JP2649743B2 - Linear motion guide device and assembly method thereof - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a linear motion guide device used for a linear guide portion of, for example, a machine tool or an industrial robot.

In particular, with the diversification of the linear motion parts of various machines, loads in all directions, that is, radial loads, horizontal loads, reverse radial loads, and moment loads are applied to the linear motion parts, and the loads are applied. The track base material and slide base material, which are raw materials for the size and direction, are shared, and have a contact angle adapted to the load direction so as to obtain the maximum life, rigidity and allowable load. The present invention relates to a linear motion guide device and an assembling method thereof.

BACKGROUND ART -First Conventional Example- As a linear motion guide device of this type, for example,
No. 199710.

As shown in FIG. 23, this linear motion guide device 30
Is configured to include a raceway 31 having a square cross section, a slide 32 having a recess 32c having a square cross section for receiving the raceway 31, and four rows of infinitely circulating balls 33. .

Two ball rolling grooves 31a are formed on the upper surface of the track base 31, and one ball rolling groove 31b is formed on each side surface. In the recess 32c of the slide table 32, two ball rolling grooves 32a and one ball rolling groove 31a are opposed to the two ball rolling grooves 31a and one ball rolling groove 31b of the track base 31, respectively. Ball rolling groove 32b
Are formed. The opposing ball rolling grooves 31a, 32a are
It is a shallow arc-shaped groove slightly larger than the ball, and the opposing ball rolling grooves 31a, 32a are Gothic arc-shaped grooves.

The retainers 34 and 35 are provided to prevent the balls 33 from falling off when the slide 32 is removed from the track base 31.

The contact angle of the linear motion guide device 30 is substantially perpendicular to the upper two rows of balls, and the lower two rows of balls are inclined obliquely upward in a ball rolling groove formed by combining two arcs. And at approximately four lower locations (hereinafter, referred to as "complete four-point contact"). As described above, the linear motion guide device 30 supports the load from above with the two circular arc-shaped ball rolling grooves 31a and 32a,
Gothic arc ball rolling groove for lateral load
Since it is supported by complete four-point contact at 31b and 32b, it has excellent load supporting capacity both for loads from above and loads from the lateral direction.

Second Conventional Example On the other hand, Japanese Utility Model Publication No. 63-24258 discloses another type of linear motion guide device 40.

As shown in FIG. 24, this linear motion guide device 40
Is configured to include a rail 41 having a rectangular cross section, a slide 42 having a recess 42c having a rectangular cross section for receiving the rail 41, and four rows of infinitely circulating balls 43. .

On each side of the way 41, two ball rolling grooves 41a are formed, and in the recess 42c of the slide 42, the ball rolling groove 41a of the way 41 faces the ball rolling groove 41a, A total of four ball rolling grooves 42a are formed. These opposing ball rolling grooves 41a, 42a are Gothic arc-shaped grooves, and the contact angle in each ball row is approximately 45 degrees with respect to the horizontal.

In the linear motion guide device 40, the interval A between the two ball rolling grooves 41a, 41a formed on each side surface of the track base 41 is set to the corresponding two ball rolling grooves 42a, By making it larger or smaller than the interval B of 42a, the intersection of the contact angles in each ball row on each side of the way 41 is
Intersect outside the way 41 (hereinafter, referred to as “DB structure”) or intersect inside the way 41 (hereinafter, referred to as “DB structure”).
"DF structure").

In any case, in the linear motion guide device 40, when the vertical load applied thereto is small, the load is supported by a total of two rows of balls on one side, and when the vertical load is large, a total of four rows of balls are provided on one side. To support the load. As described above, by increasing the number of ball rows that support the load under a high load, the load on the ball rolling grooves is reduced, and the life of the linear motion guide device 40 is extended.

-Third conventional example- Further, a linear motion guide device provided with two rows of balls on the upper surface side of the way and two rows of balls on each of the left and right sides of the way, providing a total of six rows of balls. For example,
There is one described in JP-A-62-141308.

As shown in FIG.
Reference numeral 0 denotes a track 101, a slide 102 having a recess 102d for receiving the track 101 and linearly guided along the track 101, and freely rolling between the slide 102 and the track 101. And six rows of infinitely circulating balls 103 interposed.

The way 101 has two sets of ball rolling grooves 101a on the upper surface.
Are formed, and a pair of ball rolling grooves 101b and 101c are formed on each side surface in two lines. On the other hand, the ball rolling groove 1 of the track base 101 is provided on the upper surface and each side surface of the recess 102d of the slide base 102.
Ball rolling grooves 102a, 102b, 102c corresponding to 01a, 101b, 101c
Are formed.

Then, when the slide 102 is pulled out from the way 101, the ball
In order to prevent the 103 from falling off, retainers 107 and 108 are respectively provided on the two rows of balls 104 formed on the upper surface and the two rows of balls 105 and 106 formed on each side surface.

The contact angle of the ball 4 in the linear motion guide device 100 is an angle based on the horizontal line of the contact line of the ball 103 in the ball rolling groove 101a of the track 101 in the two rows of balls 104 formed on the upper surface. The contact angle α is set at 90 degrees, and the upper row of ball rolling grooves 101b and the lower row of ball rolling grooves 101c are formed in the two rows of balls 105, 106 formed on each side surface.
The angle of contact of the contact line of the ball 103 with respect to the horizontal line, the contact angle β is inclined upward and downward toward the inside of the track 101 45
And the intersection of both contact lines is located outside the track 101.

The linear motion guide device 100 configured as described above has a vertical load acting on the slide table 102 from above with two ball rows 104 on the upper surface and two ball rows 106 on the lower row on each side.
Are supported by a total of four rows of balls 104 and 106.

The lateral load acting from the left and right depends on the direction of the load, and the upper and lower two rows of ball rows 105, 1 on either side.
The longitudinal direction, supported by 06 and acting from below,
The load in the so-called lifting direction is supported by the upper two rows of ball rows 105 on each side.

-Fourth conventional example- Also, Japanese Patent Application Laid-Open No. 64-53621 discloses another type of linear motion guide device 200 having six rows of balls.

As shown in FIG.
Reference numeral 0 denotes a rail 201, a slide 202 having a recess 202d for receiving the rail 201, and being linearly guided along the rail 201, and freely rolling between the slide 202 and the rail 201. And six rows of infinitely circulating balls 203 interposed.

On each side surface of the way 201, three ball rolling grooves 201a are formed. In the recess 202a of the slide table 202, three ball rolling grooves 202a, 202b, 202c corresponding to the three ball rolling grooves 201a, 201b, 201c of the track base 201 are formed.

When the slide 202 is pulled out of the way 201, the ball
In order to prevent the 203 from falling off, a retainer 207 is provided on each of the three rows of balls 204, 205, and 206 formed on each side surface.

The contact angle of the ball 203 in the linear motion guide device 200 is determined by the three rows of balls 204, 205, and 206 on each side surface.
The upper and middle stages are inclined downward toward the inside of the way 201, and the lower stage is inclined upward toward the inside of the way 201, and each is set to approximately 45 degrees, and the contact line L1 at the contact angle of the upper, middle, and lower stages, Tracks 20 at intersections O1 and O2 of L2 and L3
It is located inside 1.

The linear motion guide device 200 configured as described above includes the contact lines L1 and L2 of the balls 203 of the upper and middle ball rows 204 and 205.
However, since both extend diagonally downward toward the inside of the way 201, the radial load acting on the slide table 202 from above is received by the upper row and the interrupted ball rows 204, 205, and the inverse radial load in the floating direction is Lower row of balls 20
You will receive it at 6. Therefore, the rigidity with respect to the radial load is higher than the reverse radial load. Here, rigidity refers to a performance that is not easily deformed by the load acting between the slide base and the track base and does not rattle, and in the case of this conventional example, the radial The rigidity with respect to the load F in the direction is increased to increase the ability to load heavy loads.

-Fifth conventional example-Also, in Japanese Patent Application Laid-Open No. 64-53622, in the above-mentioned linear motion guide device 200, as shown in FIG. , Contact angle line L2
1, L22 is almost downward and upward toward the inside of the way 201.
Linear motion guide device with contact structure that crosses at 45 degrees
200 'is disclosed.

The linear motion guide device 200 'thus configured supports the radial load F by the upper row of balls 204, and supports the reverse radial load f by the lower row of balls 206.

On the other hand, since the ball row 205 in the middle stage is in four-point contact, it is configured to apply loads in both directions of a radial load and a reverse radial load.

By the way, in the linear motion guide devices of the first to fifth conventional examples described above, various ratios of load supporting capacity are required for loads from four directions (up, down, left, and right). For example, various performances are required for loads in each direction, such as causing vibrations to be attenuated or causing light movement for high-speed operation.

However, the above-described linear motion guide device is of a type adapted to only one of various aspects required for this type of linear motion guide device, and cannot respond to these various functional requirements.

Conventionally, the shape of the way and the slide table, the number of balls and the contact angle are selected according to the application, and the linear motion guide device is designed, manufactured and supplied to meet the required performance. I was If the manufacturer responds to the customer's request in such a manner, the types of linear motion guide devices are increased, and there is a disadvantage that mass production is lacking and productivity is poor.

The present invention has been made in view of the problems of the related art, and forms a ball rolling groove having an optimal contact angle by changing a pitch between ball rolling grooves of a track and a slide in accordance with a load condition. Accordingly, an object of the present invention is to provide a linear motion guide device having performance adapted to loads in each direction and a method of assembling the same.

DISCLOSURE OF THE INVENTION The present invention provides a track, a slide having a recess for receiving the track, and being linearly guided along the track, and a rolling base between the slide and the track. The track is provided with at least one ball rolling groove on an upper surface and at least one ball rolling groove on both side surfaces, A linear motion guide device comprising a ball rolling groove corresponding to the ball rolling groove on the upper surface and both side surfaces of the track base on the upper surface and both side surfaces of the recess, The ball rolling grooves on one of the upper surface and both side surfaces, the corresponding positional relationship of the groove center with respect to the corresponding ball rolling groove of the track base or the slide base is the same or deviated. Tracks or slides with the same or deviated correspondence It is characterized in that it is mounted on an opposing track or slide in any combination.

It is characterized in that two ways of ball rolling grooves are provided on the upper surface of the way, and one ball rolling groove is provided on each of the left and right side surfaces of the way.

It is characterized in that two sets of ball rolling grooves are provided on the upper surface of the way, and two sets of ball rolling grooves are provided on both sides.

The cross section of the way is square, and 2
Changing the distance between the ball rolling grooves of the strip and the distance between the ball rolling grooves formed on the upper surface and each side surface with respect to the distance between the corresponding ball rolling grooves of the slide table. Thus, the center positions of the corresponding ball rolling grooves of the track base and the slide base are identical or deviated in the corresponding positional relationship.

The ball rolling groove has a depth that allows the ball contact angle to be freely selected.

The depth of the ball rolling groove is approximately 1/4 to 1/2 of the ball diameter.

The ball rolling groove formed on the upper surface of the way and the rolling groove of the sliding table opposed to the ball form an arc shape slightly larger than the ball, and at least the ball formed on each side surface of the way. The rolling groove and the ball rolling groove of the slide table facing the rolling groove are formed by combining two arcs.

The ball rolling groove formed on the upper surface of the way and the rolling groove of the sliding table facing the same, and the ball rolling groove formed on each side surface of the way and the sliding table facing the same. Each of the ball rolling grooves has an arc shape slightly larger than the ball.

Ball rolling groove formed on the upper surface of the way and the ball rolling groove of the sliding table facing the same, and ball rolling groove formed on each side surface of the way and the sliding table facing the same Are characterized in that each of the ball rolling grooves has a shape obtained by combining two arcs.

The ball rolling groove formed on the upper surface of the way and the ball rolling groove of the sliding table opposed thereto have a shape formed by combining two arcs, and the ball rolling groove formed on each side surface of the way is provided. The dynamic groove and the ball rolling groove of the slide table opposed thereto have an arc shape slightly larger than the ball.

The contact angle of a ball interposed between a pair of ball rolling grooves on two surfaces corresponding to each other on the upper surfaces of the track base and the slide base is 90 degrees with respect to the horizontal, and The contact angle of the ball interposed between a pair of ball rolling grooves on two sides corresponding to each other on both sides is approximately 45 degrees inclined upward toward the inside of the way relative to the horizontal. I do.

The contact angle of the ball interposed between a pair of ball rolling grooves on two sides corresponding to each other on both sides of the track base and the slide base is made substantially 0 degree with respect to the horizontal, The contact angle of the ball interposed between a pair of ball rolling grooves in the two rows corresponding to each other on the upper surface of the table is substantially 90 degrees with respect to the horizontal.

All the ball rolling grooves formed on the raceway and the slide have a single arc shape slightly larger than the ball, and at least one of the ball rolling grooves has a radius of curvature of a groove cross section that is equal to the diameter of the ball. It is characterized by being set to a range smaller than 0.52.

The radius of curvature of the ball cross-section of the ball rolling groove is set to 0.
It is characterized by being set to about 51.

The method for assembling a linear motion guide device according to the present invention includes the steps of forming a first member having a first ball rolling groove on an upper surface and second ball rolling grooves on both left and right side surfaces. A second member slidably assembled via a predetermined number of rows of balls, wherein the corresponding positional relationship of the groove center is the same or deviated with respect to the first ball rolling groove of the first member. A third ball rolling groove provided;
Forming a plurality of second members having a fourth ball rolling groove provided with the same positional relationship of the groove center being the same or deviated from the second ball rolling groove of the first member; A step of selecting a combination of the first member and a plurality of types of second members so as to have a contact angle suitable for a load and a moment load in each direction, respectively.

A pair of first ball rolling grooves spaced apart by a first pitch in the width direction; and a pair of second ball rolling grooves separated by a second pitch in the height direction from the first ball rolling grooves. Forming a first member comprising: a second member slidably assembled to the first member via four rows of balls, the third member being different from the first pitch in a width direction. And a pair of fourth ball rolling grooves spaced apart from the third ball rolling groove by a fourth pitch different from the second pitch in the height direction. Forming a plurality of types of second members provided with the first and third pitches and the second pitch so as to have contact angles suitable for loads in each direction and moment loads, respectively.
And a step of selecting a combination of fourth pitches.

The ball rolling groove has a depth that allows the ball contact angle to be freely selected.

Also, make the depth of the ball rolling groove approximately 1/4 to 1/2 of the ball diameter.
A rail having a rectangular cross section and a recess for receiving the rail.

In the linear motion guide device of the present invention, the ball rolling groove may have an arc shape slightly larger than the ball, or may have a Gothic arc shape, but the depth of the groove is substantially equal to the ball diameter when the angular displacement of the contact angle is small. From / 4, it is approximately 1/2 of the ball diameter when the angular displacement of the contact angle is large. Therefore, the ball comes into contact with somewhere in the arcuate ball rolling groove, so that substantially all contact angles conventionally used in this type of linear motion guide device can be taken. .

The contact angle in each ball rolling groove is determined by the pitch (distance) between the two ball rolling grooves formed on the upper surface of the track base and the pitch between the ball rolling groove and the ball rolling groove formed on each side surface. (Distance) is arbitrarily set by variously changing the pitch (distance) between the corresponding ball rolling grooves of the slide table.

In particular, when the ball rolling groove has an arc shape slightly larger than the ball, the contact angle is not limited to 45 degrees with respect to the horizontal, but can be substantially any angle.

In addition, in the case where the ball rolling groove has a shape in which two arcs are combined, for the first time when the load exceeds a desired load, or
From the beginning, it can be set so that the ball comes into contact with each ball rolling groove at two points to cause differential slip.

Since the balls are interposed between the ball rolling grooves on the upper side of the way and the ball rolling grooves on the side surface and the corresponding ball rolling grooves on the slide, there is a gap between the ball rolling grooves. The rigidity of the linear motion guide device can be increased by providing a preload with a slightly larger ball interposed.

Further, since two deep ball rolling grooves are formed in the upper part of the recess of the slide, the thickness of the upper part of the slide can be increased. For this reason, the rigidity of the block of the slide table can be increased.

Further, since one ball rolling groove is formed on each of both inner side surfaces of the concave portion of the slide table, the length of the side surface portion of the slide table can be shortened. Increases rigidity. For this reason, the total height of the slide block can be reduced, and the height of the way can also be arranged with the ball position on the side at the top, so the overall height of the linear motion guide device is low and compact. can do.

In particular, if the depth of the ball rolling groove is set to about 51% of the ball diameter even in a gothic arch groove or circular arc groove, when a load applied during heavy cutting is applied, the operating slip increases, and rolling and slipping increase. Rolling motion is similar to sliding motion because of mixed motion, damping effect (damping)
Is improved. Therefore, when using machine tools, etc.,
Even during heavy cutting, the amount of chatter can be reduced as much as possible, and the processing accuracy can be improved. In particular, it is effective if the contact angle between the ball rolling groove on the upper surface on which the load of heavy cutting acts and the ball is 90 degrees.

Further, if the depth of the ball rolling groove is set to about 51% of the ball diameter, the ball contact area becomes larger (closer to the roller) than a normal circular arc groove, and the contact angle configuration is synergistic. In addition, the load capacity of heavy loads is dramatically increased, and a highly rigid and stable linear motion can be obtained.

The movement at the time of heavy cutting is slow, and even if a slight slip occurs, the life is not significantly affected. Further, since the operation slip increases in proportion to the load, an extremely rational contact structure is obtained.

BRIEF DESCRIPTION OF THE DRAWINGS FIGS. 1 to 13 show the present invention applied to a linear motion guide device having four rows of balls, and FIG. 1 is a partially cutaway perspective view of one embodiment.

 FIG. 2 is a cross-sectional view of FIG.

FIG. 3 is an explanatory diagram for explaining the positional relationship of the ball rolling grooves in the linear motion guide device of FIG.

FIG. 4 is a diagram illustrating an example of a machine tool to which the linear motion guide device is applied.

FIG. 5 is an explanatory diagram of various loads acting on the linear motion guide device.

FIG. 6 is an explanatory diagram of the linear motion guide device according to the first embodiment of the present invention.

FIG. 7 is an explanatory diagram of a linear motion guide device according to a second embodiment of the present invention.

FIG. 8 is an explanatory view of a linear motion guide device according to a third embodiment of the present invention.

FIG. 9 is an explanatory diagram of a linear motion guide device according to a fourth embodiment of the present invention.

FIG. 10 is an explanatory diagram of a linear motion guide device according to a fifth embodiment of the present invention.

FIG. 11 is an explanatory diagram of a linear motion guide device according to a sixth embodiment of the present invention.

FIG. 12 is an explanatory diagram of a linear motion guide device according to a seventh embodiment of the present invention.

FIG. 13 is an explanatory diagram of a linear motion guide device according to an eighth embodiment of the present invention.

FIG. 14 is an explanatory diagram of differential slip in the case of a gothic arch groove.

FIG. 15 is an explanatory diagram of differential slip in the case of a circular arc groove.

FIG. 16 is a view showing another example of the contact angle structure of the four ball rows.

17 to 21 show the present invention applied to a linear motion guide device having six rows of balls. FIG. 17 is an explanatory view of a linear motion guide device according to a ninth embodiment.

FIG. 18 is a partially broken perspective view showing the basic configuration of the linear motion guide device having the six rows of balls shown in FIG.

FIG. 19 is an explanatory diagram of a linear motion guide device according to a tenth embodiment of the present invention.

FIG. 20 is an explanatory diagram of a linear motion guide device according to an eleventh embodiment of the present invention.

FIG. 21 is an explanatory diagram of a linear motion guide device according to a twelfth embodiment of the present invention.

FIGS. 22 (a) to 22 (c) are diagrams showing other examples of various contact angle structures of the linear motion guide device having six rows of balls.
(D), (e) is a figure which shows the other example of a ball row structure.

FIG. 23 to FIG. 27 are cross-sectional views of various configuration examples of a conventional linear motion guide device.

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, a linear motion guide device according to the present invention will be described in detail with reference to the drawings.

1 and 2 are cross-sectional views of one embodiment of the linear motion guide device according to the present invention.

The linear motion guide device 10 according to the present invention generally includes a rail 11 having a rectangular cross section, and a recess 12 for receiving the rail 11.
The slide table 12 has a plurality of balls 13 rotatably interposed therebetween.

The slide table 12 includes a slide table block 14 having high rigidity and side covers 15 fixed to both end surfaces of the slide table block 14.

Two ball rolling grooves 11a are formed on the upper surface of the way 11, and one rolling groove 11b is formed on each of the side surfaces. On the other hand, the recess 12c of the slide base block 14
The ball rolling grooves 12a and 1b are located at positions facing the respective rolling grooves 11a and 11b.
2b and a ball escape hole 16 are formed. On the side cover 15,
A direction change path 17 is provided to connect both ends of the ball passage in the load area and both ends of the ball relief hole 16 between the opposing ball rolling grooves 11a, 12a and 11b, 12b.

Further, in this example, the track base 11 is
No retainer is provided to prevent the ball 13 from falling off when the ball is pulled out.

Each of the opposing rolling grooves 11a, 12a and 11b, 12b is a combination of two circular arcs as shown in FIG. 14, even when the cross-sectional shape as shown in FIG. 15 is a so-called circular arc shape having a single circular arc. It may have a so-called Gothic arch shape, but the depth is set to a depth at which the ball contact angle can be freely selected. In this embodiment, the depth of the ball rolling groove is set to almost half of the ball diameter. As a result, the ball 13 has a substantially semicircular ball rolling groove 11a,
Since it comes into contact with any of 12a and 11b, 12b, substantially all contact angles conventionally used in this type of linear motion guide device can be taken.

In particular, when the ball rolling groove has an arc shape slightly larger than the ball, the contact angle is not limited to 45 degrees with respect to the horizontal, but can be substantially any angle. When the variation of the contact angle is small, the ball rolling groove does not need to be approximately half of the ball diameter, and may be approximately / 4 of the ball diameter.

On the other hand, for example, in the case of the ball on the upper surface side of the conventional linear motion guide device 30 shown in FIG. 23, the contact angle other than the vertical direction is not originally targeted, but even if the contact angle other than the vertical is targeted, Since the ball rolling grooves 31a and 32a are arc-shaped grooves slightly larger than the shallow balls, the contact points of the balls with the ball rolling grooves are near the edges of the ball rolling grooves. Therefore, the contact stress is extremely high at the edge, and there is a possibility that the rolling surface is broken.

In this linear motion guide device 10, as shown in FIG. 3, the pitch (distance) B1 between two ball rolling grooves formed on the upper surface of the track base 11 and the pitch (distance) B1 formed between the ball rolling grooves and each side surface. The pitch (distance) B2 + B3 between the ball rolling grooves to be rotated is the pitch (distance) A1, A2, A3 between the corresponding ball rolling grooves on the slide.
6 to 13 by variously changing
The linear motion guide device having various contact angles as shown in (1) and (2) is provided, and has a performance adapted to a load in each direction. FIGS. 6 to 13 schematically show only the way, the ball, and the contact angle for the sake of clarity. The direction of the contact angle is indicated by an alternate long and short dash line in the figure, and this line is a line connecting between the ball contact portions with the opposing ball rolling grooves, and is hereinafter referred to as a contact angle line.

In all of the illustrated examples, as shown in FIG. 5, basically, a radial load PR in a direction in which the slide table 12 is pressed against the track table 11 from above, and the slide table 12 is lifted upward from the track table 11. Reverse radial load PL acting in the direction
The load in any direction orthogonal to the axial direction of the way 11 is represented by a four-directional load PT, which is a lateral load PT acting from the left and right sides. In addition, a moment Mc about the trajectory eleventh axial direction Z, a moment Mb about the vertical axis Y, and a moment MA about the horizontal axis X can be basically received, but it is necessary to appropriately select a contact angle. Thus, the rigidity in each direction is relatively changed in accordance with the specific load acting direction.

In the case of the linear motion guide device 40 shown in FIG. 24,
By making the interval A larger or smaller than the interval B, the contact structure becomes a DB structure or a DF structure, but the contact angle itself remains unchanged at approximately 45 degrees. Therefore, in the case of this linear motion guide device 40, the load supporting capacity in the horizontal direction with respect to the vertical direction is arbitrarily changed, etc.
It cannot be made to have the performance adapted to the load in each direction.

FIG. 6 shows a linear motion guide device according to a first embodiment of the present invention.

In this embodiment, two ball rolling grooves 11a formed on the upper surface of the way 11 and the ball rolling grooves 12a of the slide 12 facing the same, and one ball formed on each side face of the way 11.
The ball rolling groove 11b of the strip and the ball rolling groove 12b of the slide base 12 opposed thereto have a circular arc shape having a single arc shape having a depth of almost half of the ball diameter.

The contact angles in the upper row of balls are oriented substantially vertically, and the contact angle lines in the lower row of balls intersect each other at approximately 45 degrees with respect to the horizontal and above the position of the ball rows. .

This linear motion guide device is suitable for high-speed operation because it has a large load supporting capacity against a main load from above (radial load) and has a design with little so-called differential slip. That is, in this case, the radius of curvature of the groove section of the ball rolling grooves 11a, 12a; 11b, 12b is set to a normal size of about 0.52 of the diameter of the ball, and the differential slip is set in a small range. It is.

Further, to make the radius of curvature of the ball rolling groove having the circular arc shape close to the ball radius so as to be substantially equal to the ball rolling groove pitch (distance) A1 to
Even if A3 and B1 to B3 are slightly changed, there is an effect that linear motion guide devices having various contact angles can be obtained.

In addition, the differential sliding means that the ball contacts the ball rolling groove in an arc shape, and the inner contact diameter and the outer contact diameter of the arc-shaped ball contact surface are different, so that when the ball rotates, As shown in Fig. 14, slip on the surface
In the case of a gothic arch-shaped ball rolling groove combining two arcs, four-point contact occurs and the rolling of the ball due to the four-point contact has a large difference between the inner contact diameter d1 and the outer contact diameter d2 in rotation. When a rolling motion is performed about the axis X, the difference between the inner contact point C and the outer contact point D increases,
A large slip occurs between the ball outer peripheral surface and the ball rolling groove. As a result, the ball rolls while sliding, and the rolling resistance at the time of ball rolling increases, and the sliding table 12
When the robot moves along the way 11, a large frictional resistance acts. Here, E in the figure represents the shape of the area where the ball and the rolling groove are in contact.

In this regard, as shown in FIG. 15, when the ball rolling groove has a circular arc shape having a single circular arc, the contact width a at the two-point contact is smaller than that of the Gothic arch shape. The ball performs a good rolling motion with small slip.

Referring to FIG. 7, there is shown a linear motion guide device according to a second embodiment of the present invention.

Also in this embodiment, the two ball rolling grooves 11a formed on the upper surface of the way 11 and the ball rolling grooves 12a of the sliding table 12 opposed thereto, and the 1
The ball rolling groove 11b of the strip and the ball rolling groove 12b of the slide base 12 opposed thereto have a circular arc shape having a depth almost half of the ball diameter.

The contact angle in the upper row of balls is substantially vertical, and the contact angle in the lower row of balls is substantially horizontal.

This linear motion guide device has a large load supporting capacity with respect to a lateral load which is a main load, and is designed to reduce so-called differential slip, so that it is suitable for high-speed operation.

In addition, when a track with a contact angle of FIG. 7A and a slide are combined and a preload is applied to the ball between the ball rolling grooves,
As shown in FIG. 7B, the contact angle of the ball changes in a direction sandwiching each other, and a preload is applied to the ball in the rotation direction when the slide table is viewed from the axial direction. A rigid linear motion guide device with no gap is obtained.

Referring to FIG. 8, there is shown a linear motion guide device according to a third embodiment of the present invention.

Also in this embodiment, the two ball rolling grooves 11a formed on the upper surface of the way 11 and the ball rolling grooves 12a of the sliding table 12 opposed thereto, and the 1
The ball rolling groove 11b of the strip and the ball rolling groove 12b of the slide base 12 opposed thereto have a circular arc shape formed of a single circular arc having a depth nearly half the ball diameter.

In the embodiment of FIG. 5, the contact angles in the upper row of balls are approximately 45 degrees with respect to the horizontal and cross each other above the position of the row of balls, and the contact angles in the lower row of balls are different. Also point in a direction substantially parallel to the contact angle in the upper row of balls.

This linear motion guide device has a large load supporting capacity against a load from the bottom (reverse radial load), and is designed to reduce so-called differential slip, so that it is suitable for high-speed operation.

When a raceway with a contact angle of FIG. 8A and a slide are combined and a preload is applied to the ball between the ball rolling grooves,
As shown in FIG. 8B, the contact angle of the ball changes in a direction sandwiching each other, and a preload is applied to the ball in the rotation direction when the slide table is viewed from the axial direction. A rigid linear motion guide device with no gap is obtained. The application of the preload can be obtained by setting the distance between the opposing ball rolling grooves and the ball diameter to be smaller. That is, when a preload is applied to the balls on the left and right sides, the raceway shrinks horizontally and slightly deforms in the direction due to the compression reaction force of the balls, and the slide base slightly deforms in the direction extending in the horizontal direction. Changes.

Referring to FIG. 9, there is shown a linear motion guide device according to a fourth embodiment of the present invention.

In this embodiment, two ball rolling grooves 11a formed on the upper surface of the track base 11, the ball rolling grooves 12a of the slide base 12 opposed thereto, and one ball forming groove formed on each side surface of the track base 11. The ball rolling groove 11b of the strip and the ball rolling groove 12b of the slide base 12 opposed thereto have a circular arc shape having a depth almost half of the ball diameter.

In the embodiment of FIG. 9, the contact angles in the upper row of balls are each inclined inwardly with respect to the horizontal and intersect each other below the ball rolling grooves. The contact angles are respectively inclined upward with respect to the horizontal and cross each other above the ball rolling grooves.

This linear motion guide device has a large load supporting capacity for loads in all directions, that is, radial load PR, horizontal lateral load PT, and reverse radial load PL from below. It is suitable for high-speed operation.

Referring to FIG. 10, there is shown a linear motion guide device according to a fifth embodiment of the present invention.

In this embodiment, the two ball rolling grooves 11a formed on the upper surface of the track base 11 and the ball rolling grooves 12a of the sliding base 12 opposed thereto have a cross-section having a depth of almost half the ball diameter. It is a circular arc groove with a single arc shape,
Also, one ball rolling groove 11b formed on each side surface of the raceway 11 and the ball rolling groove 12b of the slide base 12 opposed thereto.
Has a shape obtained by combining two arcs having a depth of almost half of the ball diameter.

In the embodiment of FIG. 10, as in the embodiment of FIG. 8, the contact angles in the upper row of balls are each approximately 45 degrees with respect to the horizontal and cross each other above the position of the row of balls, and The contact angle of the lower row of balls is also substantially parallel to the contact angle of the upper row of balls.

This linear motion guide device is suitable for high-speed operation because it has a large load supporting capacity against a load from below (reverse radial load), which is a main load, and has a design with little so-called differential slip.

Referring to FIG. 11, there is shown a linear motion guide device according to a sixth embodiment of the present invention.

Also in this embodiment, the two ball rolling grooves 11a formed on the upper surface of the track base 11 and the ball rolling grooves 12a of the sliding base 12 opposed thereto have a circular shape having a depth almost half of the ball diameter. One ball rolling groove 11b formed on each side surface of the track base 11 and the ball rolling groove 12b of the sliding base 12 opposed to the ball rolling groove 11b have an arc shape. It has a Gothic arc shape having a depth.

In the embodiment of FIG. 11, as in the embodiment of FIG. 6, the contact angle in the upper row of balls is substantially vertical, and the contact angle in the lower row of balls is approximately 45 degrees with respect to the horizontal. And they cross each other above the position of the ball row.

This linear motion guide device has a large load supporting capacity against a main load (radial load) which is a main load. When a large radial load is applied to the linear motion guide device, four-point contact is made in the lower row of balls as shown in FIG.

As a result, a so-called differential slip is generated to attenuate the mechanical vibration generated when the workpiece W of the machine tool is cut by the tool TO, for example, as shown in FIG. And dimensional accuracy can be improved. In addition, the ball screw mechanism S for driving the linear motion guide device 10 and a motor M as a driving source thereof serve as a damper or a buffer. FIG. 4 shows an example in which a linear motion guide device 10 according to the present invention is used in a motion guide section of a top table T for transporting a workpiece W.

Referring to FIG. 12, there is shown a linear motion guide device according to a seventh embodiment of the present invention.

In this embodiment, the two ball rolling grooves 11a formed on the upper surface of the track base 11 and the ball rolling grooves 12a of the slide base 12 opposed thereto have a Gothic having a depth almost half the ball diameter. One ball rolling groove 11b formed on each side surface of the track base 11 and the ball rolling groove 12b of the sliding base 12 opposed to the ball rolling groove 11b have an arc shape. It has a circular arc shape having a depth.

In the embodiment of FIG. 12, the contact angle in the upper row of balls is approximately 45 degrees with respect to the horizontal and intersects each other above the position of the ball row, and the contact angle in the lower row of balls. Is oriented almost horizontally. When a large horizontal load is applied to this linear motion guide device,
As shown in FIG. 12 (b), four ball contacts are made on one ball row on the upper surface of the track base. As a result, so-called differential slip occurs, damping the machine vibration caused by cutting the workpiece of the machine tool, improving the finished roughness of the workpiece and improving the dimensional accuracy, and driving the linear motion guide device. Ball screw machine, and a damper or a damping means for a motor as a driving source thereof.

Referring to FIG. 13, there is shown a linear motion guide device according to an eighth embodiment of the present invention.

In this embodiment, two ball rolling grooves 11a formed on the upper surface of the way 11 and the ball rolling grooves 12a of the slide 12 facing the same, and one ball formed on each side face of the way 11.
The ball rolling groove 11b of the strip and the ball rolling groove 12b of the slide base 12 opposed thereto have a Gothic arc shape having a depth of almost half the ball diameter.

In the embodiment of FIG. 13, when a large downward load is applied to the slide base 12, the balls sandwiched between the pair of ball rolling grooves 11a, 12a move the opposing ball rolling grooves formed on the raceways 11 and 12. A total of four points are brought into contact with the moving grooves.

As a result, a large downward load can be received,
Suitable for machine tools requiring relatively heavy cutting and heavy grinding, such as NC machine tools and machining centers.

Further, since the ball completely contacts the ball rolling grooves 11a, 12a formed on the raceway base 11 and the slide base 12 with four points or sub-points with a bias in the manner of contact, the ball always slides sufficiently. Resistance is obtained. Since the sliding resistance increases in accordance with the magnitude of the downward load, the ball screw mechanism that moves the slide table 12 while receiving the cutting or grinding load does not directly receive the load. Therefore, there is no disadvantage that the conventional apparatus has such that the ball screw mechanism is relatively quickly damaged by heavy cutting or heavy grinding.

In the examples of FIGS. 11 to 13 described above, the ball rolling grooves are formed in a Gothic arch shape composed of a combination of two arcs as shown in FIG. 14, and differential friction is obtained by four-point contact when a heavy load is applied. However, as shown in Fig. 15, even in a circular arc shape composed of a single arc, the differential slip is increased by making the radius of curvature of the groove cross section closer to the radius of curvature of the ball, and sliding. Resistance can be increased.

In this case, the radius of curvature R of the ball rolling groove is preferably set to a range smaller than approximately 0.52 of the diameter Da of the ball. However, if the radius of curvature R is too small, the friction becomes too large, which impairs the light movement, which is a characteristic of the rolling guide device, so that it is preferable to set the radius to the range of 0.52 to 0.505, particularly about 0.51. Is preferably set to.

In general, in the case of a rotary type rolling bearing, the radius of curvature of the cross section of the ball rolling groove is determined by reducing the rolling friction of the surface on which the ball rolls, especially to prevent heat generation during high-speed rotation. The diameter of the ball is about 0.52 to 0.54. In other words, when the radius of curvature of the ball rolling groove approaches 0.5 of the ball diameter, the contact width of the ball with the ball rolling groove increases, so that the differential slip between the center and the end of the contact width increases. Therefore, the frictional resistance is increased and the calorific value is also increased. Therefore, it is usually set to about 0.52 or more.

Also, in the case of the thrust ball re-bearing, the cross-sectional radius of curvature of the inner race of the ball rolling groove and the ball rolling groove of the outer race is set to about 0.54 of the ball diameter.

The linear rolling guide is also an extension of this idea,
It is customary to use a so-called circular arc groove whose cross section has a single circular arc shape as the groove shape of the ball rolling groove, and use a radius of curvature of 0.52 to 0.54 of the ball diameter to minimize the increase in frictional resistance as much as possible. The above-described examples shown in FIGS. 3 to 11 are used with this range set.

Converting this idea, by positively utilizing the differential slip in the ball rolling groove having a single arc cross section to attenuate the mechanical vibration caused by cutting the workpiece of the machine tool,
The same effect as the Gothic arch groove of FIG. 13 can be obtained.

That is, as shown in FIG. 15, the cross-sectional shape of the ball rolling groove cut along a plane perpendicular to the axial direction is a single circular arc shape, and the ball has a circular arc shape with respect to each ball rolling groove. The ball contact surface is an elliptical arc surface whose major axis is in a direction perpendicular to the axial direction.

At each contact position along the long axis of the ball contact surface, the distance from the rotation center axis of the ball is different, so that a differential slip occurs on the ball contact surface. That is, when the ball makes a rolling motion, rolling contact without slip occurs at a position on the long axis of the ball contact surface, and rolling contact with slip occurs at other positions.

Conventionally, the differential slip was reduced as much as possible to reduce the friction. However, the present invention utilizes the differential slip to control the axial friction to obtain the required dynamic rigidity and damping. It is to get the nature.

That is, if the radius of curvature R of the ball rolling groove is set to about 0.51 of the diameter D of the ball, the differential slip increases due to a load applied by heavy cutting or the like, and the rolling and the sliding motion are mixed. It becomes close to exercise, and the damping property (damping property) is improved. The rolling phenomenon occurs between the ball and the rolling groove, and the movement becomes heavy, the damping property is increased, the effect is obtained for damping, and the chatter can be prevented even in heavy cutting.

Also, unlike the Gothic arch groove shape, if the depth of the ball rolling groove is set to about 51% of the ball diameter, the ball contact area becomes larger than a normal circular arc groove (closer to the roller), Synergistically with the configuration of the contact angle, the ability to load a heavy load is dramatically increased, and a highly rigid and stable linear motion can be obtained.

Next, a method of assembling the linear motion guide device according to the first to eighth embodiments shown in FIGS. 6 to 13 will be described.

First, a track base material and a slide base material which are raw materials use, for example, a common material manufactured by drawing or the like.
On the other hand, the depth of each ball rolling groove is approximately 1/4 to 1/2 of the ball diameter.
A dresser capable of forming a circular arc groove or a gothic arc groove is prepared. The pitch (distance) in the width direction and the height direction of each dresser is variously changed depending on what kind of contact angle of the linear motion guide device is to be obtained.

That is, a pair of upper dressers capable of forming a predetermined groove shape are separated by a first pitch (distance) in the width direction and a predetermined groove shape separated by a second pitch (distance) in the height direction from the upper dresser. Using a pair of lower dressers that can be formed, the track base 11 is manufactured from a common track base member having a square cross section. The track base 11 manufactured in this manner has a pair of ball rolling grooves 11a, 11a spaced apart by a first pitch (distance) in the width direction on the upper surface, and the ball rolling grooves 1a on each side surface.
The ball rolling groove 11b has a second pitch (distance) in the height direction with respect to 1a.

Next, a pair of upper dressers capable of forming a predetermined groove shape are separated from each other by a third pitch (distance) different from the first pitch in the width direction, and the second dresser is moved in the height direction with respect to the upper dresser.
By using a pair of lower dressers capable of forming a predetermined groove shape separated by a fourth pitch (distance) different from the pitch (distance), a plurality of types of slide tables 12 are manufactured from a common slide table material. .

The slide table 12 manufactured in this way has a pair of ball rolling grooves 12a, 12a separated by a third pitch (distance) in the width direction on the upper surface of a square recess 12c, and on each side surface. The ball rolling groove 12b has a fourth pitch (distance) apart from the ball rolling groove 12a in the height direction.
These third and fourth pitches (distances) are made different from the first and second pitches of the way 11, respectively, and by changing the different degree, one way as a reference can be obtained. Pitch (distance) between ball rolling grooves for 11
Are manufactured.

Then, the first and third pitches (distances) so as to have a contact angle suitable for each direction load and moment load.
Then, a combination of the second and fourth pitches (distances) is selected, and a linear motion guide device having a desired contact angle and a desired groove shape is assembled.

The above-described method of assembling the linear motion guide device includes the way 11
Although a plurality of types of slide bases 12 are manufactured based on the slide table, conversely, a plurality of types of track bases 11 may be manufactured based on the slide base 12. The positional relationship between the ball rolling grooves is basically the positional relationship between the ball rolling grooves formed on the upper surface and the left and right side surfaces on the track base side, and the ball rolling formed on the upper surface and the left and right side surfaces of the slide base. The positional relationship between the groove centers of the grooves may be the same position between the corresponding ball rolling grooves or may be formed so as to be deviated, and the processing reference surface may be set to a position other than the upper surface of the track base.

FIGS. 16A to 16E show other various examples of the configuration of the contact angle.

FIG. 16 (a) shows a configuration in which the contact angle of the two balls on the upper surface of the way is approximately 90 degrees, and the contact angles of the left and right balls are inclined downward by a predetermined angle with respect to the horizontal line toward the center of the way. It is what it was. In this case, since a radial load can be received by the ball on the side, the radial rigidity is high.

FIG. 16 (b) shows the contact angle of the ball row on the upper side of the way.
The configuration is such that they cross each other at approximately 45 degrees to the horizontal and below the position of the ball row, and the left and right ball contact angles are inclined downward by a predetermined angle with respect to the horizontal line toward the center of the track base. The configuration is as described above.

FIG. 16 (c) shows the contact angle of the ball row on the upper side of the way.
The configuration is such that they cross each other at an angle of approximately 45 degrees with respect to the horizontal and above the position of the ball row, and the right and left ball contact angles are inclined downward by a predetermined angle with respect to the horizontal line toward the center of the track base. The configuration is as described above.

16B and 16C, the ball on the upper surface side can also receive a lateral load, so that the rigidity against the radial load and the lateral load is increased.

FIG. 16D shows the contact angle of the ball row on the upper side of the track,
The configuration is such that they are inclined at approximately 45 degrees to the horizontal and in parallel in the same direction, and the contact angles of the left and right balls are inclined at 45 degrees to the horizontal in opposite directions to the contact angle of the upper ball. It is configured.

FIG. 16 (e) shows the contact angle of the ball row on the upper side of the way.
Each of the left and right ball contact angles are parallel to each other at an angle of 45 degrees with respect to the horizontal, in the same direction as the contact angle of the upper ball. The configuration is inclined. FIG. 16 (d),
In (e), since the contact angle of the ball on the upper surface side is inclined in parallel, it is possible to receive a lateral load from the right side in the figure, and in particular, the rigidity against the lateral load from the right in the figure increases.

In addition, the contact angle may be a combination type of horizontal and inclined, and it is possible to provide linear motion guide devices having various contact angle structures in which rigidity in a required direction is increased in accordance with a use site.

[Six-row type] FIGS. 17 to 21 show two rails respectively on the upper surface and both side surfaces of the way.
An example of a linear motion guide device of a six-row type having a set of ball rolling grooves provided in a row and having a total of 6 ball rolling grooves is shown.

7 to 21 show the ninth to twelfth embodiments of the linear motion guide device according to the present invention. First, referring to FIGS. 7 and 8, the basic configuration of the linear motion guide device according to the present invention will be described. Will be described.

Reference numeral 1 denotes an entire linear motion guide device.
A slide 3 having a recess 3d for receiving the track 2 and guided linearly along the track 2; and a six-row rotatably interposed between the slide 3 and the track 2 Infinite circulating ball 4
It is composed of

The way 2 has a rectangular cross section and is continuous in the longitudinal direction. This way 2 has a pair of ball rolling grooves 2a extending in the longitudinal direction on the upper surface thereof and a set of ball rolling grooves 2a extending in the longitudinal direction of the way 2 on both sides.
2b and 2c are formed.

The slide 3 has a recess 3d having a rectangular cross section for receiving the raceway 2 having a rectangular cross section, and a ball which receives loads on the upper surface and both side surfaces of the recess 3d in the longitudinal and lateral directions of the race 2. Ball rolling grooves 3a, 3b, 3c corresponding to the rolling grooves 2a, 2b, 2c are formed, and the slide base 3 is inserted into the recesses 3d and straddles the track base 2. It is attached so that.

The slide base 3 includes a slide base block 5 having high rigidity and side covers 6 fixed to both end surfaces of the slide base block 5. The ball rolling grooves 3a, 3b, 3c and the ball escape hole 6 are formed in the recess 3d of the slide block 5. The side cover 6 has opposing ball rolling grooves 2a, 3a and 2
A direction change path is provided to connect both ends of the ball passage in the load area between b, 3b; 2c, 3c and both ends of the ball escape hole 7.

Between the ball rolling grooves 2a, 2b, and 2c of the track base 2 and the corresponding ball rolling grooves 3a, 3b, and 3c of the sliding table 3, a large number of balls 4 are loaded so as to roll freely, respectively. A total of six ball rows, that is, two ball rows 5 and two ball rows 6, 7 are formed on both side surfaces.

Then, two ball rolling grooves 2b, 2c (or 3b, 3c) on either side surface of either the track base 2 or the slide base 3,
Ball rolling groove 3 of track 2 or slide 3 corresponding to each other
b, 3c (or 2b, 2c), the corresponding positional relationship of the groove center is made identical or deviated in the vertical direction, and the corresponding positional relationship of the groove center is made identical or deviated in the vertical direction. Alternatively, the slide table 3 is mounted on the track base 2 or the slide table 3 on the other side in any combination.

As described above, the track base 2 or the slide base 3 in which the corresponding positional relationship of the groove center is the same or deviated in the vertical direction is mounted on the counterpart track base 2 or the slide base 3 in any combination. Thereby, the contact angles of the balls 3 of the ball rows 6 and 7 on both side surfaces can be adjusted. Thereby, rigidity in the vertical direction in the vertical direction and the lateral direction in the horizontal direction required for the load can be obtained, and a linear motion guide device having load load characteristics according to the application can be provided.

In adjusting the contact angle, it is preferable to make the ball rolling grooves as follows.

That is, the opposing ball rolling grooves 2a, 2b, 2c and 3a, 3
b, 3c may be the circular arc shape shown in FIG. 15 or the gothic arc shape shown in FIG. 14, but at least the corresponding ball rolling grooves 2b, 2c on both sides.
And the depth of 3b, 3c is set to approximately 1/2 of the diameter of the ball 4. As a result, the balls 4 of the two rows of ball rows 6, 7 on both sides come into contact with some of the ball rolling grooves 2b, 2c and 3b, 3c, which have a substantially semicircular shape. All contact angles can be taken. If the variation of the contact angle is small, it may be about 1/4 of the diameter of the ball 4.

17 to 21, the corresponding positional relationship of the groove center in the linear motion guide device having the above-described configuration is equal or deviated in the vertical direction, and the track base 2 or the slide base 3 is Various contact angle structures are obtained by arbitrarily combining with the table 3.

FIG. 17 shows a ninth embodiment of the present invention, in which the groove centers OA of the two ball rolling grooves 2b and 2c on both side surfaces of the track base 2 are aligned with the ball rolling grooves 3b and 3b of the corresponding slide base 3. The corresponding positional relationship of the groove center with respect to the groove center OB of 3c is deviated upward, or the groove center OB of the two ball rolling grooves 3b, 3c on both side surfaces of the slide 3 is
The corresponding positional relationship of the groove center OA of the corresponding ball rolling grooves 2b, 2c of the track base 2 is deviated downward with respect to the groove center OA, and the contact angles of the balls 4 of the double-row ball rows 6, 7 on both sides. Is approximately 45 degrees inclined upward toward the inside of the way 2 with respect to the horizontal. The method of the deviation can be set in the same manner as the assembly method described in the first to eighth embodiments. On the other hand, the contact angle of the balls 4 of the two rows of balls 5 on the upper surface is substantially 90 degrees with respect to the horizontal.

In the case of the ninth embodiment, a vertical load (radial load) PR acting on the slide table 3 from above is supported by the two rows of ball rows 5 on the upper surface. Further, a lateral load (horizontal load) PT acting from the left and right is supported by the two rows of ball rows 6 and 7 on either side depending on the direction of the load. Further, a vertical load (reverse radial load) PL acting from below is supported by the two rows of ball rows 6, 7 on both sides.

In addition, since the contact angle of the balls 4 of the two rows of balls 6 and 7 on both sides is approximately 45 degrees inclined upward toward the inside of the track base 2 with respect to the horizontal, the contact angles in the reverse radial direction and the lateral direction are increased. The load can be evenly received. In addition, the rigidity against the lateral load is basically higher than that of the single left and right side type.

Further, with respect to the load in the radial direction, the rigidity is increased because it is supported by the two rows of balls 5 having a contact angle of substantially 90 degrees with respect to the horizontal of the upper surface.

In particular, as described above, if the depth of the ball rolling groove is set to about 51% of the ball diameter, the ball contact area becomes larger (closer to the roller) with respect to a normal circular arc groove, and the contact angle becomes smaller. Synergistically with the configuration, the load capacity for heavy loads is dramatically increased, and high rigidity and stable linear motion can be obtained.

That is, when a load is applied in the radial direction, the reverse radial direction, or the horizontal direction (left and right), the combination of the track and the slide is optimal.

FIG. 19 shows a linear motion guide device according to a tenth embodiment of the present invention. The linear motion guide device 1a is provided on either side of the track base 2 or the slide base 3. The two ball rolling grooves 2b, 2c (or 3b, 3c) are connected to the corresponding ball rolling grooves 3b, 3c (or 2b, 2c) of the raceway 2 or the slide base 3.
And the contact positions of the balls 4 of the two rows of ball rows 6 and 7 on both sides are set to substantially 0 degrees with respect to the horizontal, with the corresponding positional relationship of the groove center being the same. On the other hand, the contact angle of the balls 4 of the two rows of balls 5 on the upper surface is substantially 90 degrees with respect to the horizontal.

In the tenth embodiment, a vertical load (radial load) acting on the slide table 3 from above is supported by the two rows of balls 5 on the upper surface. The lateral load (horizontal load) acting from the left and right is supported by the two rows of ball rows 6 and 7 on either side depending on the direction of the load.

Then, the contact angle of the balls 4 of the two rows of balls 6 and 7 on both sides is made substantially 0 degree with respect to the horizontal, and the contact angle of the balls 4 of the two rows of balls 6 and 7 on the upper side is Since it is approximately 90 degrees, not only high rigidity can be achieved, but also radial loads and horizontal loads can be equally received.

In other words, the combination of the rail and the slide slide has a large rigidity against loads in the horizontal direction (left and right) and in the radial direction, and is optimal when a load in the radial direction and horizontal direction (left and right) is applied.

FIG. 20 shows a linear motion guide device according to an eleventh embodiment of the present invention. In this example, the contact angle of the balls 4 of the upper two rows of ball rows 6 and 7 on both sides is approximately 45 degrees with respect to the horizontal.
And the intersection of the contact lines at this contact angle is located inside the way 2. The contact angle of the balls 4 of the lower two rows of ball rows 6 and 7 on both sides is substantially equal to the horizontal. 0
It is a degree.

On the other hand, the contact angle of the balls 4 of the two rows of balls 5 on the upper surface is set to approximately 45 degrees with respect to the horizontal, and the intersection of the contact angles intersects outside the track base 2.

FIG. 21 shows a linear motion guide device according to a twelfth embodiment of the present invention.
In the linear motion guide device of the eleventh embodiment, the contact angles of the ball rows 6 and 7 on both sides are set in a reverse combination to that of the third embodiment. That is, the contact angle of the balls 4 of the lower two rows of ball rows 6 and 7 on both side surfaces is set to approximately 45 degrees with respect to the horizontal, and the intersection of the contact lines at this contact angle is located inside the track base 2. The contact angles of the balls 4 of the upper two rows of ball rows 6 and 7 on both sides are set to substantially 0 degrees with respect to the horizontal.

That is, the way 2 in the eleventh and twelfth embodiments is used.
The combination of and the slide 3 is an optimal combination of the track and the slide when a large load is applied to the load in the reverse radial direction.

FIGS. 22A to 22C show other examples of the contact angle configuration of each ball. Any combination of the contact angles other than the illustrated example is possible.

FIG. 22 (d) shows a row of balls on the side, two rows on one side,
FIG. 22 (e) shows a configuration in which the other side is arranged in a single row, and FIG.

In this way, the ball rows on the top and side surfaces are
A combination of rows may be used, and in some cases, the upper surface and both left and right sides may be formed as a single row to form a three-row configuration. Furthermore, the number of rows is not limited to two, and three or more rows may be used.

Further, in each of the above-described embodiments, the case where the retainer for preventing the ball 4 from falling off when the slide base 3 is pulled out from the track base 2 is described as an example, but the present invention employs a retainer. The present invention can be applied to a type having the same.

Furthermore, in each of the above-described embodiments, the way in which the track base has a rectangular cross section and the recess of the slide base has a square cross section has been described as an example, but the present invention is not particularly limited to this shape.

This makes it possible to obtain a load characteristic in a necessary direction with respect to the load, and to provide a device having a large load capacity according to the application.

INDUSTRIAL APPLICABILITY In the linear motion guide device of the present invention, the contact angle in each ball rolling groove is determined by the distance between the two ball rolling grooves formed on the upper surface of the track and the ball rolling groove. The distance between the ball rolling grooves formed on each side surface and the distance between the corresponding ball rolling grooves on the slide table can be arbitrarily set by changing the distance between the ball rolling grooves. By changing the pitch between the ball rolling grooves of the table in accordance with the load condition and forming the ball rolling grooves having the optimum contact angle, there is an effect that the performance adapted to the load in each direction can be obtained.

The cross-sectional shape of the ball rolling groove may be a single arc shape or a configuration combining two arcs, but the depth is set to a depth at which an arbitrary ball contact angle can be selected. The diameter is preferably about 1/4 to 1/2. In this case, the ball comes into contact with somewhere in the arc-shaped ball rolling groove, so that it takes substantially all contact angles conventionally used in this type of linear motion guide device. be able to.

In the method of the present invention, a common slide base material and slide base material can be used. In forming the ball rolling groove, the type and pitch (distance) of the dresser, Since various linear motion guide devices can be obtained simply by changing the pitch between the ball rolling grooves formed according to the load conditions, the productivity is dramatically improved.

Claims (18)

(57) [Claims] 1. A base, a slide having a recess for receiving the base and guided linearly along the base, and a rolling base between the base and the base. Wherein the raceway has at least one ball rolling groove on the upper surface and at least one ball rolling groove on both side surfaces, A linear motion guide device provided with ball rolling grooves corresponding to the ball rolling grooves on the upper surface and both side surfaces of the track base on the upper surface and both side surfaces of the place; The ball rolling grooves on the upper surface and both side surfaces of the same are deviated from the corresponding ball rolling grooves of the track base or the slide base by the same or the same positional relationship of the groove center, and the corresponding position of the groove center described above. A track or slide with the same or deviated relationship is Linear motion guide apparatus characterized by being mounted with in any combination to the road base or slide base. 2. The linear motion guide device according to claim 1, wherein the track base has two ball rolling grooves on the upper surface and one ball rolling groove on each of the right and left side surfaces of the track. 3. The straight line according to claim 1, wherein a pair of ball rolling grooves are provided on the upper surface of the track base, and a pair of ball rolling grooves are provided on both side surfaces. Exercise guidance device. 4. A cross section of a track base having a square shape, wherein a distance between two ball rolling grooves on an upper surface of the track base and a distance between ball rolling grooves formed on the upper surface and each side surface are defined by the following formula: By changing the distance between the corresponding ball rolling grooves of the slide base, the groove centers of the corresponding ball rolling grooves of the track base and the slide base have the same positional relationship or deviate in the corresponding positional relationship. The linear motion guide device according to claim 2 or 3, wherein: 5. The ball rolling groove has a depth such that a ball contact angle can be freely selected.
5. The linear motion guide device according to 1, 2, 3, or 4. 6. The depth of the ball rolling groove is set to approximately 1/4 of the ball diameter.
The linear motion guide device according to claim 5, wherein the ratio is set to 1/2. 7. The ball rolling groove formed on the upper surface of the track base and the ball rolling groove of the slide base opposed thereto have an arc shape slightly larger than a ball, and each side surface of the track base. Wherein at least the ball rolling groove formed on the sliding base and the ball rolling groove of the slide table opposed thereto have a shape formed by combining two arcs.
7. The linear motion guide device according to 5 or 6. 8. A ball rolling groove formed on the upper surface of the track base and a ball rolling groove of the slide base opposed thereto, and
The ball rolling groove formed on each side surface of the track base and the ball rolling groove of the slide base opposed thereto have an arc shape slightly larger than the ball.
7. The linear motion guide device according to 1, 2, 3, 4, 5, or 6. 9. A ball rolling groove formed on an upper surface of a track base and a ball rolling groove of the slide base opposed thereto, and
The ball rolling groove formed on each side surface of the track base and the ball rolling groove of the slide base opposed thereto are both formed by combining two arcs.
7. The linear motion guide device according to 3, 4, 5, or 6. 10. A ball rolling groove formed on the upper surface of the way and a ball rolling groove of the sliding table opposed thereto have a shape formed by combining two arcs, and are provided on each side surface of the way. The ball rolling groove formed and the ball rolling groove of the slide table opposed to the ball rolling groove have an arc shape slightly larger than a ball. The linear motion guide device as described in the above. 11. The method according to claim 11, wherein a contact angle of a ball interposed between a pair of ball rolling grooves on the upper surface of the track base and the slide base corresponding to each other is 90 degrees with respect to the horizontal. And the contact angle of the ball interposed between the pair of ball rolling grooves in the two rows corresponding to both sides of the slide base is set to approximately 45 degrees, which inclines upward toward the inside of the track base with respect to the horizontal. 4. The linear motion guide device according to claim 3, wherein: 12. The track according to claim 1, wherein a contact angle of a ball interposed between a pair of ball rolling grooves on both sides of the track base and the slide base corresponding to each other is substantially 0 degree with respect to the horizontal. 4. The contact angle of a ball interposed between a pair of ball rolling grooves in two rows corresponding to each other on the upper surface of the base and the slide base is substantially 90 degrees with respect to the horizontal. Linear motion guide device. 13. All the ball rolling grooves formed in the raceway and the slide base have a single arc shape slightly larger than the ball, and at least one of the ball rolling grooves has a radius of curvature of the groove cross section. 7. The linear motion guide device according to claim 1, wherein is set to a range smaller than 0.52 of the diameter of the ball. 14. The ball rolling groove, wherein the radius of curvature of the groove cross section is set to about 0.51 of the diameter of the ball.
14. The linear motion guide device according to 13. 15. A step of forming a first member having a first ball rolling groove on an upper surface and second ball rolling grooves on both left and right sides, and a predetermined number of rows of balls with respect to the first member. A second member slidably assembled via a third ball rolling groove provided in such a manner that a corresponding positional relationship of the groove center is the same or deviated with respect to the first ball rolling groove of the first member. And a plurality of fourth ball rolling grooves provided with the same positional relationship of the center of the groove with respect to the second ball rolling groove of the first member or the fourth ball rolling groove provided to be deviated. And a step of selecting a combination of the first member and a plurality of types of second members so as to have a contact angle suitable for a load and a moment load in each direction, respectively. . 16. A pair of first ball rolling grooves separated by a first pitch in the width direction, and a pair of second balls separated by a second pitch in the height direction from the first ball rolling grooves. Forming a first member having a rolling groove; and a second member slidably assembled to the first member via four rows of balls, wherein the second member has a first pitch in a width direction. A pair of third ball rolling grooves separated by a different third pitch, and a pair of fourth ball grooves separated by a fourth pitch different from the second pitch in the height direction with respect to the third ball rolling grooves.
Forming a plurality of types of second members having ball rolling grooves; and forming the first and third pitches and the second and fourth pitches so as to have contact angles suitable for loads and moment loads in respective directions. Selecting a combination of pitches. A method for assembling a linear motion guide device, comprising: 17. The method for assembling a linear motion guide device according to claim 13, wherein the depth of the ball rolling groove is set to such a depth that the ball contact angle can be freely selected. . 18. The depth of the ball rolling groove is set to approximately 1 / ball of the ball diameter.
16. The method for assembling a linear motion guide device according to claim 15, wherein the ratio is set to 4 to 1/2.