JPH03219471A - Linear guide mechanism - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a linear guide mechanism for accessing a head in a magnetic disk device.

[Conventional technology]

Conventional devices, as described in US Pat. No. 4,743,987, press a guide wheel against a rail to form a linear guide mechanism. No special improvements were made to the guide wheel itself, and the effects of assembly errors were not taken into consideration. With the structure of this conventional linear guide mechanism, if there is an assembly error in the guide wheel or guide bearing, the following problems will occur.

(1) If the contact point between the guide bearing outer ring and the rail deviates slightly from the widthwise center of the guide bearing outer ring, the friction force between the guide bearing outer ring and the rail will cause the contact point between the outer ring and the rail to erect on the rail surface. A moment I is applied that rotates the outer ring around the linear direction. This moment made the running of the outer ring unstable, causing a decrease in positioning accuracy.

(2) When the guide bearing is assembled to the bogie body with its rolling direction at an angle to the rail direction, the outer ring of the guide bearing moves in the axial direction (@ direction), and there is a gap between the outer ring and the axle. The intervening ball rides on its raceway surface, resulting in a change in the distance between the guide bearing's rotation axis and the rail.
This caused a decrease in the positioning accuracy of the carriage. Axial movement of the outer ring causes unstable running of the bearing, and also causes slippage between the outer ring and the rail, causing wear.

[Problem to be solved by the invention]

The above conventional technology does not take into account the effect that the assembly error of the guide bearing with respect to the carriage has on the accuracy of the linear guide mechanism, and the rolling elements of the bearing ride on the raceway groove, resulting in a change in the distance between the car and the guideway. There are problems in that the positioning accuracy of the linear guide mechanism is reduced, and that wear occurs due to slipping between the outer ring of the guide bearing and the guide path, reducing the reliability of the linear guide mechanism.

An object of the present invention is to solve the above problems and provide a linear guide mechanism with high positioning accuracy.

[Means to solve the problem]

In order to achieve the above object, the linear guide mechanism of the present invention includes a movable body having a main shaft and an outer ring rotatably provided on the main shaft, and a movable body having a plurality of bearings attached as wheels, and the outer ring rolling into contact with the outer ring. The linear guide mechanism includes a guide path for guiding a movable body, and is characterized in that an attachment angle adjustment member is provided to adjust the angle between the main shaft and the guide path.

It is preferable that the mounting angle adjusting member is a member that can be contracted/expanded by a signal and is provided between the main shaft and a mounting hole of the movable body into which the main shaft is inserted. A member may also be provided between the guideway and a support member supporting the guideway.

Further, when the mounting angle adjusting member is provided between the main shaft and the mounting hole of the movable body into which the main shaft is inserted, the mounting angle adjusting member is installed at at least two places in the axial direction of the main shaft, and at least two places around the main shaft. It is preferable that the angle adjustment mechanisms be provided in parallel to each other in pairs at each of at least two locations in the axial direction of the main shaft, or in at least two locations in the axial direction of the main shaft.
Preferably, one pair of attachment angle adjustment members are provided in each location axially symmetrically, and one pair of attachment angle adjustment members are positioned in a direction parallel to the running surface of the guideway, and the other pair of attachment angle adjustment members are positioned in a direction perpendicular to the running surface.

Further, the pair of mounting angle adjusting members may be provided axially symmetrically at one location in the axial direction of the main shaft, and a pivot bearing may be formed between the bottom surface of the mounting hole and the base end of the main shaft.

Further, in order to achieve the above object, another linear guide mechanism of the present invention includes a movable body having a main shaft and a plurality of bearings as wheels, each having a main shaft and an outer ring rotatably provided on the main shaft;
In the linear guide mechanism including a guide path in which the outer ring rolls into contact with the movable body to guide the movable body, a cylindrical holding member is fitted into a mounting hole provided in the movable body and accommodates the main shaft. The present invention is characterized in that an attachment angle adjustment member is provided between the inner circumferential surface and the main shaft inserted into the holding member to adjust the angle formed between the main shaft and the guide path.

In order to achieve the above object, another linear guide mechanism of the present invention includes a movable body having a main shaft and an outer ring rotatably provided on the main shaft, the outer ring rolling into contact with a movable body having a plurality of bearings attached as wheels. 7- In the linear guide mechanism provided with a guide path for guiding the movable body, a cylindrical first holding member is fitted into a mounting hole provided in the movable body and accommodates the main shaft, and the first holding member is fitted to the outside of the main shaft. A second holding member having a cylindrical shape is inserted into the diameter thereof, and an attachment angle for adjusting an angle formed between the main shaft and the guide path between the inner circumferential surface of the first holding member and the outer circumferential surface of the second holding member. It is characterized by the provision of an adjustment member.

The mounting angle adjusting member is characterized in that it is a piezoelectric element.

Furthermore, in order to achieve the above object, another linear guide mechanism of the present invention includes a movable body having a main shaft and an outer ring rotatably provided on the main shaft, and a movable body in which a plurality of bearings are attached as wheels, and the outer ring rolls. The linear guide mechanism includes a guide path that guides the movable body in contact with the main shaft, and is characterized in that the main shaft has a bimetal structure, and a drive circuit that drives the bimetal is provided.

[Effect]

In the linear guide mechanism of the present invention, the angle adjustment member adjusts the angle between the main axis of the bearing, which is a wheel, and the guideway, and adjusts the contact state in the rolling direction of the outer ring or in the width direction between the guideway and the outer ring. Fix it. The attachment angle adjustment member is, for example, a piezoelectric element that expands or contracts as the applied voltage increases or decreases.

If this mounting angle adjustment member is provided in pairs in parallel to the running surface of the guideway at two locations in the direction of the main axis between the main shaft and the mounting hole of the movable body into which the main shaft is inserted, the signal will be If one of the pair of attachment angle adjustment members provided at one location is contracted and the other is expanded, and one of the pair of attachment angle adjustment members provided at the other location is expanded and the other is contracted. Since the main shaft rotates in a plane parallel to the running surface of the guideway, the rolling direction of the outer ring can be adjusted. In addition, in the above explanation, if each pair of attachment angle adjustment members is provided in a direction perpendicular to the running surface instead of parallel to the running surface, the main shaft will rotate in a plane perpendicular to the running surface, so the parallelism between the running surface and the main shaft can be adjusted. I can do it.

In addition, a pair of mounting angle adjustment members are provided axially symmetrically at two locations in the direction of the main shaft between the main shaft and the mounting hole of the movable body into which the main shaft is inserted. If the main axis is parallel to the running surface and the other part is perpendicular to the running surface, by contracting one mounting angle adjustment member at one location and expanding the other, the main axis will be parallel to the running surface. By contracting one mounting angle adjustment member and expanding the other at another location, the main shaft turns in a plane perpendicular to the running surface, thus adjusting the rolling direction of the outer ring and the main shaft. The parallelism of the surfaces can be adjusted.

In a linear guide mechanism in which a pair of mounting angle adjustment members are provided at one location on the main shaft and a pivot bearing is formed between the bottom of the mounting hole of the movable body and the base end of the main shaft, the pair of mounting angle adjustment members are installed parallel to the running surface. In this case, by contracting one mounting angle adjusting member and expanding the other, the main shaft turns parallel to the running surface around the pivot, and if the pair of mounting angle adjusting members are made perpendicular to the running surface, By contracting one attachment angle adjusting member and expanding the other, the main shaft pivots about the pivot l- in a direction perpendicular to the running surface.

By combining the bearing, the mounting angle adjustment member, and the holding member that houses them, the combined set can be attached to a movable body as a single unit. Also, the first-
By combining the holding member, the attachment angle adjusting member, and the second holding member, assembly and disassembly of the combined set, bearing, and movable body can be simplified.

In another linear guide mechanism of the present invention, in which the mounting angle adjusting member is provided between the guide path and its supporting member, the mounting angle adjusting member is expanded or contracted to support the running surface of the guide path. The distance from the vehicle can be changed, and the posture of the movable body on the running surface, such as the tilt, can be adjusted.

In another linear guide mechanism of the present invention, in which the main shaft is made of a bimetal as an attachment angle adjustment member, the rolling direction of the outer ring can be adjusted by making the bending direction of the bimetal parallel to the running surface.
Also, if the bending direction of the bimetal is perpendicular to the running surface,
The contact condition between the running surface and the outer ring, for example, the unevenness of the outer ring, can be corrected.

〔Example〕

An embodiment of the present invention will be described below with reference to FIG. 1st
The figure is a sectional view perpendicular to the running direction of the linear guide mechanism. Here, a case will be described in which the linear guide mechanism is applied to a magnetic disk device.

The capacity of recent magnetic disk drives has been increasing year by year, and the biggest challenges are increasing density and throughput.

In order to achieve higher density, it is necessary to improve the guiding accuracy of the linear guide mechanism for accessing the head.

In the embodiment shown in FIG. 1, the linear guide mechanism includes a carriage 5 that is a movable body, a pair of guide paths 16 with trapezoidal cross-sections facing each other with the carriage 5 in between, and a guide attached around the carriage 5. The guide bearing 9 and the preload bearing 27 are pressed against the trapezoidal horizontal plane of the guide path 16, and the guide bearing 9 and the preload bearing 27 are pressed against the trapezoidal surface of the guide path 16. Outside of 27 @12
It rolls along the guide path 16 with the rotation of.

The preload bearing 27 is given a radial force by the spring member 15 and is pressed against the guide path 16 . This pressing force is transmitted to other guide bearings 9, and as a result,
The attitude of the carriage 5 is determined. In addition, the guide bearing 9 rolls on the horizontal plane, which is the running surface of the guide path 16, and
2, an inner race shaft 14 which is a main shaft coaxially mounted within the outer race 12 via rolling elements 13, and a carriage 5 into which the outer circumference of the extended shaft portion of the inner race shaft 14 is fitted and fixed.
The mounting angle adjusting member 17 (hereinafter simply referred to as the angle adjusting member 17) is interposed between the mounting hole and the inner surface of the mounting hole. The angle adjustment member 17 has a guide bearing 19
so that it rolls smoothly on the guide path 16 without twisting.
It is provided to adjust the angle between the inner ring shaft 14 and the running surface of the guideway 16, and is used to adjust installation errors caused by machining errors of parts such as guide bearings and mounting holes and assembly errors after assembly. , can be zero.

Here, we will discuss why the angle between the guide bearing 9 and the guide path 16 is a problem. First, consider the angle between the direction in which the carriage 5 is guided by the guide path 16, that is, the direction perpendicular to the plane of the paper in FIG. 11, and the axis of the inner ring shaft 14 of the guide bearing 9. When this angle is not 90°, the outer shaft 12 of the guide bearing moves in the axial direction as the carriage 5 moves. As a result, the distance between the guide path 16 and the axis of the guide bearing 9 changes. This causes pitching, rolling, and yawing that change the attitude of the carriage 5. Furthermore, if the attitude of the carriage 5 changes, it causes a head positioning error. Therefore, it is necessary to accurately set the angle of the guide bearing 9 to 90°. By providing the above-mentioned angle adjustment member 17 at an appropriate position, this installation error can be canceled.

Next, the running surface of the guideway 16 and the inner ring shaft 14 of the guide bearing 9
The angle (here, it is assumed to be γ) with the axis of is described. This will be explained using a ball bearing as an example. When a bearing has radial clearance, the outer ring can be tilted with respect to the inner ring axis by the angular clearance corresponding to the radial clearance.

However, if a moment that tends to tilt the guide bearing beyond the angular clearance acts, the life of the guide bearing will rapidly decrease. Also,
The outer ring of the guide bearing 9 comes into partial contact with the guide W&16. In this situation, carriage 5
This reduces the guiding accuracy of the head and causes head positioning errors. Therefore, a means for canceling the angle γ is required.

Note that even when a sliding bearing is used, a lubricant or self-lubricating substance is present in the gap between the outer ring and the inner ring shaft, and the outer ring is tilted with respect to the inner ring axis by the amount of the gap, causing the outer ring to The problem of one-sidedness arises.

The embodiment shown in FIG. 1 shows an angle adjustment member 17 having a structure that can cancel the angle γ.

15- The operation is based on the inner ring shaft 14 of the guide bearing 9 and the carriage 5.
An angle adjusting member 17 formed of an electrostrictive element is provided between the
Two guide paths 16 are provided at two locations in the longitudinal direction of the inner ring shaft 14, respectively.
It is provided at a position facing 180 degrees perpendicularly to the running surface. The inner ring axis of the guide bearing 9 can be tilted by operating the angle adjustment members 17 at two locations in the axial direction in opposite phases.

The operation of the angle adjustment member 17 will be explained in more detail as follows. A total of four angle adjustment members 17 are provided in two locations in the longitudinal direction of the inner ring shaft 14 at opposing positions of 180 degrees for one bearing.Consider the guide bearing 9 on the lower left in FIG. . On the outer ring 12 side, numbers A, B, C, and D are given in a clockwise rotation starting from the angle adjusting member 17 provided at the bottom of the drawing.

Adjust the mounting angle of the guide bearing 9 around the axis perpendicular to the ground.
When rotating to the right, A and C may be expanded and B and D may be contracted. This makes it possible to adjust the mounting angle of the guide bearing 9. 6. Conversely, if you want to rotate counterclockwise, contract A and C,
All you have to do is expand B and D.

When a piezoelectric element is used as the electrostrictive element, if a voltage is applied in advance and the bearing is fixed with a displacement of approximately 1/2 of the maximum working displacement, then by increasing or decreasing the applied voltage, , the piezoelectric element can be contracted and expanded most effectively. Therefore, when adjusting the mounting angle of the guide bearing 9, the applied voltages of A and C may be increased and the applied voltages of B and D may be decreased in order to rotate the guide bearing 9 clockwise.

Furthermore, after the mounting angle has been adjusted, the applied voltage after adjustment is maintained, so that no further adjustment is required. Furthermore, by storing this applied voltage, even after the applied voltage is removed, the adjustment of the mounting angle of the guide bearing is completed by applying the same applied voltage at the time of restart.

Next, a method for adjusting the mounting angle of the guide bearing will be described. If there is an error in the mounting angle of each guide bearing 9, the outer ring of the bearing will roll due to the reciprocating motion of the carriage, and the inner ring shaft 14 will be distorted relative to the guide path 16, as described above.
displacement occurs.

This displacement changes the attitude of the carriage 5.

Changes in the posture of the carriage 5 cause head positioning errors. Therefore, if the tilt of the carriage 5 is determined by directly measuring the attitude of the carriage 5 or by knowing the positioning error of the head from the positioning signal, it is possible to know whether the adjustment of the mounting angle of the guide bearing 9 is correct or not. Therefore, while determining the attitude of the carriage 5, the mounting angle of the guide bearing 9 may be adjusted, and the mounting angle adjusting member 17 may be set so that the positioning error of the head is minimized.

Next, a method of determining the direction in which the mounting angle of the guide bearing 9 should be adjusted will be described. Errors in the mounting angle of the guide bearing 9 can be divided into errors around an axis perpendicular to the surface of the guide path 16 of the guide bearing 9 and errors around an axis parallel to the traveling direction of the carriage 5. Assuming that the former error is β and the latter error is γ, the displacement of the inner race shaft 14 due to each error is expressed by the following equation from FIGS. 21 and 22.

X=ZXsin β ・・(1) △X = (r − rcos(φ−θ)+ rt:l
5iny・ (6) △Xo= r+γ (7) △X−△Xo= rl sin α+ (8) 2: X: αI: α. : rI : ro Distance over which the guide bearing 9 has rolled Amount of axial movement of the outer ring 12 Ball 13 and inner ring shaft
Contact angle of raceway groove on 2nd side Inner ring shaft 14 side raceway groove radius Outer ring 12 side raceway groove radius 19- d: Diameter of ball 13 △hβ: Displacement of inner ring shaft 14 due to installation angle error β ΔX: Adjacent ball is on inner ring shaft 14 Distance from the orbit center D r s : Diameter of the orbit center on the inner ring shaft 14 side r : Orbit radius at a point ΔX away from the center φ : Spacing between balls 13 (2π
/number of balls) σ: Position of ball 13 △Xo: Distance from center to contact point of ball 13 Δhγ: Displacement of inner ring shaft 14 due to installation angle error r (1), (2), (3) From equations (4) The formula is obtained, (5
), (6), (7), and (8), equation (9) is obtained. Comparing both formulas, if the error β is small, the rate of change of Δhβ with respect to the rolling distance of the bearing is small (that is, the period is long). On the other hand, it can be seen from equation (6) that Δhγ is periodically repeated depending on the interval between balls. Therefore, from the characteristics of both, it is possible to know which of the errors β and γ has a larger influence, and the direction in which the mounting angle of the bearing should be adjusted can be selected.

Next, a method for adjusting the mounting angles of the plurality of guide bearings 9 will be described. It is assumed that the mounting angles of n guide bearings 9 are adjusted. The adjustment procedure is to sequentially change the n angle adjustment members 17 by minute angles, and then the head positioning error (calculated from the off-track amount of the head at the same position). , which will be discussed in detail later). Here, the head positioning error is assumed to be ei (j=1 to n).

Therefore, find the minimum value of (ei)2 (i = 1 to n), and (e
i) Change the mounting angle adjusting member that minimizes 2 by ΔOi. Repeat the above steps in order and e2(=Σe
The mounting angles of a plurality of guide bearings can be adjusted by adjusting until i2) becomes the minimum or falls below the standard tolerance value e2max.

Next, a method for determining the head positioning error will be described.

Since the guide accuracy of the linear guide becomes a problem especially in magnetic disk drives having a plurality of heads and a plurality of disks, this case will be explained. First, based on the disk on which the servo information has been written, the servo information is transferred to another data disk. Next, while repeating back-and-forth seek, the servo information recorded on each disk at the same position is read. At this time, depending on the reproducibility depending on the position,
A slight positional shift is detected in the data read by each head compared to when it was recorded. This positional deviation is called the off-track amount of the head, and by taking the ratio of this off-track amount and the distance between the heads I-, the change in the attitude of the carriage (the inclination of the carriage) can be determined. By adjusting the angle of each guide bearing so as to minimize this positioning error, a highly accurate guide mechanism can be achieved.

In order to reduce the installation error of the guide bearing, it is possible to improve the machining accuracy and assembly accuracy of the components of the linear guide mechanism, but this will lead to higher costs and there is a limit to the accuracy improvement, so the above-mentioned By adjusting the mounting angle of the guide bearing according to the method, a highly accurate guide mechanism can be easily achieved.

The structure and operating principle of one embodiment of the present invention have been explained above.Next, we will show the overall structure of a magnetic disk drive in which a linear guide mechanism is used, and explain the role of the linear guide mechanism and the necessity of guiding accuracy. In addition, the operation of the guide bearing and its problems will be explained.

Figure 2 shows the overall structure of a magnetic disk drive, which includes a head 3 for reading and writing data, a disk 1 on which data is stored, a spindle motor 2 for rotating the disk 1, and a guide arm 4. A carriage 5 on which a supported head 3 is mounted, a guide bearing 9 and a guide path 8 that guide the carriage 5, a base 11 that supports the guide path 8 and the spindle motor 2, and a voice coil 7 that makes the carriage 5 perform an access operation. The magnet 1-6, the drive circuit 29 that drives the voice coil 7, the control circuit 3o that controls data reading/writing and the drive circuit 37, -23= connecting member 10 that elastically connects the base 11 and the magnet 6 It consists of

The carriage 5 is driven by a voice coil motor composed of a voice coil 7 and a magnet 6, and reciprocates on a guide path 8. This allows the head 3 to read the data written on the disk 1, or
Write the data.

In order to read and write this data, the head 3 at the tip of the carriage 5 must be positioned at an arbitrary point on the disk 1. This positioning accuracy ensures that the carriage 5 is
It depends on the accuracy of guiding the head 3 over the disk and the accuracy of the control circuit 30 using the position signal detected by the head 3 from above the disk. The assembly accuracy of the guide bearing 9 has a negative effect on this positioning accuracy. Figure 3 is the second
3 is a sectional view of a guide bearing 9 when a part of the linear guide mechanism shown in the figure is viewed from the access direction of the carriage 5. FIG. Among the assembly accuracy of the guide bearing 9, the one that has the greatest influence on the positioning accuracy is the one with respect to the access direction of the carriage 5, as shown in Fig. 4.4 When the guide bearing 9 is assembled at an angle β It is. FIG. 4 is a partial plan view of the linear guide mechanism when the guide bearing 9 of FIG. 3 is viewed from above. The angle β in FIG. 4 is called a slip angle in the vehicle context, and if this angle exists, when an access operation is made in the direction of the carriage 5 in FIG. 4, the outer ring 12 of the guide bearing 9 will move in the direction of the arrow Proceed to.

This is because a frictional force acts between the outer ring 12 of the guide bearing 9 and the guide jl@16, and this frictional force causes the outer ring
12 moves in the direction of the inner ring shaft 14 with respect to the inner ring shaft 14 . The range in which the outer ring 12 moves is within the range of the axial clearance of the guide bearing 9 at most.

FIG. 5 is a partial sectional view of the guide bearing when the outer part 12 of the guide bearing 9 is displaced in the axial direction. This axial displacement of the outer ring causes the rolling elements 13 to move into the raceway groove 3 of the guide bearing 9.
1, and as a result, the distance between the inner race shaft 14 and the guideway 16 changes.

This change in distance changes the attitude of the carriage 5, so
This reduces the guiding accuracy of the linear guide mechanism. Changes in the posture of the carriage 5 affect the relative positions of the disk 1 and the head 3, and as a result, the positioning accuracy of the head 3 is adversely affected. In particular, in a magnetic disk device in which one head detects a position signal written on the disk 1 and positions a plurality of other heads, this effect is large and poses a serious problem of decreased positioning accuracy.

FIG. 6 is an enlarged view of the mounting angle adjusting member of the embodiment of the present invention shown in FIG. Further, FIG. 7 is an enlarged view of the inner race shaft 14 in FIG. 6. A part of the cylindrical surface of the inner ring shaft 14 is cut to provide a flat surface, and the angle adjusting member 17 and the inner ring shaft 14 are
By increasing the contact area of the inner ring shaft 14 and the angle adjustment member 17,
, the assembly of the carriage 5 is facilitated. The flat portions provided on the inner ring shaft 14 are provided at two axially symmetrical positions in the axial direction, and in this embodiment, the flat portions are provided at four locations in total. Then, the inner ring shaft 14 is tilted within the plane formed by these four angle adjusting members 17. Therefore, by arranging the angle adjustment member 17 as shown in FIG. 6, it becomes possible to adjust the mounting angle in the direction parallel to the plane of the paper in FIG.

FIG. 8 shows another embodiment of the present invention, in which the angle adjustment member 17 is arranged in a plane parallel to the guide surface of the guide path 16. With this arrangement, the angle at which the guide 1 and the bearing are attached to the traveling direction of the carriage 5 can be adjusted.

FIG. 9 shows another embodiment of the present invention, in which a pair of angle adjustment members 17 and a convex portion provided at the tip of the inner ring shaft 4 form a pivot bearing to adjust the installation angle of the guide bearing. I made it possible. This embodiment has the advantage of reducing the number of parts because it can function with a pair of angle adjustment members.

FIG. 10 shows another embodiment of the invention. In this embodiment, the angle adjustment members 17 are arranged at four locations within the same plane,
Further, a bearing mounting housing 19 is further provided outside the angle adjustment member 17.

When the guide bearing 9 of FIG. 10 is taken out, it becomes as shown in FIG. 11, in which the guide bearing 9, the angle adjustment member 17, and a bearing mounting housing 1927- for housing them are integrally constructed. According to the present invention, the guide bearing 9 can be integrated with the angle adjustment member 17 into the carriage 5, so assembly is easy, and the guide bearing can be assembled into a unit with the angle adjustment member incorporated. It has the advantage of being scalable.

FIG. 12 shows another embodiment of the present invention, in which a bearing sleeve 20 is further inserted between the inner race shaft 14 and the angle adjustment member 17 in the embodiment of FIG.

FIG. 13 shows only the bearing mounting housing 19, angle adjustment member 17, and bearing sleeve 20 shown in FIG. 12 taken out. According to this embodiment, there is an advantage that the angle adjustment member can be made into a unit. Further, since the guide bearing can be manufactured separately and combined, manufacturing becomes easy. Furthermore, since the angle adjustment member is unitized, assembly becomes easier. That is, the assembly is completed by simply assembling the unitized angle adjustment member into the carriage 5, and then the guide bearing, and so on.

8-FIG. 14 is another embodiment of the present invention. Figure 15 shows
A cross section taken along line II in FIG. 14 is shown. In this embodiment, the two pairs of angle adjustment members 17 are arranged not in the same plane but at an angle shifted by 90 degrees. In this way, the two pairs of angle adjustment members 1
7, in FIG. 14, it is possible to adjust the angle around the normal to the plane of the paper and the angle in the front-rear direction with respect to the plane of the paper.

For example, when only one pair of angle adjustment members is operated, the other pair of angle adjustment members becomes its rotation axis.

In this embodiment, two pairs of angle adjustment members are operated simultaneously. and angle adjustment around two axes at the same time. Also, if only the pair of angle adjustment members are operated, -
The angle around the axis can be adjusted.

FIG. 16 shows another embodiment of the invention. In this embodiment, the inner ring shaft of the guide bearing has a bimetal 21.22 structure to adjust the mounting angle of the bearing. Since the bearing itself has an angle adjustment function, the number of parts is small.
Assembly is also easy.

FIGS. 17(a) and 17(b) show a method of assembling the embodiment shown in FIG. The angle adjustment member 17 is
A case where it is configured with an electrostrictive element will be explained. Figure 17 (
As shown in a), the bearing mounting housing 19 in which the angle adjustment member 17 is previously assembled is installed in the carriage 5. No voltage is applied to this angle adjustment member 17. Next, install the guide bearing. At this time, there is a slight gap between the inner ring shaft of the guide bearing and the angle adjustment member 17, so after inserting the guide bearing, apply voltage to the angle adjustment member 17 as shown in FIG. 17(b). . The installation is now complete, and during operation, voltage is applied (positive or negative voltage) for angle adjustment.

FIG. 18 shows a method for adjusting the mounting angle before operation. A pre-recorded position signal is read while repeating a seek, and while determining the guiding accuracy, the voltage applied to each angle adjusting member is adjusted to cancel the installation error of the guide bearing.

As a result, a highly accurate linear guide mechanism is constructed.

FIG. 19 shows another embodiment of the invention. In this embodiment, an angle adjustment member 2 is provided between the guide path 16 and the housing 11.
By arranging 4, the installation angle caused by processing errors and assembly errors can be canceled by adjusting the inclination of the guide path. This embodiment is characterized by a simple configuration.

FIG. 20 shows another embodiment of the invention. In this embodiment, the bolt 28 is used to adjust the mounting angle, and an electric circuit for driving is not required, so that the structure is easy.

FIG. 23 shows another embodiment of the invention. In this embodiment, the liquid-sealed tube 32 is used as a bearing mounting angle adjusting member. The way it works is that by slightly squeezing the exposed part of the liquid-sealed tube 32 on the side where you want to tilt the bearing, internal pressure increases, and the part of the bearing in contact with the inner ring shaft expands, pushing the shaft to one side. . This allows adjustment of the mounting angle. Further, since the crushed portion by using the metal tube maintains its shape when crushed through plastic deformation, the adjusted mounting angle is also maintained. Therefore, if the 31-degree adjustment is performed, subsequent adjustment becomes unnecessary.

The protrusion 33 supports the bearing on the outer periphery of the shaft and serves as a fulcrum for adjusting the mounting angle. The liquid-tight tube 32 in FIG.
Three locations may be provided around the inner ring shaft of the bearing. In this case, the mounting angle can be adjusted in any direction.

FIG. 24 shows another embodiment of the present invention. In this embodiment, the resistance heating element 34 is used as a bearing mounting angle adjustment member. In this operation method, by energizing the resistance heating element 34 on the side opposite to the side on which you want to tilt the bearing, the area around the inner ring shaft of the bearing of the carriage 5 to which the resistance heating element 34 is attached is heated. By expanding and tilting, the mounting angle of the bearing is adjusted. This method is advantageous in that it is only necessary to attach the resistance heating element 34 externally, and the processing and assembly of the bearing mounting portion can be used without any changes. In addition, resistance heating 34
may be provided at three or more locations around the shaft. If you do this,
The mounting angle can be adjusted in any direction.

32 [Effects of the Invention] According to the present invention, the linear guide mechanism includes a movable body to which a bearing having a main shaft and an outer ring rotatably provided on the main shaft is attached as described above, and a movable body in contact with the outer ring. a pair of mounting angle adjusting members that are arranged parallel to the running surface of the guideway, and a mounting angle adjusting member that expands/contracts between the main shaft and the mounting hole of the movable body to which the main shaft is attached; By operating the main shaft to rotate parallel to the running surface, the rolling direction of the outer ring can be aligned with the direction of the guideway.Also, by operating a pair of mounting angle adjustment members installed perpendicular to the running surface, the main shaft can be rotated parallel to the running surface. By turning the main shaft perpendicular to the running surface, the main shaft and the guideway running surface are parallel to each other, smoothing the contact between the outer ring and the running surface, or preventing uneven contact, so that bearings, movable objects, etc. Processing errors and assembly errors can be canceled, and a highly accurate and reliable linear guide can be provided.

In addition, by placing a mounting angle adjustment member between the guideway and its support member and adjusting the inclination of the guideway running surface, processing errors and assembly errors of the guideway can be canceled, improving the accuracy of the linear guide. , which in turn can improve reliability.

Further, according to the present invention, another linear guide mechanism is configured to include a movable body having a bimetallic main shaft and a bearing having an outer ring rotatably provided on the main shaft, and a guide that guides the movable member by contacting the outer ring. The rolling direction of the outer ring can be corrected by making the bending direction of the bimetal parallel to the running surface of the guideway, and by making the bending direction of the bimetal perpendicular to the running surface, the contact between the outer ring and the running surface can be corrected. Since the condition can be corrected, processing errors of bearings and movable bodies, and their assembly errors can be canceled, improving the accuracy of linear guides.
As a result, reliability can be improved.

[Brief explanation of drawings]

Fig. 1 is a longitudinal cross-sectional view of a linear guide mechanism according to an embodiment of the present invention, Fig. 2 is a longitudinal cross-sectional view of a magnetic disk drive, Fig. 3 is a longitudinal cross-sectional view of a guide bearing, and Fig. 4 is a cross-sectional view of a guide bearing. side view,
FIG. 5 is a partial vertical cross-sectional view of a guide bearing, FIG. 6 is a vertical cross-sectional view of a linear guide mechanism according to another embodiment of the present invention, FIG. 7 is an enlarged view of the inner ring shaft in FIG. 6, and FIG. FIG. 9 is a longitudinal sectional view of a linear guide mechanism according to another embodiment of the invention, FIG. 9 is a sectional view of a guide bearing according to another embodiment of the invention, and FIG. 10 is a longitudinal sectional view of a linear guide mechanism according to another embodiment of the invention. Longitudinal cross-sectional view, Figure 11 is Figure 10
12 is a longitudinal sectional view of a guide bearing according to another embodiment of the present invention, FIG. 13 is a sectional view of the mounting angle member unit of FIG. 12, and FIG. 14 is a sectional view of the guide bearing according to another embodiment of the present invention. FIG. 15 is a longitudinal sectional view of a guide bearing according to another embodiment of the present invention, FIG. 15 is a sectional view taken along line 1-1 in FIG. ), (b) is a diagram showing how to assemble the angle adjustment member, FIG. 18 is a block diagram of the installation angle adjustment method, and FIG. 19 is a longitudinal sectional view of a linear guide mechanism according to another embodiment of the present invention. Fig. 20 is a longitudinal sectional view of a linear guide mechanism using bolts as attachment angle adjustment members, Fig. 21 is a partial sectional view of the guide bearing, Fig. 22 is a partial sectional view of the guide bearing, and Fig. 23 is a partial sectional view of the guide bearing. Another Example 35 - Longitudinal sectional view of a guide bearing according to an embodiment, FIG. 24 is a longitudinal sectional view of a guide bearing according to another embodiment of the present invention. 1...Disc, 2...Spindle motor, 3...
・Head, 4... Guide arm, 5... Carriage, 6... Magnet, 7... Voice coil, 8...
・Guideway, 9... Guide bearing, 10... Connecting member,
DESCRIPTION OF SYMBOLS 11... Base, 12... Outer ring, 13... Rolling element, 14... Inner ring shaft, 15... Oil seal, 16...
... Guide path, 17... Installation angle adjustment member, 18.
... Oil seal, 19... Bearing mounting housing, 2o... Bearing mounting housing, 21... Bimetal shaft, 22... Bimetal shaft, 23... Inner ring,
24...Guideway installation angle adjustment member, 25...Guideway fixing bolt, 26...Guideway fixing spring, 27...
・Preload bearing, 28... Adjustment bolt, 29... Drive circuit, 30... Control circuit, 31... Raceway groove, 32...
- Liquid sealed tube, 33... Protrusion, 34... Resistance heating element, 35... Power supply, 36... Wiring. 6

Claims (1)

[Scope of Claims] 1. A movable body equipped with a plurality of bearings as wheels having a main shaft and an outer ring rotatably provided on the main shaft, and a guide path in which the outer ring rolls into contact to guide the movable member. A linear guide mechanism comprising: a mounting angle adjusting member for adjusting an angle formed between the main shaft and the guide path. 2. The mounting angle adjusting member is a member that can be contracted/expanded by a signal, and the mounting angle adjusting member is provided between the main shaft and the mounting hole of the movable body into which the main shaft is inserted. The linear guide mechanism according to claim 1. 3. The attachment angle adjustment member is a member that can be contracted/expanded by a signal, and the attachment angle adjustment member is provided between the guide path and a support member that supports the guide path. 1. The linear guide mechanism described in 1. 4. The linear guide mechanism according to claim 2, wherein at least two mounting angle adjustment members are provided around the main shaft at at least two locations in the axial direction of the main shaft. 5. The linear guide mechanism according to claim 2, wherein a pair of said angle adjustment mechanisms are provided at least two locations in the axial direction of said main shaft, parallel to each other and axially symmetrical. 6. A pair of the mounting angle adjustment members are provided axially symmetrically at at least two locations in the axial direction of the main shaft, and one pair of the mounting angle adjustment members are arranged parallel to the running surface of the guideway, and the mounting angle of the other pair is adjusted in parallel to the running surface of the guideway. 3. The linear guide mechanism according to claim 2, wherein the adjusting member is positioned perpendicular to the running surface. 7. Claim 2, wherein the pair of mounting angle adjustment members are provided axially symmetrically at one location in the axial direction of the main shaft, and a pivot bearing is formed between the bottom surface of the mounting hole and the base end of the main shaft. Linear guide mechanism as described. 8. A linear guide mechanism comprising a movable body having a main shaft and an outer ring rotatably provided on the main shaft and a plurality of bearings attached as wheels, and a guide path in which the outer ring rolls into contact and guides the movable body. in which a cylindrical holding member is fitted into a mounting hole provided in the movable body and accommodating the main shaft;
A linear guide mechanism characterized in that an attachment angle adjustment member is provided between an inner circumferential surface of the holding member and the main shaft inserted into the holding member for adjusting an angle formed between the main shaft and the guide path. 9. A linear guide mechanism comprising a movable body having a main shaft and an outer ring rotatably provided on the main shaft and a plurality of bearings attached as wheels, and a guide path through which the outer ring rolls into contact and guides the movable body. In this step, a cylindrical first holding member is fitted into an attachment hole provided on the movable body and which accommodates the main shaft, and a cylindrical second holding member is fitted onto the outer diameter of the main shaft, and the first holding member is A linear guide mechanism characterized in that an attachment angle adjusting member is provided between an inner circumferential surface and an outer circumferential surface of the second holding member to adjust the angle formed between the main shaft and the guide path. 10. The linear guide mechanism according to claim 2, wherein the mounting angle adjusting member is a piezoelectric element. 11. A linear guide mechanism comprising a movable body having a plurality of bearings attached as wheels having a main shaft and an outer ring rotatably provided on the main shaft, and a guide path through which the outer ring rolls into contact and guides the movable body. A linear guide mechanism characterized in that the main shaft has a bimetal structure and is provided with a drive circuit for driving the bimetal.