. In this case, only one spindle may be swung, and the other spindle may be made to follow as a load mass.

(Fourth Embodiment) Next, a fourth embodiment of the present invention will be described with reference to FIGS. FIG. 12 is a diagram schematically showing the structure of a superfinishing line using the superfinishing apparatus according to the present invention, and FIG.
FIG. 14 is a diagram showing a state in which a workpiece is being superfinished in the superfinishing line of FIG. 14, and FIG. 14 is a diagram schematically showing movement of boxes in the line of FIG.

In the present embodiment, a line for superfinishing a workpiece received from a grinding line by using any of the superfinishing apparatuses shown in the above-mentioned respective embodiments will be described.

With the current grinder, a cycle time of 3.6 seconds can be realized, but in order to correspond to the cycle time of this grinder on a one-to-one basis, two grindstone holders are used in the super finishing line. When it is provided (in the case of two axes), it is necessary to realize the cycle time in 3.6 seconds. In order to realize the cycle time of 3.6 seconds, it is necessary to use a grindstone (for example, a CBN grindstone) that is relatively unaffected by the crossing angle and has less clogging, and increase the rotation speed of the workpiece. . Also, it is important to shorten the time required for loading and unloading the workpiece. Therefore, in the super-finishing line, the two-roll system (see FIG. 7) is used to support the work piece, and the box is used to convey the work piece.

Specifically, as shown in FIG. 12, this line includes an inlet 150 for receiving a workpiece 151 from a grinding line, a processing section 160 for superfinishing, and a workpiece after superfinishing. And an outlet portion 170 for discharging 151,
A box 152 is used to convey the workpiece 151 from the inlet 150 to the outlet 170. Box 152
Is provided with two holding portions 152a respectively holding the workpiece 151.

The box 152 is mounted on the moving table 153. A feed screw mechanism and a linear guide are incorporated in the moving table 153. The feed screw mechanism has a screw shaft 153a and a nut portion (not shown) fixed to the moving base 153. The screw shaft 153a is screwed into the nut portion and driven by the drive motor 156.
The linear guide 154 of the movable table 153 is slidably engaged with the horizontal guide rail 155. Drive motor 156
When the screw shaft 153a is driven by the moving table 153,
Are moved along the horizontal guide rail 155.

As shown in FIG. 13, the movable table 153 is supported by a plurality of supporting members 158, and each supporting member 158 is
It is configured to be movable in the vertical direction along a vertical guide rail 172 provided on a column 173 fixed to the base 174. Each support member 158 is provided with a plurality of linear guides 171 slidably engaged with the feed screw mechanism 159 and the vertical guide races 172. The feed screw mechanism 159 of each support member 158 has a drive motor 157.
The support members 158 are moved in the vertical direction. By moving each support member 158 in the vertical direction, the moving base 153 can be moved in the vertical direction.

At the entrance 150, two workpieces 151 are received from the grinding line, and each workpiece 151 is loaded in the box 152. The box 152 on which the workpieces 151 are loaded is moved by the moving table 153, and the processing unit 1 is moved.
60 (A1 in FIG. 14).

In the processing section 160, FIGS.
As shown in FIG. 3, the two workpieces 151 stacked in the box 152 are held between a pair of rollers 163 facing each other. At this time, each workpiece 151 is positioned and rotated with respect to the grindstones 162 held by the two grindstone holders 161 respectively. Each whetstone 162
As described in each of the above-described embodiments, while being pressed against the processing target portion of the corresponding workpiece 151, it swings with the radius of curvature of this portion. As a result, the processing target portion of each workpiece 151 is superfinished.

The box 152 on which the workpiece 151 after superfinishing is loaded is sent to the outlet section 170 by the movement of the moving table 153. At the outlet section 170, the movable table 153 is moved vertically downward (A in FIG. 14).
2), the workpieces 151 stacked in the box 152
Is discharged to the outside. After that, the box 152 is returned to the entrance 150 by the movement of the moving table 153 (see A in FIG. 14).
3), the moving table 153 is moved vertically upward (A4 in FIG. 14).

[0076]

As described above, according to the present invention,
The eccentric cam is in contact with the regulating member, and the rotary shaft is angularly driven while the rotary shaft is biased by the biasing member, so that the grindstone moves around the rotary shaft while moving in the predetermined direction. Since it is oscillated to the axis, the linear distance from the axis of the rotating shaft to the tip position of the grindstone and the amount of eccentricity of the eccentric cam member can be set appropriately to follow the trajectory of the radius of curvature corresponding to the super-finished part of the workpiece. It is possible to swing the tip of the grindstone. Further, this swing mechanism can be realized with a simplified structure. Furthermore, since the mass of the entire swing mechanism can be reduced, it is possible to increase the swing speed and improve the processing efficiency. That is, the structure can be simplified, and as with the case of superfinishing the superfinishing target portion having a small curvature, it is possible to obtain a finish with high processing efficiency and good precision and roughness.

[Brief description of drawings]

FIG. 1 is a diagram showing a basic configuration of an apparatus for realizing a superfinishing method according to the present invention.

FIG. 2 is a diagram showing a locus drawn by a grindstone tip position P in FIG. 1 according to rotation of a rotary shaft.

3 is a diagram showing the relationship between the eccentric amount e of the eccentric cam and the radius of curvature (superfinishing radius) R0 when the linear distance r0 from the center of the rotary shaft to the grindstone tip position P in FIG. 1 is used as a variable. is there.

FIG. 4 is a diagram showing a relationship between a straight line distance r0 from a center of a rotating shaft to a grindstone tip position P and a curvature radius (superfinishing radius) R0 when the eccentricity e of the eccentric cam in FIG. 1 is used as a variable. is there.

5A is a top view showing the structure of the superfinishing apparatus according to the first embodiment of the present invention, and FIG. 5B is a longitudinal sectional view taken along the line AA of FIG. is there.

6A is a front view of the eccentric cam of FIG. 5, FIG. 6B is a side view of the eccentric cam of FIG. 5, and FIG. 6C is a perspective view of the eccentric cam of FIG.

7A is a vertical cross-sectional view showing the configuration of the grindstone holder of FIG. 5, and FIG. 7B is a view seen from B of FIG. 7A.

8A is a front view of another configuration example of the tip portion of the grindstone holder, and FIG. 8B is a cross-sectional view taken along line CC of FIG. 8A.

FIG. 9A is a top view showing the main part configuration of a superfinishing apparatus according to a second embodiment of the present invention, and FIG. 9B is a D of FIG.
It is a longitudinal cross-sectional view taken along line D.

10A is a top view showing a configuration of a superfinishing apparatus according to a third embodiment of the present invention, and FIG. 10B is a front view of the superfinishing apparatus of FIG. 10A.

FIG. 11 is a cross-sectional view showing a configuration example of an eccentric cam mechanism.

FIG. 12 is a diagram schematically showing a configuration of a superfinishing line using the superfinishing device according to the present invention.

FIG. 13 is a diagram showing a state in which the workpiece is being superfinished in the superfinishing line of FIG. 12;

FIG. 14 is a diagram schematically showing movement of boxes in the line of FIG.

15A and 15B are a front view and a side view showing a main part configuration of a conventional superfinishing apparatus.

FIG. 16 is a front side cross-sectional view showing a main part configuration of an apparatus for superfinishing a portion having a small curvature in a conventional workpiece.
It is a side surface side sectional view and a sectional view showing the tip tip circumference of a whetstone.

[Explanation of symbols]

1,11,71 base 2a rotating shaft 3,20,21 Grindstone holder 4,49 Whetstone 5,18,19 Eccentric cam 6a, 6b, 23, 24, 61 regulating member 16,17 spindle 35, 37, 103, 105 Spring member

Claims (2)

[Claims] 1. A method of superfinishing a curved surface forming portion of a workpiece, wherein a rotary shaft supported on a base so as to be movable in a first direction orthogonal to the axis is orthogonal to the axis of the rotary shaft. The eccentric cam member that is eccentric with respect to the rotation shaft is coaxially attached, and the regulating member and the eccentric cam member that are in contact with the eccentric cam member are provided at a predetermined distance in the second direction. A biasing member for biasing the regulating member in the direction of 1 is provided on the base, and the eccentric cam is in contact with the regulating member and the rotating shaft is biased by the biasing member. A superfinishing method, characterized in that the grindstone is swung around the rotation axis while moving the rotation axis in the first direction by rotationally driving the rotation axis. 2. A superfinishing device for a curved surface forming portion of a workpiece, a base, a rotary shaft movably supported on the base in a first direction orthogonal to an axis, and A grindstone attached to the rotary shaft at a predetermined distance in a second direction orthogonal to the axis of the rotary shaft, and an eccentric cam member coaxially attached to the rotary shaft and eccentric to the rotary shaft. A restricting member that is provided on the base and is in contact with the eccentric cam member, and a biasing member that is provided on the base and that biases the eccentric cam member toward the restricting member in the first direction. A superfinishing device comprising: a biasing member; and a drive mechanism that angularly rotationally drives the rotary shaft.