JPH03189416A - Direct-acting rolling guide - Google Patents

Abstract

PURPOSE:To facilitate a circulating travel by supplying rollers together with the retainers thereof to the inside of a circulation passage formed within a bearing with the axial centers of the rollers made to cross each other for constituting a close roller type direct-acting roller bearing of rolling element circulation system. CONSTITUTION:Rollers 5 and 5' in a circulation route are made to cross each other orthogonally in a moving direction, and so positioned as to match the inner shape 8 of the route 8 formed with a V-groove 6 on a guide axis and another V-groove 7 of a bearing side opposite thereto. Also, the rollers 5 and 5' are fed to a cylindrical roller retaining hole 1c within respective adjacent retainers 1 and 1', and match the rectangular board surface of the route in a guide surface 1b formed on the external surface of the retainers 1 and 1'. Also, the retainers 1 and 1' are kept in contact with each other via a cylindrical surface 1a formed on the external surface thereof. According to the aforesaid construction, no constraint occurs between the retainers 1 and 1', and relative slip friction due to rolling contact can be avoided. Also, smooth travel for circulation can be embodied.

Description

[Detailed Description of the Invention] The linear motion rolling guide of the present application has the linear motion guide accuracy, durability, i4 load resistance, static and dynamic rigidity, etc. required for a rolling bearing among conventional linear motion rolling bearings. Focusing on the non-circulating cross-roller direct-acting rolling bearing, which is considered to have the best performance, we devised a new cage for the inner rollers of the bearing, and installed the rollers together with the cage inside the bearing. In the formed circulation path, the axes of the rollers are fed so as to cross each other, thereby forming a cross-roller type direct-acting rolling bearing with rolling element circulation.
A high-performance linear motion rolling guide is achieved using a guide shaft with a molded raceway surface.In the attached Figure 1, (A) to (D1.
) and (C) are perspective views of roller cages that are adapted to the circulation path in the above-mentioned circulating cross-roller type bearing and are molded with different shapes as indicated by symbols 1.2.3 in the figure. As shown in the diagram.

In the cage l shown in Figures (A) to (D), the contact between adjacent cages 1m in the circulation path is made on the cylindrical surface 1a, and
B), Fig. (C1) Both cages 2 and 3 have a spherical surface 2.
b, 3b are molded so that they are in contact with each other. Also, lb in Figures (A) to (D), TB), Ic)
, 2b, and 3b are all adapted to the raceway of the rollers formed by the shaft of the crossed roller type bearing and the raceway of the rollers formed in the V-groove shape with an angle of 90°, as shown in the figure. As shown, in cages 1 to 3, between the inner peripheral surfaces of the rolling paths of the rollers in the moving direction of the cage shown by the arrow in the figure,
In order to allow the cage to run while maintaining a slight gap, retainers 21 are formed at four locations on the outer peripheral surface of each cage, parallel to the rolling direction and at right angles to each other, at equal intervals with respect to the center of the cage. This is a running guide surface of the inner roller of the cage formed on the outer peripheral surface. Similarly, Figures (A) to (D) to (l in C1
c, 2c, and 3c are roller holding holes formed in each cage, and in 1C and 2c, the rollers are housed in the axial direction of the rollers, leaving a gap between them and the outer peripheral surface of the rollers. and the relative positioning of the rollers to the cage.
The roller holding part for the cage shown in figure (C) is 3 in the figure.
As shown in c, the insertion opening was formed into a rectangular shape as shown in the figure to match the cross-sectional shape including the roller axis so that the rollers are aligned with the cage mainly at both end faces in the axial direction. It is something.

Further, the embodiment shown in Figure (H) is formed in a linear motion rolling bearing using balls as rolling elements, including a load area formed between the rolling surface formed on the guide shaft. When the circulation path of the rolling element is formed into a rectangular cross section perpendicular to the direction of movement of the rolling element, it is similar to the roller cage shown in the above figures (A) to (D) to (C). , shows an example of a cage that can be applied to the circulation path method, and 4a to 4 in the figure
4c is a spherical surface that forms a contact surface between adjacent cages as in the case of the rollers described above, and 4b is a spherical surface that forms a contact surface between adjacent cages; 4b is a spherical surface that forms a contact surface between adjacent cages; Two pairs of parallel planes parallel to the moving direction of the cage form a guide surface for the cage in the path, and 4C is an insertion port for inserting the ball into the holding section in the cage.

Figure 2 is a projected view of the roller retainer for the direct acting roller bearing of the present invention shown in the perspective views of Figures 1 (A) to (D).
is a plan view, (B) is a front view, (C) is a side view, (D) is a front view (sectional view taken along the cross-sectional line E-H shown in Bl,
E) is a sectional view taken along line FF shown in Figure (B). 1a to lc in the figure are the same as in FIG. 1(A). la is a cylindrical surface that becomes a contact surface between adjacent cages in the circulation path, and 1b is a guide surface of the cage in the roller circulation path.

Figure 1 above and TA), (B), T in these figures
As is clear from C), the cage is formed into a rectangular shape as a whole, keeping at right angles to two adjacent surfaces around the cage, corresponding to the direction of cage movement in the load area. Further, the cylindrical surface 1c that holds the rollers in the cage passes through the cage at an angle of 45°, and among the guide surfaces formed by the four parallel surfaces,
In order to maintain simultaneous contact between the guide shaft and the rolling surface in the bearing in the load bearing area, the outer circumferential surface of the roller inserted in the cage is against the two parallel planes shown that are parallel to the cylindrical surface inside the cage. A hole 1d is formed. In addition, in the figure, the above-mentioned guide shaft and
A rectangular surface 1b is formed on the outer peripheral surface of the cage, corresponding to each rolling surface of a pair of V-shaped rollers formed on the bearing.
The convex portions 1e formed at the four corners of the periphery of the cage, which are formed so as to intersect with each other, are the retaining portions created by forming the holes 1c on the cylindrical inner circumferential surface for inserting rollers into the cage. This is to compensate for the decrease in strength of the container, and the space in which these convex parts interpose in the circulation path is required. It can be determined in accordance with the normal clearance value that is set when the rectangular groove for relief bending in the V-groove bottom is opposed to the V-shaped groove in the shaft and bearing.

In Figure 3, the outer peripheral surface is spherical, as shown in Figure 1+Bl, and like the cage shown in Figures 1 (A) to (D) and Figure 2, it adapts to the shape of the circulation path. This is a projected view of the roller retainer for a direct acting rolling bearing of the present application, in which the roller guide surface is formed in a rectangular shape in the circulation direction, and I8), [8), and (C) in the figure are They are a plan view, a front view and a 1gS side view of the cage, respectively, and (Y) and (E) are a front view (
It is a cross-sectional view located at the cross-sectional lines ε-E and F-F shown in B). In each of the above figures, 2a is a spherical surface with which adjacent cages maintain contact within the aIi annular path, and 2b is a rolling surface of rollers formed at four locations around the cage to conform to the shape of the inner peripheral surface of the circulation path. The guide surface 2c is a cylindrical surface for holding rollers in the cage, which is formed orthogonally to a pair of mutually opposing surfaces among the roller guide surfaces formed at four locations on the outer circumferential surface; 2d is a cylindrical surface for holding the rollers in the cage; A roller is formed between the cage inner cylindrical surface 2c and the roller guide surface 2b formed on the outer peripheral surface of the cage so as to maintain contact between the periphery of the rollers supplied to the inner roller holding cylindrical surface and the rolling surface. The elongated holes 2e are located at four corners of the outer circumferential surface of the cage, between the guide surfaces of the rollers that are perpendicular to each other and have Mti, as explained in FIGS. 1(A) and 2. Convex F in cage
Like IS10, this is a convex portion formed on the outer peripheral surface for the purpose of reinforcing the cage.

Figure 4 is a projected view of the cage for the linear rolling bearing of the present application shown in the perspective view of Figure 1 (C), in which +A) is a plan view, (B) is a front view, and (C) is a side view. Figure (0) is a sectional view taken along the cross-sectional line E-H shown in Figure (8), (E) is Figure (D
Cross-sectional view along cross-sectional line F-F in J, (F) is figure (C)
FIG. Also (A
) to (D) to (F), 3a is a spherical surface that becomes the contact surface of the adjacent cage in the circulation path, and 3b is molded at four locations on the outer peripheral surface of the cage. The guide surface of the cage inner roller in the circulation path, 3c is shown in Figures (B), (DJ, (E)
l, As shown in (F), unlike the holding cases shown in Figs. 2 and 3, the rollers are mainly positioned and restrained within the cage at both end faces in the axial direction of the rollers, and As shown in the cross-sectional view of Figure (El), even the middle of the roller periphery can be involved in positioning the roller with respect to the cage.
Also, in the cage itself, it is not necessary to form the convex parts e and 2e for reinforcing the cage as described in Figs. 2 and 3, so it is easy to form the roller circulation path and the cage. However, the axial length of the rollers is restricted, and the load capacity of the rollers is also somewhat reduced compared to the old method. Figure (E), (F
) is 3d.

This hole is formed to maintain contact between the rollers of the cage and the raceway surface on one side of the load-bearing area.

FIG. 5 shows that even in a conventional linear motion rolling bearing constructed using balls as rolling elements, a retainer is adapted to the balls.
Since high-precision, high-performance bearings are not available, we have developed a linear-driving wheel using VjNI-type rollers and balls, similar to the cross-roller type linear-acting roller bearing of the present application, with VjNI-type rolling and rolling rollers molded into the guide shaft and bearing. A spherical cage that can be adapted to be formed into a receiver is formed by applying the molding method for the roller cage shown in FIG. The ball holder is again illustrated in a projection view.

That is, (A) to (D) in the figure are plan views of the cage, (
B) is a front view, (C) is a side view, (b) is a cross section taken along the cross-sectional line ε-E in the iB) figure, and (E) is a cross-sectional view taken along the cross-sectional line F-F in the (C1) figure. Also, in these figures, 4th is an arcuate curved part formed in the circulation path,
4b is a spherical surface formed so as to be able to adapt by rolling contact with an adjacent cage to reduce the frictional resistance generated between the cages in the circulation path;
As mentioned in the figure, the guide surface 4c is formed on the outer peripheral surface of the cage in order to conform to the cross-sectional shape of the rectangular circulation path and to smoothly move the rolling elements inside the cage. This is a hole for holding a ball formed by a cylindrical surface and a spherical surface molded inside.

FIG. 6 shows the rolling element retainer for the direct acting roller bearing of the present application shown in FIGS. 1(A) to (D) above and shown in FIG.
This is an explanatory diagram when it is placed in the bearing. As shown in the figure, the bearing has an elliptical shape in the axial direction due to the linear motion range in the operating direction of the normal shaft and the circular arc path for circulation. This corresponds to one end in the axial direction of the circulation path to be formed, and is shown in a perspective view.

1' is a cage for the rollers, 5' is a roller, 6 is an operating shaft that repeats relative reciprocating motion between the shaft and the bearing,
The rolling surface of the grooved rollers, 7 shows the rolling surface of the V-shaped roller formed in the bearing corresponding to the rolling surface of the operating shaft, and 8 shows the cross-sectional shape of the circulation path formed in the bearing. As shown in the figure, in the cross-roller type direct-acting roller bearing of the present invention, the rollers in the circulation path cross each other at 90 degrees in the rolling direction of the rollers, as shown at 5 and 5' in the figure. It is arranged to conform to the internal shape of the path formed by the V-shaped groove 6 formed on the guide shaft and the V-shaped groove 7 on the bearing side opposite thereto. Therefore, (when the rollers touch each other and travel on the Y road.

The generating lines on the outer circumferential surfaces of each roller intersect, resulting in point contact, and even if the contact pressure is small, the mutual contact pressure becomes excessive, causing damage to the outer circumferential surfaces of the rollers, and causing unevenness in the rolling direction of the rollers. This causes a so-called skew phenomenon, which impedes smooth rolling of the rollers across the bearing width. Therefore, in conventional non-circulating type bearings of this type, various cages have been devised and applied to operate the rolling rollers in isolation from each other. However, in this roller circulation type pass bearing, it can be applied over the entire range of the linear motion range and the curved path range for circulation in the elliptical path in the operating direction. It is difficult to form a cage, and the application of a cage that is functionally rational has not yet been found.

In the cage for a linear rolling bearing of the present invention, the rollers 5.5' shown in the above figure have a cylindrical inner peripheral surface formed in the above 1c of the rolling cage in the adjacent cage 1.1' shown. The guide surface 1b of the roller supplied to the roller holding section and formed on the outer peripheral surface conforms to the rectangular wall surface of the circulation path, and between adjacent cages, the cylindrical surface 1a also formed on the outer peripheral surface of the cage conforms to the rectangular wall surface of the circulation path. Contact is maintained, and the cages are not restrained with each other throughout the entire path, and relative sliding friction is avoided by rolling contact between the cylindrical surfaces of the outer circumferential surface of the cage, even in the arcuate curved portion of the path. This makes it possible to realize smooth running for circulation.

FIG. 7 is an explanatory diagram of the case where the cage for the linear acting roller bearing of the present application shown in FIG. 1 (Bl) and FIG. The outer circumferential surface of the cage, excluding the roller running guide surface, has been changed from a cylindrical surface to a spherical surface. In the figure, 2 and 2' are roller cages, and 5.5'
Roller 6 is a 90°V tll formed on the bearing guide shaft.
Rolling guide surface of shaped rollers, 7 is 90" which is also molded into the bearing.
The raceway surface of the V-groove rollers, 8 is a rectangular cross-sectional shape perpendicular to the guide direction of the cage in the circulating running path of the bearing inner rollers, 2a
is a spherical outer peripheral surface of the cage, 2b is a guide surface for rollers on the outer peripheral surface of the cage, and 2c is a cylindrical surface for inserting rollers in the cage. As in the case of Fig. 6 above, roller 5.5'
The axes thereof are perpendicular to the circulation direction, and intersect with each other at right angles, and are disposed in the cylindrical holes 2c in the respective cages 2 and 2, and travel within the circulation path. The cages in each group maintain point contact between the spherical surfaces on the outer circumferential surface of the adjacent cages, and, like the contact between the cylindrical surfaces of the outer circumferential surface of the cage in FIG. 6 above, throughout the entire circulation path. , it is possible to realize smooth circulation without causing restraint between the cages. In addition, in the cage outer peripheral surfaces shown in (Al and (B) in Fig. 1 above), in a comparison between cages in which the contact surfaces between adjacent cages are formed into a cylindrical shape and those in which the contact surfaces are formed into a spherical shape, When the cage is formed with a spherical surface rather than a cylindrical surface, the shape of the cage as a whole becomes simpler, and the cage is easier to mold.
The outer peripheral surface was molded to conform to the shape of the circulation path. In comparing the intersection angle between the roller guide surface 1b and the cylindrical surface la of the outer circumferential surface of each cage l and cage 2, and the intersection angle between the roller guide surface zb and the spherical surface 2aT:m, The angle at the cage 2 is blunter than the intersection angle at the cage l, and when the cage runs in the circulation path, smooth sliding between the cage guide surface of the roller and the path wall is achieved. I can do it.

FIG. 8 shows the inside of the bearing in a plane inclined by an angle a with respect to the xy plane shown in the above-mentioned attached FIG. An example of the configuration of a bearing is shown in which a roller circulation path is formed and the rollers are supplied into the path. In the figure, 3.3' is a roller cage, and 3a is a contact surface of an adjacent cage. A spherical outer circumferential surface, 3b is a guide surface for rollers in the path in the cage,
3c is the roller insertion opening into the cage, 5.5' is the roller, 6 is the raceway surface of the V-groove roller with an angle of 90° formed on the guide shaft, and 7 is formed on the bearing. The raceway surface of the V-groove roller, which together with the V-groove 6 forms the load bearing range of the roller, 8 is a bearing circular circulation path for the roller, and 1. in the figure. As shown in Figures 6 and 7 above, the circulation path of the roller is placed in the xy plane parallel to the mounting surface of the normal guide shaft, and parallel to the path of the load supporting range, along the X axis in the figure. The distance -he from the bearing circular direct motion circulation path range formed in the above-mentioned shaft mounting part is the distance between the bearing internal rotation range formed parallel to the X-axis in the xz plane orthogonal to the xy plane parallel to the shaft mounting part. The distance between the circulation path and the X axis, L! It includes the center line of the circulation path of the inner rollers of the bearing mentioned above, and is directed downward from the X-axis.
In addition, in the plane that intersects the xy plane and the xz plane at an angle α, the distance between the center line of the path in the load support range shown in the figure and the center line of the circulation path in the linear motion range within the bearing, θ is the xy plane mentioned above.
As shown in the drawing, which shows the rotation angle of the cage center in the circulation path on one side semicircular arc for circulation in a plane that intersects with the γ plane at an angle α, in the linear acting roller bearing of the present application, the above-mentioned first By using 2 to 4 cages of rollers and balls shown in the figure, it is possible to form a circulation path for the inner rollers of the bearing in any angular range from a = 0 to 90 degrees in three-dimensional space. Adjacent cages in the path can always maintain mutual contact on the spherical surface to ensure smooth circulation movement. Therefore, when adopting this type of rolling linear motion guide in various high-performance machines, if space constraints arise to form a circulation path within the bearing, for example When forming an arcuate path, the number of retainers arranged in the arcuate path is:
At least four or more cages are required, and in bearing configurations with fewer cages, the cages lack smooth circulation, and this tendency is exacerbated as the relative speed between the shaft and bearing increases. be done. Therefore, when configuring the circulation path, the maximum diameter of the illustrated arcuate path should be set to 1. When limited to , the diameter of the arcuate path is ! , can be made approximately 1.4 times as large as .

FIG. 9 shows an axis -
When forming the circulating rolling element path in the bag, in addition to the turning movement of the rolling element in the xy plane within the arcuate path to convert the running direction of the rolling element by 180 degrees, the rolling element is rotated in the Z direction perpendicular to the xy plane. This diagram shows the behavior of the resulting displacement. The horizontal axis in (A) in the figure shows the turning angle of the rolling element in the inclined plane, and the vertical axis shows the turning angle in the Z direction mentioned above. It shows the displacement of the rolling elements. As shown in the figure, the displacement curve in the Z direction exhibits a smooth displacement behavior according to a gentle buffer curve when people enter the arcuate route. Near the turning angle gO° where the two buffer curves are connected, the rising angle is on the xy plane. It corresponds to the inclination angle a of the inclined plane with respect to . Figure (8)
1 indicates the turning angle of the rolling element in the path as a reference for the displacement in the Z direction.

Figure 1 θ (Al-(E) is an explanatory diagram of the circulating motion of the cage remaining in the bearing internal ring path during the operation of the direct acting roller bearing of the present application, and 21 to 2 in Figure 1 indicate retention of the rollers. 5 is the roller, 6 is the transfer surface of the roller formed on the guide shaft, 7
9 is the rolling surface of the roller which is also molded into the bearing, 9 is the guide shaft,
Reference numeral 10 denotes the direct-acting roller bearing body, the eye indicates the circulation path within the bearing, and angle β is the intermittent turning angle of the retainer that occurs at the curved portion of the illustrated circulation path when the bearing is operated.

Introduction In Figures (A) to (D), the attached diagrams and bearing 1
The roller 5 shown in the side view (El) supports the load between the V-shaped grooves 6 and 7, and moves in the opposite direction to the bearing. The cage 2 is rolling and is applied to these rolling rollers in Figure (A).
m, 2. ．． 2@ also moves in the opposite direction to the direction of movement of the bearing,
2 in these cages. The retainer 2. is in the position shown in FIG. While keeping any contact, hold i! While the rollers in 8Izs contact the V-shaped grooves 6 and 7 in the shaft and bearing described above and continue the transfer of the load bearing area, the cage 21 as shown in Figure (C1).

Cage 2. At the same time, a series of cages up to cage 2I arranged in mutual contact in the circulation path is moved, and at the same time cages 2. As a result, the cage 2° is moved toward the rolling path of the rollers in the load supporting range formed by the shaft and the V-shaped groove 6.7 formed between the bearing. These cages are then shown in Figure (D) as the cage 2. When the rollers in the cage complete the transfer of the load-bearing range, they stop moving in the path, and the cage 2. As the load support range of the cage inner rollers is transferred, the bearings continue to move in the opposite direction to the movement of the bearings mentioned above, and move to the positions 2 and 2 degrees of each cage in Figure (A), and the load support is increased. The movement of the cage in the path is repeated every time the roller rolls in the range corresponding to the distance between the cages arranged in the range. In the direct-acting cross-roller type rolling bearing of the present application, which is constructed by applying a cage that circulates in the path by such a mechanism, the cage of the rollers is connected to the rolling surface of the V-shaped rollers in the load supporting range. On the other hand, when the axes of the inner rollers of the cage are alternately arranged to be orthogonal to each other and the rollers in the circulation path are operated to support a load, there is no direct contact between them through the cage. , and a cylindrical shape la formed on the outer peripheral surface of the cage, or a spherical surface 2a,
3a to avoid sliding frictional contact between the cages, and roller guide surfaces 1b, 2b, and 3b that are also formed with high precision on the outer circumferential surface of the cage to adapt to the rectangular inner circumferential shape of the circulation path.
This allows for smooth running within the bearing inner ring path.

Figure 11 shows the V of the rollers formed in the load bearing area of the present bearing.
a path formed between an iR-shaped raceway surface and a raceway surface of a V-groove roller formed on a bearing guide shaft corresponding to the raceway surface;
When a roller retainer is provided in a circulation path formed in the bearing that is connected to this and a linear motion rolling guide is configured, the formation of the circulation path, which can be set with the present bearing, and the formation of the circulation path into the path. This shows how to arrange the cages.
), (B), (C1, (D) are plan views of the cage 2 arranged in the circulation path and the rollers 5 in the cage formed between the above bearing and the guide shaft, (A ), +B
), (C1, (D) are the guide shafts and both sides of the V-shaped rollers formed on the bearings shown in FIGS. The roller 5 and the axis of rotation of the coin roller are shown in a side view in the path where the coin roller rotates.
A') is a V formed on the side of a shaft with a rectangular cross section in the axial direction.
With grooved sides.

A V-shaped raceway surface 7 formed on the side surface of the bearing corresponding to the raceway surface.
Figure (B) and (B
In '1, the arrangement of the cage inner rollers in the circulation path of the guiding shaft and the rollers between the bearings, which are formed in the same way as in the case of the above figures (A) and (A'), is arranged so that the rotation axis of the rollers is (5) The rotational axis should be aligned with either one of the rotational axes, perpendicular to the rolling direction of the rollers in the path within the load-supporting range, and parallel to each other between the rollers. In Figures (C1 and (C')), both side surfaces and 7 of the V-groove rollers in the guide shaft and bearing are arranged at an angle of 45° with respect to the side surface of the rectangular shaft as shown. They are formed on the side surface, and are arranged between the raceway surfaces and in the wII! path in the bearing, in the cage alternately orthogonal to the axis of the rollers, and as shown in Figure (n).
, (D'), the above (C), (C'
In the formation of a circulation path between the same shaft and bearing as l, the above 181, +! Same as +').

Figure +B1, (
As in the embodiment [1'), this is an embodiment in which they are arranged in the circulation path along the rotation axis on either side.

In this way, in the present bearing, the above-mentioned V
When forming grooves on the outer circumferential surface of the rectangular guiding shaft, they were formed on both sides of the shaft or on the slopes of the corners between the side surfaces and the soil surface. ■
The V-groove raceway surface formed on the bearing corresponds to the raceway surface of the grooved rollers, and the rolling path of the square rollers is formed in the load area, and the circulation path is connected to both ends of the path and formed on the bearing. It was formed with a path for. (A) in the above figure in the Makoto path when feeding the rollers into the axially oval circulation path.

(In addition to the case where the rotational axes of the rollers are arranged perpendicular to each other as shown in C1, (B) in Fig. 1.

As shown in (b), two pairs of V-groove rollers are formed so as to support the load on both sides of the guide shaft, as in the example shown in FIG. 16 of the bearing example of the present invention described later. (A) in the figure for the raceway surfaces of a pair of V-shaped rollers formed below both sides of the guide shaft.

As shown in (A) to (DT), the rotational axes of adjacent rollers are arranged so as to alternately intersect at right angles within the circulation path formed in the bearing together with the single support range of the bearing. A pair of grooves are formed above both sides of the shaft to equally support the positioning between the guide shaft and the bearing, as well as the bearing load acting on the guide shaft in the vertical and horizontal directions. On the rolling surface of the roller, (B), 18' in the figure)
As shown in Figure 1, the outer circumferential surface of the roller maintains simultaneous contact with both sides of the V-shaped groove formed on the shaft and bearing in Figure 1, and the lower and upper raceway surfaces of 7, and the center of rotation between adjacent rollers is It is possible to roll by applying a bearing load that acts in parallel without crossing and at right angles to the upper surface of the guide shaft. Fig. 12 TA), +Bl, (C1 is a conventional non-circulating cross-roller type direct-acting rolling bearing, in which the cage for the linear-acting wheel bearing shown in Figs. 1 to 8 above is applied to the inner roller of the bearing. A circulating type single-row linear-acting rolling bearing configured with
(Δ) in the figure is a front view of the rolling linear motion guide composed of the above-mentioned bearing and the guide shaft, (81 and (C1) are the side view and plan view of the above-mentioned rolling linear motion guide. , 2 is a cage applied to the roller, 5 is a roller, and 6 is a cage applied to the roller.
7 is the raceway surface of the V-shaped roller formed on the guide shaft, and 7 is the raceway surface of the V-shaped roller formed on the bearing in the load bearing area.

9 is a guide shaft, 9a is a bolt hole for fixing in the attached figure, 0 is a bearing body, 10a is a screw hole for fixing a bearing, 12. +3 is a bearing component for forming a circulation path for rollers within the bearing;
Reference numeral 14 corresponds to a roller supplied into the bearing inner ring path.

A thin sheet metal 15 is a side plate at both ends of the bearing in the axial direction, and lsa is a dust seal added to the side plate 15 to prevent it from falling out of the bearing.

FIG. 13 is a perspective view of the bearing shown in FIG. 12 disassembled and showing each component of the bearing. The rolling surface 7 of the rollers, the threaded hole 10a for bearing fixation, the parts 12 and 13 for forming the W ring path of the bearing inner roller retainer, which are integrated with the ring bearing body, and the rollers. Sheet metal eyes to prevent rollers and cages from falling off from raceway surface 7, and side plate 1
A screw hole 10b for fixing the bearing circular circulation path 5 and an axial recess 10c for fitting together the bearing circular circulation path forming parts 12 and 13 are formed to prevent the retainer from falling off in the circulation II path. In the sheet metal 14 for the bearing body, holes +4b for fixing the sheet metal to the bearing body are
5, the convex portion 1sa of the sheet metal for forming a dust seal corresponds to the rolling surface of the V-shaped rollers of the guide shaft, and the screw hole 10b of the bearing body 10 corresponds to the screw hole 10b, and the structure is integrated into the bearing body. A mounting hole lsb for measuring is formed.

FIG. 11 corresponds to a guide shaft in which the V-groove rolling surface of the rollers to be transferred is formed in double rows according to the cross-roller system shown in FIG. 1Z and FIG. This figure shows an embodiment of the bearing structure of the present application in which the circulation path of the rollers rolling while supporting the load between the bearings is formed in a double row. In the figure, 2 is the roller cage, 5 is the roller, 9 9a is the linear guide shaft, 9a is the screw hole for fixing the linear guide shaft, 10 is the bearing body, 1
0a is a screw hole for fixing the bearing, 12.13 is a bearing component that forms a circulation path for the grooved rollers inside the bearing, and 14 is for preventing the rollers and retainer from falling off from the circulation path inside the bearing that occurs during bearing operation. Sheet metal, 14c is a screw for fixing the wrong sheet metal,
15 are bearing side plates at both axial ends of the bearing, and 15c are screws for fixing the bearing component 15 to the bearing body. In addition, (A) to (D) in the figure are front views of this embodiment, (6) is a side view, and (C) is a plan view. Side view of F-F
This is a cross-sectional view along the cross-sectional line, and in Figure fnl, the part is shown in Figure (A
) shows the structure of the bearing according to the cross-sectional line G-G of FIG. This is a double-row configuration instead of a single-row raceway configuration. Therefore, the bearings shown in these examples can be used at the front and rear of various machines.
When applying the linear motion guide of a horizontally or vertically movable table, bearings in which V-shaped grooves of the load area rollers are formed in a single row are installed on both sides of the movable table.
The bearing arrangement seen in the side view of Figure (B) and the upper and lower surfaces of both ends of the moving table in this embodiment correspond to the main load in the vertical direction of the moving table as shown in the side view of Fig. 14). In comparison with the case where a linear motion guide is configured by arranging bearings, the load bearing capacity of the bearing can be increased four times in this embodiment with respect to the main load acting in the vertical direction of the movable table. Further, the present embodiment is constructed by applying a direct drive wheel bridge. In the reciprocating movable table, each slope is formed into two rows of ■-shaped grooves to accommodate the large number of rollers arranged between the guide surfaces of the guide shaft and the bearing by the above-mentioned cross roller method. Through the rollers interposed between the rolling surfaces, it is possible to restrain the displacement due to the vertical main load on the upper surface of the moving table as well as the load acting in conjunction with the moving direction of the table in the horizontal plane.

Therefore, in the reciprocating motion of the movable table, the X-axis, y-axis,
Constrain 5 degrees of freedom out of the 6 degrees of freedom for translation and rotation in each axis, which are allowed in the three orthogonal axes,
For example, when allowing linear motion only on the The axis of rotation of the rollers in the load bearing area placed between them is parallel to the rolling surfaces of the rollers, which are the upper and lower, left and right sides, and also between the rollers. They are arranged parallel to each other while maintaining a right angle to the running direction.
Although it is possible to support a load in the direction perpendicular to the guide surface, it is not possible to expect a restraining force against loads in three directions on the raceway surface of this embodiment. When configuring a linear motion guide for a shaft or a moving table, in the above-mentioned conventional roller bearing, a total of 4 It is necessary to arrange it in a plane to form a linear guide. In the bearing embodiment of the present application, as noted in -h, by forming the rolling surface of the V-groove rollers between the shaft and the bearing, it is possible to cope with loads in the vertical and horizontal directions between the shaft and the bearing. or the top and bottom surfaces of the moving platform,
Alternatively, by arranging them on both sides, the linear motion rolling guide structure of the shaft or the moving table can be simplified.

FIG. 15 shows, in an embodiment of the linear motion roller bearing of the present invention, a load is applied to the rolling surface of the V-groove rollers formed on both sides of the guide shaft on both sides of the moving table in the linear motion roller bearing of the present invention. In the figure, 2 is the roller cage, 5 is the roller, 6 is the V-groove roller raceway surface on the guide shaft, and 7 & i bearing @ V
9 is a guide shaft; 9a is a screw hole for fixing the guide shaft; 10 is a bearing body; 10a is a screw hole for fixing the bearing body relative to the movable table; +2. +3 is a part for forming a circulation path for the inner rollers of the bearing, 15 is a bearing side plate, and +5c is a screw for fixing the side plate to the bearing body 10. As shown in the figures, in this embodiment, the guides have a rectangular cross-sectional shape and are formed on both sides of the accompanying drawings. In the bearing body 10, the raceway surfaces 7 of the 90° V grooved rollers in the load bearing region are formed corresponding to both side surfaces of the pair of 90° V grooved rollers. A pair of m-ring path forming Vs in the bearing component 12.13 shown in FIG. 13 of the bearing embodiment of the present invention are connected to both ends in the axial direction, and the circulation path of the bearing inner rollers is shown in FIG.
Similar to shape grooves +2a and +3c, the bearing inner axial direction oval shape alI that connects to the load bearing area! ! The bearing component parts 12 and 13, which have V-shaped grooves for path configuration, are adapted to the bearing body weight ◎ as shown in the figure to form a circulation path for the bearing inner rollers, and also to form a circulation path in the axial direction of the bearing body 1G. On both end faces, side plates 15 for positioning are fixed on the bearing body of the bearing components 12 and +3.
The bearing is constructed by fixing the copper plate to the bearing body with screws 15c.

Therefore, in the above-mentioned linear motion guide, the rolling motion of a pair of V-groove rollers in the load bearing area formed on the bearing surface corresponds to both sides of the pair of V-groove rollers formed on both sides of the guide shaft. surface 7, a semicircular arc extending to both axial ends of the rolling surface 7 of the roller, and a linear path extending to the other end of the semicircular arc.

In the circulation path formed in an axially oval shape.

Scope of patent claims! ) A large number of rollers to which the cage described in ) is applied are arranged so that the axes of the rollers are alternately orthogonal to each other, and when the bearing is operated, the loads acting in the vertical and horizontal directions of the bearing are transferred to the above-mentioned guide. The rollers shown in the attached drawings and between the V-groove raceway surfaces formed on the bearing body 10 can be operated with an even load applied to them.

As shown in Figure 16 (A) to (D1. (B), double rows of raceway surfaces of grooved rollers are formed on each of both sides of the guide rectangular shaft to correspond to the raceway surfaces. FIG. 17 shows a front view and a side view of an embodiment of the linear acting roller bearing of the present application, which has a higher load capacity than the embodiment shown in FIG. 15, and FIG. 17 shows a perspective view of each component of the bearing embodiment. In these figures, 2 is a retainer applied to the inner roller of the bearing, 5 is a roller, and 6 is a grooved roller in the above attached guide diagram. 7 is the raceway surface of the V-groove roller in the load area formed on the bearing, 9a is the screw hole for fixing in the attached figure for guidance, 10 is the bearing body, 10a is for fixing the bearing on the moving table The screw holes 10b and Inc are the bearing body 1
The screw hole 14 is for fixing the side plate 15 to 0, and 14 is the load area V in the bearing internal ring path when the bearing is removed from the guide shaft.
Sheet metal for preventing the rollers from falling off from the groove 1A is a hole formed in the wrong sheet metal to prevent the rollers from falling off, +4b is a hole for fixing the sheet metal to the bearing body 10, and 15 is a ring bearing. ■ Side plate with molded groove + sd for forming circulation path of inner roller,
+6b is attached to the side plate by mounting screw lsc! 5 to the wheel holder body 1
0, a screw for fixing in the screw hole 10b,
ISe is a mounting hole for fixing the V-shaped groove ISa formed in the side plate 15 to the bearing body using a screw Isf. This is a bearing component in which V-shaped grooves 16a and 16a' are formed to form a circulation path. Therefore, in this embodiment of the linear roller bearing of the present application, as shown in the attached FIGS. 16A), 1B1 and 17.

Two pairs of V-groove rollers are molded on each of the two side surfaces of the guide square in the attached drawing, and two pairs of V-groove rollers are formed at two locations on both inner side surfaces of the frame-like bearing body 10 corresponding to the two side surfaces. The raceway surface 7 of the grooved rollers is molded, and the raceway surface 7 of the bearing body, which corresponds to both side surfaces of the rollers 11 and forms the bearing-side load area raceway surface, is provided at both axial ends of the raceway surface 7. The running path of the bearing rollers and cage is formed by the V-groove guide grooves ISd formed on the bearing side plate 15 and the same V-groove guide grooves 16a, 16a formed on the bearing component parts 16 and 16'. The large number of rollers 5 supplied together with the roller cage 2 into the 11 fl path rolls in the load area between the attached figure and both sides of the V-groove rollers formed in the bearing body 10. When running, as in the embodiment shown in the attached Fig. 15, the rollers are alternately perpendicular to the rotational axis on each rolling surface formed in a V-groove shape consisting of two orthogonal planes on both sides of the guide shaft. Through the large number of arranged rollers, the loads acting on the bearing in the upper, lower, left and right directions can be applied equally, and the value of the load capacity is compared with the value of the embodiment shown in the attached Figure 15 above. can be doubled in

Figure 18 (Al, (81, Figures 19 and 20)
The diagram is.

In the bearing structure of the present application shown in the above-mentioned attached FIGS. 15 and 16, in order to further improve the bearing load capacity and bearing rigidity, as shown in the figure, the axis of both sides and the upper surface of the bearing guide shaft is A pair of inclined V-groove rollers were formed at the corners of the direction, and the rollers were formed on both sides of the guide shaft opposite to the rolling surfaces. The cylindrical surfaces of a large number of rollers arranged alternately and perpendicularly to the raceway surfaces of the other l pairs of inclined V-groove rollers according to the above-mentioned cross roller system are connected to the raceway surfaces of the guide shaft. Tilt between a plane parallel to the top and bottom and two planes perpendicular to both sides @
It is configured so that it alternately maintains contact with two rolling surfaces formed in a V-groove shape and can roll while supporting vertical, horizontal, and horizontal loads acting on the bearing.

That is, attached FIG. 18 (Al, (B)) is a front view and side view of the embodiment of the present application, FIG. 19 is a perspective view of the bearing component in the embodiment of the present application, and FIG. 20 is a further diagram of the bearing component. 2 is a projected view of the w-ring path component parts in the bearing, and in each of these figures, 2 is a cage; 5 is a
6 is the raceway surface of the V-groove rollers on the guide shaft, 7 is the raceway surface of the V-groove roller formed in the bearing internal load area, 9 is the guide shaft, 9a is the attached diagram for the guide Bolt hole for medium stationary use! 0 is the bearing body, 10a is a screw hole for fixing the bearing to the moving table, job is a screw hole for fixing the side plate 15 to the bearing body, 10d is a hole for arranging a tubular part for forming a circulation path for the inner rollers of the bearing, 15 is the bearing side plate, 15b is the bearing body 10
lsc is the screw for fixing the side plate 15 to the bearing body, lSg is a recess for the bearing circular circulation path forming parts 17 and 18 to the copper plate 15, lS
h is a recess for positioning the bearing component with respect to the side plate 15, 1
7 is a bearing component for forming a curved part in the circulation path of the bearing inner rollers together with 18; 17a and 18a are V-shaped parts formed on the bearing components 17 and 18 to form a curved part in the circulation path of the rollers; Grooves 17b and 18b are V-shaped grooves for forming joints between components of the circulation path of the oval rollers in the bearing inner axial direction, and 17c and 18c are parts for the side plate 15 formed to correspond to the recess 15h of the bearing side plate. 17.18 Positioning convex portions, 17d and 18d form a positioning convex portion between the above-mentioned eye and 18 and a hole for fitting the convex portion, I9 forms a straight running portion of the circulation path of the rollers in the bearing. In order to do this, a square hole 19a is formed in the axial direction, and at both axial ends
This is a tubular intra-abdominal circulation path component whose joint surface is shaped to correspond to the joint formed by the V-bulges 17b and 18b in the parts 17 and 10 that form the curved portion in the path.

Therefore, in the above-mentioned embodiment of the linear motion roller bearing of the present invention, as shown in the attached drawings, both side surfaces of the pair of inclined V-groove rollers are formed at the corners of the 0 both side surfaces and the top surface in the attached drawings for guidance. 1, which corresponds to the rolling surface and is formed into a downwardly inclined V-groove shape separated by a certain range on both sides as shown in the attached diagram for guidance.
The embodiment shown in FIGS. 18 to 20 attached above includes a raceway surface 7 in the load bearing area in the bearing with respect to both side surfaces of the pair of rollers, and the l1lifIA path of the axially oval rollers. The guide shaft includes the center line of the rollers arranged on the rolling surface of the guide shaft, as shown in the attached FIGS. 8 and 9, without being parallel to the mounting surface of the guide shaft. The first
Bearing circular path components IT and I shown in Figures 9 and 20
l1 and 19 are arranged in the mounting hole 10d formed in the bearing body and in the concave fi15g of the side plate 15. In this embodiment with such a configuration, the main loads acting on the top, bottom, left and right of the bearing are as follows. , Figures 15 and 16 attached above.
The outer periphery of the roller interposed between the raceway surfaces of the V-groove rollers formed on both sides of the guide shaft shown in the figure and the V-groove roller raceway formed in the bearing circular load area corresponding to the raceway surfaces. Unlike the bearing configuration in which the rollers are supported between the rolling surfaces inclined at 45 degrees with respect to the direction of the main load acting on the bearing, the load supporting force of the rollers between the guide shaft and the bearing rolling surface is The contact stress between the shaft and bearing is not resolved vertically or horizontally, but directly acts as a load supporting force in the direction perpendicular to the main load on the guide shaft and bearing, and the main load on the bearing is It is possible to improve the load bearing capacity of the bearing in the horizontal direction as well as on both sides of the guide shaft, and in the direction in which the bearing load is applied in the vertical direction of the bearing. Regarding the bearing stiffness value related to the amount of elastic proximity between the guide shaft and the bearing, see attached No. 15.
18 to 20 above.
In this embodiment shown in the figure, the bearing displacement type with respect to the shaft is small, and it is possible to improve the bearing rigidity value under the action of a load. Furthermore, in accordance with the characteristics of the roller retainer for the present bearing, which is basically formed with a spherical outer circumferential surface, as shown in the above-mentioned attached FIGS. 8 and 9, the present bearing structure is implemented in which the circulation path of the bearing inner rollers is formed three-dimensionally. In this example, in this type of bearing where the three-dimensional volume of the bearing is limited, it is possible to increase the radius of curvature of the curved part in the inner ring path of the bearing so that the rollers in the path can run smoothly. .

Attached Figures 21 (A) to (D), +B+ and Figures 22 (A) to (D), (B) are the same as the above attached Figures 15 to 1.
It is constructed to correspond to the rolling surfaces of the rollers, which are molded on both sides of the square guide shaft shown in Figure 9. In the embodiment of the linear motion roller bearing, the structure of the linear motion roller bearing of the present invention is shown which differs depending on the characteristics of the bearing load acting on the bearing, the ease of bearing construction, and the method of positioning the bearing with respect to the moving table.
In these figures, 2 is a roller cage, 5 is a roller, 6.6a is a roller rolling surface formed on a guide shaft, and 7.7 is a roller cage.
a is the rolling surface of the rollers in the bearing circular load support range, 9 is the guide square shaft, 9a is the fixed bolt hole in the attached figure, 10 is the bearing body, 10a is the screw hole for fixing the bearing body, 15 is the bearing side plate , 19 are tubes for forming an axial circulation path inside the bearing.

First, in the embodiment shown in FIG. 21, (Al in the figure is a front view showing a section of this embodiment, and figure (B) is a side view showing the same section as a section. In this embodiment, both sides of the two pairs of rollers molded on both sides in the attached diagram for guidance are V-shaped, and 68 mm.
As shown in the figure, one side inclined raceway surface of the V-groove raceway surface is formed in the axial direction of the corners of both side surfaces and the top surface in the attached drawing, and the inner surface of the bearing is formed in correspondence with these raceway surfaces. The circulation path of the rollers is inclined on the upper and lower surfaces and both side surfaces of the bearing body, and is located at the four corners between two adjacent surfaces of the outer peripheral surface of the bearing body, as in the embodiment shown in the attached FIGS. 18 to 20. hand.

Tubular parts for forming the travel path in the axial direction! 9, and in the bearing circular circulation path, the guide shaft is formed at the corner between the surface and both side surfaces, and the rotation axis of the roller in the bearing internal circulation path formed corresponding to both side surfaces a. The cores are arranged parallel to each other in accordance with the above-described cross-roller method, without intersecting each other, and corresponding to both side surfaces a of the guide shaft.

Next, in the embodiment shown in attached FIGS. 22(A) to (D1.(B)), l pairs of inclined V-groove raceway surfaces are formed at the corners of both side surfaces and the top surface in the attached figures as shown in the figures. In this case, according to the embodiment shown in attached Figs. 18 to 20, and in the case of a V-groove raceway surface formed with a bar at the center of the shaft angle side surface, the attached Fig. 15 is applied.
The bearing is constructed according to the embodiment shown in the figure, and the arrangement of the rollers in the bearing internal circulation path is determined depending on the bearing load acting direction, for example, for a main load acting from above to below the bearing.
In the inclined V-groove raceways formed at the corners of the upper surface and both side surfaces of the shaft, the axis of rotation of the rollers in the load region of the shaft and bearings is aligned parallel to the upper and lower surfaces in the attached diagram. ■For the groove-shaped raceway surface and the roller between the bearing circle load area raceway surface, which is arranged and molded at the center of both sides in the attached diagram above,
When arranged to apply loads according to the cross-roller method described above, among the loads that act on the bearing in the vertical and horizontal directions, the main load that acts from the top to the bottom is mainly applied to the top surface of the shaft. Inclined V molded into the corners of both sides
Loads acting on the groove-shaped raceway surface, and in the left-right direction and from the bottom to the top, can be applied to the V-groove raceway surface in the center of the wheel side surface. It is possible to improve load characteristics.

Figures 23(A) and +B) show the bearing of the present application in the bearing corresponding to the rolling surfaces of the rollers formed on both sides of the square guide shaft shown in the attached Figures 15 to 22. Similar to the bearing configuration in which a cage is applied to form the circulation path of the rollers, the rollers attached inside the bearing correspond to the rolling surfaces of the balls formed on both sides of the square guiding shaft. A front view and a side view of an embodiment of a linear motion ball bearing configured by forming a circulation path for balls to which the bearing retainer of the present application is applied, and attached No. 24
Figures (A) to (D1. (B) are also partially enlarged views of the above-mentioned linear motion ball bearing configuration.
In Figure 4.

4 is a ball holder, and 6C is a sloped V formed on both sides of the guide shaft.
Ball rolling surface on one running surface of the groove-shaped cage, 7c corresponds to the above-mentioned both sides, and ball rolling surface in the bearing load area formed on one side of the inclined V-groove cage running surface, 9 is a guide. Axle for use, 10
15 is a bearing body, 15 is a bearing side plate, 16 is a bearing component for forming a circulation path, 20 is a ball, and 14 is a metal plate for preventing the ball from falling off from the rolling surface in the bearing load area.

As shown in the figures, in this embodiment, the balls in the load bearing area formed on the rolling surface of the balls molded in the bearing body 10 are connected to both ends in the axial direction of the running path of the ball retainer, and the bearing Similar to the embodiment shown in FIGS. 16 and 17 attached hereto, a V-shaped groove I is formed in the bearing 18l@15 and the bearing component 16.
Sa and +6a form a circulation path of the bearing internal cage, and the holding @ 4 shown in double box 1 (D) and Fig. 5 is applied to the balls circulating in this path. As with the rollers of the linear acting roller bearing width of the present application, a large number of rollers in the path always avoid direct contact between adjacent rollers via the ball cage, and between adjacent ball cages in the path, Due to the rolling contact between the spherical outer circumferential surfaces of the inner curved portions, relative sliding friction between the cages does not occur, and when the cage is running on its own path, the above-mentioned bearing circular circulation path wall 1sa, It is guided by the travel guide surface 4b, which is formed with a slight gap between it and the guide surface 16a, and can be expected to run smoothly in the path without meandering of the in-path holder.

Therefore, unlike conventional linear motion ball bearings of this kind, which are configured without applying a cage to the balls in the bearing circular circulation path, in this embodiment of the bearing configuration, a cage is installed between the guide shaft and the bearing. Under the action of preload and bearing load, impact contact pressure fluctuations between the balls acting between each of the balls in the path described in the attached Figure 10 above and repeated during movement from the circulation area to the load area and , one-pair noise due to the collision between the adjacent gap and the ball and the path wall due to contact pressure fluctuations, and the increase in running friction force proportional to the contact pressure between the ball and the path wall caused by the meandering of the inside path method. Avoiding the occurrence of vibrations in the bearing accompanied by vibrations, and the deterioration of bearing guidance accuracy and bearing friction and wear characteristics during operation.
A high performance linear motion ball bearing for rolling linear motion guide can be constructed.

FIG. 25 compares the differences in IIL load characteristics in the vertical and horizontal directions of the bearing for each of the embodiments of the linear motion rolling guide of the present invention explained in the attached FIGS. 15 to 24. In the valley embodiment, the size of the rolling elements in the load area and the number of rolling elements are the same, and in each of the embodiments in which rollers are used as the rolling elements in the figure, the rotation axis of the roller is ) to (D) to (H), the axes of the rollers are arranged perpendicular to each other, or the axes of adjacent rollers are arranged parallel to each other. (A) in the figure is shown.
~(D)~(11) The load capacity in the vertical and horizontal directions of the bearing, indicated by arrows on the right side of each figure, is determined by the pair of V-groove rollers formed on both sides of the shaft in Figures (A) to (D). This figure is shown in comparison with the load capacity of the load capacity bearing example shown in the attached FIG. 15, which has equal load capacity in the vertical and horizontal directions, and is constructed by arranging rollers in accordance with the above-mentioned cross roller system with respect to the running surface.

Therefore, in each of the bearing embodiments of the present application, in the bearing configuration in the embodiment shown in attached FIG.
In the case of FIG. 18), in which rollers are arranged on all of the pair of V-groove raceway surfaces according to the above-mentioned cross roller method, the load capacities of the bearings in the vertical and horizontal directions are as shown in FIGS. (A) to (D). The load capacity is doubled, and as shown in Figure (C), the bearing structure is the same as in Figure 181, and the two pairs of V-groove raceway surfaces molded on both sides of the attached figure. , when the rollers on the V-groove raceway surfaces of l pairs located in the L direction are arranged as shown in the figure, the load acting from above the bearing is For loads acting from below, it increases, and conversely for loads acting from below, it decreases. In addition, in the diagram (D) showing the bearing structure of the embodiment in the attached Figure 21, the bearing structure is somewhat different from the embodiment in Figure fcl, but the arrangement of the rollers with respect to the raceway surface in the attached diagram This is the same as case C), and the bearing load capacity for vertical and horizontal loads acting on the bearing is the same in both cases. In Figure (E), regarding the two pairs of raceway surfaces on both sides in the attached figure, the upper pair of raceway surfaces is formed into a V-groove shape, and the lower gs pair of raceway surfaces is formed into an arc shape. , rollers and balls are arranged on these rolling surfaces as shown in the figure, and the upper and lower parts of the bearing,
The load capacity for loads acting on the left and right sides differs and decreases depending on the direction in which the load is applied, from above to below the bearing, from left to right, and from below to above. Attached Figures 18 to 20
In the embodiment shown in Figure (F) according to the bearing configuration shown in the figure, the bearing is constructed by arranging rollers as shown on each of the two pairs of raceway surfaces formed on both sides of the guide shaft. The load capacity is equal in the vertical and horizontal directions of the bearing, similar to the embodiments shown in the above figure (Al) and figure fB). It is about 1.5 to 3 times larger than the example.

The embodiment shown in Figure (G) has the same bearing configuration as Figure (F), but has rollers arranged between the rolling surfaces in the q heavy load area as shown in the figure, and the bearing load capacity on the upper and lower and left and right sides is , Figure (F)
Compared to the embodiment, the load capacity for loads acting downwardly is doubled, and the load capacity in the left and right direction is halved correspondingly to the load capacity. In the diagram (H) showing the bearing configuration shown in attached Figure 22, the diagram (Gl
As in the embodiment, the load capacity for loads acting from above to below the bearing is large, but the load capacity from left to right of the bearing and the negative joint capacity from below to above are smaller than in the case of Gl. In the embodiment shown in the above attached FIGS. 23 and 24, the bearing load capacity in the bearing configuration shown in FIG. The value of is smaller than the value in the embodiments shown in FIGS. (B) and (F), in which rollers are arranged and configured, similar to this embodiment.

Therefore, each linear motion guide roller of the present invention corresponds to one or two pairs of rolling surfaces formed on both sides of the above-mentioned square guide shaft, and forms a circulation path for the rollers disposed in the bearing according to the cross roller system. In the bearing embodiment, the load-bearing characteristics of the bearing, which can cope with loads in the vertical and horizontal directions of the bearing, and the arrangement of the rollers in the path, as shown in the example in the figure above, are as follows. The axes of all adjacent rollers are arranged to intersect or parallel, or the axes of the rollers are arranged intermittently in the path at a ratio of 1 for every 2 rollers, 1 for every 3, etc. Therefore, in the bearing configuration of the present application, in response to the magnitude of the bearing load that acts on the top, bottom, left and right sides of the bearing, the load capacity of the bearing is adapted and the static and dynamic rigidity of the bearing is improved. It is possible to set an appropriate preload for the purpose, and it is possible to respond to the various bearing load characteristics required for this type of bearing.

Therefore, these linear motion rolling bearings of the present invention are formed of two mutually orthogonal planes.

Marked on - of a pair of guide shafts with V-groove raceway surfaces
In the path formed on the shaped raceway surface, in which two pairs of raceway surfaces are formed in the axial direction of the guide shaft, the length is slightly shorter than the diameter (the shaped roller is placed on the axis of the roller). orthogonal to each other,
Arranged at equal intervals in the axial direction via a sheet metal retainer.

Non-circulating linear motion according to the cross roller system, in which the rollers in the above path alternately maintain contact with the two pairs of rolling surfaces in the above path, supporting the load and rolling. The roller bearing is configured as a circulating linear roller bearing according to the cross-roller method of the linear roller bearing, so it is newly shown in the attached FIGS. 1 to 5. A cage was devised to be applied to the rollers for the above-mentioned circulating roller bearing, and then the rollers to which the cage was applied were assembled according to the cross-roller system in which the axes of adjacent rollers intersect, as shown in the attached Figures 6 to 4. Alternatively, the axes of adjacent rollers can be arranged in parallel with each other in an axially oval circulation path formed in the bearing, and according to this construction method, the attached rollers shown in Figs. 25th
The linear roller bearing shown in the figure has the following features compared to conventional bearings of this type.

In other words, corresponding to the V-groove raceway surface of the rollers arranged according to the cross-roller system, which is formed on the guide square shaft, the V-groove raceway surface in the load bearing area is connected to both axial ends of the V-groove raceway surface formed in the bearing. In the circulation path of the axially oval rollers formed in the ring bearing, the area is perpendicular to the circulation direction formed between the bearing load area and the rolling surface of the V-groove rollers formed on the guide square shaft. In order to ensure smooth circulation of the rollers while adapting to the walls of the circulation path, which are formed in a rectangular cross section, the present invention was newly designed to be applied to the rollers in the circulation path. The roller cage shown in the attached Figures 1 to 5 has been developed, and in this cage, as shown in the attached Figures 1 to 11 above, the contact surface between the cages in the path is Each cage is formed into a cylindrical or spherical surface, and the cages always run while maintaining line contact or point contact between their outer circumferential surfaces. Therefore, even in curved sections in the path, the cages can roll without relative slipping between them. Even when contact is continued and contact pressure is generated between the cages, mutual interference between the cages can be kept to a minimum, and smooth movement of the machine in the path can be achieved. In addition, between the cage and the circulation path, the wall surface of the bearing inner circular circulation path is formed corresponding to the rolling surface of the two pairs of V-groove rollers formed on the guide shaft and the bearing in the bearing load area. The outer circumferential surface of the cage is
In order to avoid bias in the rolling direction of the cage inner rollers with respect to the load-bearing area raceway surface in the circulation path and to ensure smooth running of the cage in the path, the distance between the walls of the circulation path is With a slight gap in between, four running guide surfaces are formed on the outer circumferential surface of the retainer as shown in the attached figures 1 to 5 above,
This is intended to avoid interference between the retainers in the path and to facilitate smooth running of the retainers in the circulation path and the rollers inserted into the retainers.

Therefore, the linear acting roller bearing of the present invention is a high-performance circulating linear roller bearing newly constructed according to the above-mentioned cross roller method. We can expect great results.

■ About the bearing configuration In the 1lIl1 type linear acting roller bearing for linear acting guide in this application,
A cage to be applied to the inner rollers of the bearing as shown in the attached figures 1 to 4 is newly molded, and the cage is applied to the rollers to form the attached figure in the axially oval circulation path inside the bearing. Each of the bearings shown in attached Figs. 12 to 24 is arranged according to the cross roller system shown in Figs. Corresponding to the bearing configuration in the embodiment, the circulation path of the bearing inner roller is configured, and therefore, in the bearing embodiment of the present application, application to various machines is attempted according to the structural characteristics of the bearing, and each In the bearing configuration in the embodiment, the diameter of the rollers for the bearing configuration can be changed, for example, to correspond to machines that are applied from small precision measuring instruments to large machine tools, industrial machines, etc. , 5 to 20 mm, an extremely wide variety of bearing configurations are possible.

In addition, in the bearing configuration shown in the figures attached to this application, the load capacity of the bearing can be set in accordance with the magnitude of the bearing load in the vertical and lateral directions of the wheel bearing, as shown in attached Figure 25. can. In other words, in the present bearing, the above circulation I
By applying the cage of the present invention to the rollers in the II path, it is possible to not only facilitate the circulation of the rollers in the path, but also
For example, as shown in the attached FIGS. 8 and 9, corresponding to the direction of the bearing load, the guide shaft may have the above-mentioned V groove shape on both sides, or an inclined groove at the axial angle between both sides and the top surface of the shaft. Corresponding to the roller raceway surface formed into a groove shape, it is possible to form a three-dimensional circulation path for the rollers that connects to both axial ends of the bearing load area raceway surface and the 1M raceway surface. The above ring.

The cross-sectional shape perpendicular to the running direction of the rollers in the circulation path of the inner rollers is formed into a rectangular shape as shown in 8 in the above-mentioned attached FIG. The route guide surface is shown in attached Figures 1 to 4.
As shown in lb, 2b, and 3b in the figure, the cage can run while keeping a small gap between the channel walls, corresponding to the channel walls having a rectangular cross section perpendicular to the running direction. In order to be The shape of the outer circumferential surface of the cage, which is formed symmetrically with respect to the axis of the rollers and arranged in the path corresponding to the shape of the inner circumferential surface of the path, is such that the axes of adjacent rollers in the cage are orthogonal to each other, Alternatively, it is the same when the rollers are arranged parallel to each other on their axes, and the relative positional relationship between the path wall and the outer circumferential surface of the cage when traveling in the path is also the same. Therefore, in each of the embodiments of the bearing of the present application shown in the attached FIGS. 12 to 22, the bearings are designed for the purpose of removing the bearing loads acting on the bearing in the vertical and horizontal directions and the gaps generated between the raceway surfaces. For each Mffl of preload, etc., the above bearing load is applied between the raceway surfaces of two pairs of rollers formed between the V groove shaped raceways formed on the shaft and the bearing, or between the inclined V groove shaped raceway surfaces. In order to equalize the load on a large number of loaded rollers, the axes of adjacent rollers in the cage are alternately orthogonal according to the crossed roller system, corresponding to the two pairs of raceway surfaces in the circulation path. In addition to arranging, alternately 2:1, 3:1
or all the rollers in the above load bearing area path without intersecting the axis of the rollers.
The rollers in the circulation path can be arranged so that they can be arranged in parallel, and according to this arrangement method, in the present bearing, for example, rollers molded on both sides of the guide shaft shown in attached Figs. 16 to 24 are used. In each embodiment of the bearing configuration, which is configured to correspond to a V-groove type or two pairs of inclined V-groove raceway surfaces, it corresponds to the main load acting on the bearing or the bearing preload, etc., as shown in attached Figure 25. This makes it possible to diversify bearing configurations.

2) Improving linear motion guide accuracy in the linear motion roller bearing of this application. Molded into the guide shaft and wheel bearing. A large number of rollers whose axial length is slightly shorter than the diameter are mounted on a V-groove rolling surface formed by two orthogonal planes.
The rollers are arranged in accordance with the above-mentioned cross-roller method through a cage, and the vertical and horizontal forces between the shaft and the bearing are restrained by two pairs of rolling surfaces orthogonal between the guide shaft and the bearing. In the configuration of a moving rolling guide bearing, the above-mentioned V-groove raceway surfaces of the shaft and bearing, the dimensional accuracy during the forming process of the rollers, the flatness, the perpendicularity between the two planes, the roller In this type of linear rolling bearing, the shape accuracy such as cylindricity can be achieved with extremely high precision, unlike the conventional circular groove rolling bearing that uses balls for the rolling elements. For example, in cases where ultra-precision cutting-edge technology is required in ultra-precision measurement equipment, ultra-precision machine tools such as electrical discharge machines, or bonding machines in high-density semiconductor manufacturing processes, A reciprocating movable platform is constructed using non-circulating linear roller bearings according to the roller system. However, in the non-circulating linear roller bearing according to the above-mentioned cross roller system, the stroke of the moving table 1 during reciprocating operation is due to the transfer of the rollers interposed between the guide shaft and the raceway surface formed on the bearing. , Due to the relative movement between the raceway surfaces, the length of the raceway surface of the shaft and bearing is limited to approximately 1/2, and as the moving platform reciprocates over a long period of time, the rollers between the shaft and bearing are Together with the sheet metal retainer applied to.

Although it has been recognized that the raceway surface can move from a fixed position in the axial direction, and the possibility of an extremely high-precision linear motion guide configuration has been recognized,
The scope of application to various machines has been limited. In the linear motion bearing of this application.

In view of the accuracy characteristics of the non-circulating cross-roller type direct-acting roller bearing, and by newly following the above-mentioned circulation system, it is possible to realize a high-precision direct-acting roller bearing that has not been seen in conventional products.

3) Regarding friction and wear characteristics In this type of linear motion rolling bearing in which circulating balls or rollers are interposed between the guide shaft and the bearing, the frictional resistance that acts overall on the bearing during operation is as shown in the attached article above. As shown in Figure 1O, the rolling friction force of the rolling elements in the load bearing area in the circulation path, the running friction force of the rolling elements against the circulation path wall, and the bearing load at the time of transition from the circulation area to the load bearing area. Resistance generated in the rolling elements due to the amount of elastic proximity between the ring and the bearing. This eliminates not only interference between the rolling elements but also friction between both ends of the roller axis and the path wall due to the skew phenomenon caused by deviation in the rolling direction of the rollers, and a straight line between the curved part and the circulation path. Even in the running section, the rollers are isolated within the cage without interference between them, and as described in FIG.
Alternatively, the sliding friction force between the cages is avoided by rolling contact between the spherical surfaces, and furthermore, the guide surface formed on the outer circumferential surface of the cage with a slight gap between the inner circumferential surface of the channel allows the cages in the channel to move between each other. Smooth circulation is ensured without meandering. In addition, the resistance that occurs when the rollers move from the circulation area to the load area is determined by the amount of elastic proximity between the shaft and bearing that occurs in response to the bearing load, compared to this type of bearing that uses balls as rolling elements. is a small value of 173 to 1 Ha, and the frictional force variation during bearing operation, which is caused by the resistance during the transition of the roller load range, is also significantly reduced, and the linear motion shown in Figs. In the linear motion rolling bearing of each embodiment of the rolling guide, the friction and wear phenomena between the rolling elements and the rollers, between the rollers and the load area raceway surfaces, and between the circulation path walls during operation are improved, allowing the bearing to last for a long time. It is possible to ensure a long life and maintain smooth bearing operating characteristics.

4) Regarding load capacity In the load characteristics of a rolling bearing in which a load is applied by interposing rollers or balls between two rolling surfaces, the diameter between the two surfaces is equal,
Furthermore, it is well known that the load capacity of rollers and balls whose length in the axial direction is equal to the diameter is about three times greater than that of balls. Therefore, for linear motion guides in various machines, attempts have been made to develop two circulating linear motion rolling shaft bearings that use rollers instead of balls in conventional products, but due to the difficulty of bearing construction, this type of bearing is still not widely used. There are no products that can be found to be compliant.

In the linear motion guide roller bearing of the present application, the above-mentioned attached figures 12 to 2
As shown in the examples of various bearings in Figure 2, applications are planned for linear motion guides in an increasingly wide range of machines, from small equipment such as various measuring instruments to space development machines such as machine tools. It consists of various types of high-performance circulating linear roller bearings with excellent load resistance.In particular, direct-acting linear roller bearings made of balls are used in recent cutting-edge technology and ultra-high precision machinery. 1 μm generated under the action of bearing cyclic load at the point contact area between the rolling surface of the ball and the core ball in the dynamic guide.
As a countermeasure against damage caused by minute peeling phenomenon at the front and rear, we have developed a new roller bearing with the aim of avoiding the above-mentioned raceway surface peeling phenomenon under load action in line contact in this type of bearing constructed using rollers. The aim is to realize a direct-acting roller bearing constructed using the following.

5) Concerning static and dynamic rigidity In a linear motion guide constructed using a linear motion rolling bearing with rolling elements circulating, the bearing load is applied between the contact surface between the shaft and the raceway formed on the bearing and a small number of rolling elements. This is due to the elastic deformation of the rolling elements. The elastic proximity between the shaft and the bearing greatly affects the static stiffness under bearing load, and the dynamic stiffness when a disturbance is applied to the bearing is determined by the above-mentioned static stiffness of the bearing, the natural frequency of the bearing, and the rolling elements and rolling elements. It is affected by the damping coefficient etc. caused by the contact situation between running surfaces. Therefore, in the present bearing, which uses rollers for the rolling elements instead of balls in conventional bearings, it is possible to secure 3 to 4 times the rigidity of the rolling elements themselves compared to the conventional bearings, and the static load The deformation of the bearing rolling elements under the action of the load, as well as the amount of elastic proximity between the bearing and the wheel raceway in the load area required for the deformation of the rolling elements, are minimized, ensuring bearing accuracy under the action of the load and smooth bearing operation. characteristics can be secured.

Regarding dynamic rigidity, the high static rigidity value mentioned above, which is directly related to the dynamic rigidity, and the damping coefficient of the rollers between the shaft and the two rolling surfaces of the bearing during vibration are approximately three times that of the case of five balls. Moreover, a cage is applied to the inner rolling element of the present bearing to promote the above-mentioned damping effect, and therefore, compared to conventional linear motion guides of this type that do not use a cage, the stress applied from the outside of the bearing is reduced. The value of the amplitude of the relative vibration between the shaft and the bearing, which indicates the dynamic rigidity when an excitation force acts on the bearing due to vibrations and vibrations generated when the rolling elements run in the circulation path including the above load area within the bearing. is small, and the harmonic noise induced by the above-mentioned vibrations, which occurs in conventional products, is also prevented.

6) Regarding molding of components In a linear motion guide configured using the bearing of the present application, as shown in the attached examples, a guide shaft and a bearing corresponding to the rolling surface of the rollers molded on the shaft are used. Furthermore, the bearing is formed by elements such as rollers, a roller retainer, a bearing body, a circulation path forming part for the rollers in the bearing, a sheet metal for preventing the roller retainer in the circulation path from falling off, and a bearing side plate. Ru. Of these components.

The molding of the roller cage shown in the attached Figures 1 to 4, which realizes smooth circulation of the rollers arranged in the cross-roller system within the bearing of the present application, is a cylindrical shape between the cages in the path shown in the figure. shape or spherical contact surfaces 1a to 4a, path self-propelled guide surfaces 1b to 4b, cylindrical holes for inserting rolling elements in the cage, and recesses 1c to 4c having rectangular and cylindrical shapes, or cylindrical shapes and spherical surfaces. , the hole or recess and the guide surface 1b~
The holes 1d to 4d necessary for contact between the rolling elements in the cage and the rolling surfaces for the grid rolling elements between 4b and the recesses 10 to 2e for reinforcing the cage on the outer peripheral surface of the cage are formed using metal materials, polymers, etc. With cutting methods from various materials, it is extremely difficult to ensure a high degree of machining accuracy of 0.011 units, which is required due to the operating characteristics and compatibility required for the cage. It is expected to be compatible with high-performance machines such as M-density measuring instruments and electrical/electronic equipment.
It is almost impossible to manufacture a cage for the linear motion guide rollers, which is constructed using rollers with a diameter of about 1 mm, and the number of cages required in the bearing inner ring path in the present linear motion guide is 10.
0 to 200, and it is impossible to supply such a large number of cages at a reasonable price.1. , the purpose of molding the outer circumferential surface of the cage and the shape inside the cage by injection molding from a molten polymer material using a mold that can mold the shape with a processing accuracy of 0.001 mm, 111, In addition to enhancing the various functions of the cage, the shape of the cage is determined to avoid the undercut shape that makes injection molding difficult. . The latest engineering plastic materials such as polyamide and polyacetal that have excellent strength, wear resistance, and heat resistance are reinforced with fibers such as glass and Kevlar, and solid lubricants such as molybdenum disulfide and Teflon are added. Using an injection molding method using a high-performance polymer composite material, the above-mentioned high-performance cage is lightweight, has high precision, and has excellent properties such as strength, durability, lubricity, and cushioning properties. It can be molded at a manufacturing cost. In addition, inside the bearing,
As detailed in the attached Figures 13, 17, and 19,
The parts for forming the circulation path of the bearing inner roller and cage, as well as the bearing side plates, can be molded by the injection molding method of the engineering plastic material mentioned above, just like the roller cage mentioned above. For the shaft, the bearing body and the guide shaft each have a cross-sectional shape perpendicular to the axial direction, as shown in the attached examples of this application. The design is designed in the form of a pedestal, square, or rectangular shape with constant axial direction, which streamlines processing by hot/cold R selection and rolling forming at the preform stage, and improves rolling element rolling surface in the load area. In particular, when forming the raceway surfaces of the high-precision rollers that are formed into the bearings and guide shafts mentioned above, it is easy to form the base surface necessary for precision machining and accuracy measurement, and it is possible to form high-precision straight lines. It is possible to ensure dynamic guide accuracy, and when the bearing is removed from the guide shaft, the thin sheet metal is formed to prevent the rollers and cage from falling off in the load bearing area of the bearing internal ring path. It can be easily molded with high precision by press molding from copper thread thin sheet metal or copper thread thin sheet metal.

In addition, in addition to the various characteristics of the bearing according to the cross roller system in the linear motion rolling guide of the present application described in 1) to 6) above, the cage applied to the rollers in the internal ring path of the bearing of the present application described above is shown in attached Figure 1. (D) As shown in Figure 5, an example in which the ball is used instead of a roller is shown in attached Figures 23 and 24.
As shown in the figure, this embodiment is constructed without applying a cage to the rolling elements. In this type of circulating type linear ball bearing, when the bearing is operated, collisions occur between the balls in the circulation path inside the bearing, and between the balls and the walls of the circulation path.
It is possible to avoid deterioration of bearing precision and performance due to vibrations within the bearing amplified by the natural frequency of the ball after 0.5 KHz, and generation of high frequency noise derived from the vibrations.

In short, the linear motion rolling guide of the present invention, as described in the attached drawings and detailed description, is a rolling bearing of this type in which a circulation path for rolling elements is formed within the bearing, and in the wyA path inside the bearing. In the conventional linear motion rolling bearing, which mainly uses balls, we have improved the bearing's simple structure, which uses rollers as rolling elements, and the bearing's linear motion guide accuracy, load capacity,
We focused on the non-circulating cross roller system, which has been recognized as having the best characteristics in terms of performance such as durability, but has been considered impossible to develop into a smoothly operating circulating linear roller bearing.
In order to realize a circulating linear roller bearing according to the cross-roller method, newly attached figures 1 (A) to (D) to TCI
Then, we devised a cage to be applied to the rollers in the bearing circulation path as shown in FIGS. 2 to 4, and installed the cage together with the inner rollers in the cage. They are arranged in the circulation path and are formed in single or double rows on one side, both sides, or the upper surface of the bearing guide square shaft, as shown in the bearing examples of the present application in the attached Figures 12 to 23. V groove shape,
Inclined V-groove shape Corresponding to the rolling surface of the rollers mentioned above, the bearing internal negative load is connected to both axial ends of the 9-region rolling surface, and is formed into an axially oval shape to supply a large number of rollers within the circulation path. 5 constitute the above-mentioned cross-roller type circulating linear roller bearing, realize the rolling linear motion guide according to the above method together with the above-mentioned linear motion guide shaft applied to the 1 bearing, and also realize the above-mentioned attached Fig. 1. (Dl and the fifth
The figure shows a ball cage that adapts to the shape of the cage applied to the above-mentioned rollers and can be applied to the balls in the ring path of this type of W-ring type linear motion ball-shaft capsule machine. Fig. 24 shows an embodiment of the above-mentioned Ili annular linear motion ball bearing configured by applying a holder. Compared to this type of bearing, which does not have a cage, this bearing realizes a high-performance linear motion bearing and a linear motion rolling guide constructed using the bearing.

[Brief explanation of drawings]

Figure 1 (Al-(D) is a perspective view of the retainer for bearing rolling elements of the present invention, and Figure 2 is a cylindrical view of the contact surface between the retainers in the bearing circulation path shown in Figures 1 (A) to (D). Figures 3 and 4 are projected views of the roller cage formed into a spherical shape, and Figure 5 is a projected view of the roller cage in which the contact surface between the cages in the path is formed into a spherical shape. Figures 6 and 7 are projection views of a legal cage in which the contact surface between the inner cages is formed into a spherical shape, and cages with a cylindrical or spherical surface formed on the outer peripheral surface are arranged in the bearing circular circulation path. Figures 8 and 9 are explanatory diagrams of the case in which the above-mentioned retainer having a spherical surface formed on its outer circumferential surface is arranged in a circulation path formed three-dimensionally within the bearing, and Figure 10 is an explanatory diagram of the above-mentioned case. An explanatory diagram of the circular movement of the cage arranged in the bearing circular circulation path,
The Nth space is also an explanatory diagram of the arrangement method of the cage in the bearing circulation path, and Fig. 12 is configured to correspond to a guiding square shaft with a V-groove raceway formed on one side surface and a 2M square shaft. Embodiment of a linear motion rolling guide constructed with the linear motion roller bearing of the present invention, Part 1
Figure 3 is an explanatory perspective view showing each part of the linear motion rolling guide bearing structure shown in Figure 12 above, and Figure 14 is a square guide shaft with a V-groove parallel rolling surface formed on the upper surface of the square shaft. FIG. 15 shows an embodiment of a linear motion rolling guide composed of a double row linear motion roller bearing of the present invention formed corresponding to the shaft.
A linear motion guide embodiment constructed of a guide shaft formed with a pair of V-groove raceway surfaces and a linear motion rolling bearing of the present invention formed corresponding to the raceway surfaces on the side surface of the wheel. A linear motion guide consisting of a guide shaft with a double-row V-groove raceway formed on each side of the shaft and a linear motion rolling bearing of the present invention formed corresponding to the shaft guide shaft, FIG. 17 shows the above-mentioned linear motion guide. Fig. 16 is a perspective view of a bearing forming element in a linear motion guide, and Fig. 18 shows a guide shaft with parallel inclined V-groove rolling surfaces formed on both sides of a square shaft. An embodiment of a linear motion rolling guide configured with a linear motion roller bearing of the present invention formed corresponding to the guide shaft rolling surface, FIGS. 19 and 20 are perspective views of the bearing forming elements in the embodiment shown in FIG. 1 above. Figures and projection views, and Figures 21 and 22 respectively show a pair of V-groove raceway surfaces on both side surfaces of the square shaft, and a pair of V-groove raceway surfaces at the axial corners between both side surfaces and the top surface of the square shaft. Implementation of a linear motion rolling guide consisting of each guide shaft formed with an inclined raceway surface or an inclined @ V-groove raceway surface, and a linear motion roller bearing of the present invention formed corresponding to the guide shaft. For example, Figure 23 is the above 16
Similar to the bearing configuration of the present application in the linear motion guide embodiment shown in FIG.
24 is an example of a linear motion guide constructed by employing a bearing formed by arranging balls in the above-mentioned circulation path together with the retainer for the present invention method in ). FIGS. 25A to 25D are partially enlarged views showing the bearing circular circulation path and the arrangement of the cages within the path. This is a comparative explanatory diagram of bearing load capacity values due to differences in the arrangement method of rolling elements via cages in the circulation path in which the rolling elements are arranged. A cage for rollers with a spherical surface molded on the outer surface.A cage for rollers with a spherical surface molded on the outer surface.A ball cage with a spherical surface molded on the outside surface. Roller rolling surface molded into a running surface Bearing Internal rolling element circulation path Wall sectional view Bearing guide shaft Bearing body Bearing Inner axial direction Elliptical rolling element circulation path Parts for forming the internal circulation path Bearing For forming the circular circulation path Components Sheet metal bearing for preventing holder falling off Side plate Bearing Components for forming circular circulation path Bearing Components for forming circular circulation path Bearing Components for forming circular circulation path Bearing Components for forming circular circulation path Engraving of sphere drawing J1 Figure (A) (B) CC ) CD) (C) (A) (B) (ε) h Condolence (A) (F) Eye (D) (C) Wake (A) (B) (E) (A) (Snake) Day (D ) Flute 6 ■ Kazu Atsume (Ra) (A) L3#-1 ÷ Fig. 10 (4) Zth mouth (A) CB) 1 1 14 (A) (8) ■ Brown) Fig. 13 2 (A) (E3) Whistle? Band (method) Display of the case 1999 Patent Application No. 327148 3゜Amendment Relationship with the case

Claims (1)

[Claims] 1) In a guide shaft for a linear motion rolling guide configuration and a direct motion roller bearing, a constant play is maintained between the guide shaft and the bearing,
A V-groove roller raceway surface consisting of a pair of orthogonal raceway surfaces is formed symmetrically on each of the bearing guide surface and the bearing surface, which are formed parallel to the operating direction of the bearing. The axial direction of a roller that corresponds to two pairs of raceway surfaces in a rectangular path formed by V-groove raceway surfaces and that rolls between any one of the two pairs of raceway surfaces. In order to avoid interference with the other pair of raceway surfaces on both end faces, a large number of rollers of the same size and shape, whose axial length is slightly shorter than the diameter, are mounted on the guide shaft. The present invention relates to a cage intended to be applied to each roller when the axes of the above-mentioned large number of rollers are arranged alternately orthogonally in the axial direction of the rolling path of the square rollers formed between the bearing and the bearing. On the outer circumferential surface of each cage, as shown by symbols 1 to 3 in the perspective views of FIGS. 1 (A) to (C) and the projected views of FIGS. 2 to 4, In the cage 1 shown in the above attached drawing, the contact surface is formed into a cylindrical surface indicated by the symbol 1a in the drawing, and in the cages 2 and 3 also shown in the attached drawing, the contact surface is formed into a cylindrical surface shown by the symbols 2a and 3a in the drawing. The cages 1 to 1 are molded into the spherical surfaces shown in order to avoid interference between the cages in the path.
On the outer circumferential surface of No. 3, a slight gap is set between the inner circumferential surfaces of the rectangular paths, which is necessary when the cage runs, and a gap is set symmetrically with respect to the center of the cylindrical or spherical outer circumferential surface of each cage. , rectangular cage running guide surfaces 1b to 3b parallel to the inner circumferential surface of the route.
The cage shown in the attached figures above is formed at the center of one pair of parallel guide surfaces in the two pairs of parallel guide surfaces on the rectangular running guide surface on the outer peripheral surface of the cage. 1 and 2 have cylindrical holes 1c and 2c for inserting the rollers into the cage with a slight clearance between the outer peripheral surfaces of the rollers to which the cage is applied, and the holes 1c and 2c. Corresponding to 1c and 2c, the other pair of guide surfaces 1b and 2b of the square cage guide surfaces 1b and 2b have outer circumferential surfaces of rollers inserted into the holes 1c and 2c in the cage. , 2 of the rectangular path between the guide shaft and the bearing.
Rectangular holes 1d and 2d are formed to maintain contact with any one of the rolling surfaces of the pair of rollers, and a V-groove rolling contact between the guide shaft and the bearing is formed. At four corners of the square guide surface on the outer peripheral surface of the cage, which is formed corresponding to the square path between the surfaces, there is a clearance between the guide shaft formed with the V-groove raceway surface and the parallel guide surface between the bearings. and corresponding to the square grooves for molding the groove bottom flank surface required during high-precision molding of the pair of V-shaped guide surfaces, and connected to the cylindrical or spherical surface of the outer peripheral surface of the cage, for reinforcing the cage. A convex portion 1e or 2e is formed. In addition, in the pair of parallel surfaces in the rectangular cage running guide surface formed by the two pairs of parallel surfaces molded on the outer circumferential surface of the cage 3 in the above attached drawing, the pair of parallel surfaces one side guide surface At the center of the roller, perpendicular to the guide surface, as shown in the figure, a roller whose axial length is shortened compared to the rollers when the cages 1 and 2 are applied is placed on the outer circumferential surface of the roller. A semi-circular cylinder corresponding to the outer circumferential surface of the inner roller of the cage is installed at the bottom of the hole in order to insert the roller into the cage from the outer circumferential surface of the roller while ensuring a slight gap between the two end faces in the axial direction. A rectangular hole 3d is formed to maintain contact between the cage inner roller and the rolling surface.
A rectangular hole 3c is formed. Next, cages 1 to 3 shown in the attached figures are attached to the rolling surfaces of two axially rectangular pairs of rollers formed between the rolling surfaces of the V-groove rollers formed on the above-mentioned guide shaft and bearing. The shape of the inner circumferential surface corresponds to the inner circumferential surface of the rectangular rolling path in the rolling direction of the rollers, and there is a slight play between the outer circumferential surfaces of the cage during running. The retainer in the bearing and the rollers in the retainer are formed by a semicircular arc path at both ends in the axial direction of the bearing, and a linear path range continuous to the other end of the semicircular arc path range. A circulating rolling path is formed, and when the cage is arranged in the circulating path that is formed in an oval shape as a whole by the circulating path and the rolling path of the guide shaft and the rollers between the bearings. As shown in each of the attached FIGS. 6 to 8, a large number of cages in the path have line contact between the cylindrical surfaces 1a on the outer peripheral surface of the cages, or spherical surfaces 2a,
3a, and with respect to the contact line or contact point, the center line of the rectangular inner circumferential surface of the circulation path is orthogonal to the contact line between the cylindrical surfaces 1a at the center of the contact line. In addition, the contact point between the spherical surfaces 2a and 3a is located on the center line, and the contact between the cages in the path is due to the cylindrical surface 1a or the contact between the spherical surfaces 2a and 3a, so that the cages are mutually connected during bearing operation. In addition, the contact pressure acting on the outer circumferential surface of the retainer in the path when the bearing is in operation, as shown in attached FIGS. It acts between the contact surfaces of the outer circumferential surface of the cage located at the center of the inner circumferential surface of the rectangular path, and corresponds to the shape of the inner circumferential surface of the rectangular path on the outer circumferential surface of the cage, with a slight play between the inner circumferential surfaces of the channel. The rectangular running guide surfaces 1a to 3b are formed symmetrically with respect to the center of the cage.
Then, it is applied to each of a large number of rollers 5, 5' arranged in a circulation path connected to both ends of the V-groove raceway surface formed on the linear motion rolling guide shaft and bearing of the present invention, and the above-mentioned circulation of the rollers is applied. A roller for a circulating direct-acting roller bearing, characterized in that it is formed so that it can roll in the load area between the shaft and the bearing in the path and smoothly run in the running range for circulation within the bearing. retainer. 2) In the roller cage 3 according to claim 1), a rolling path is formed on the outer peripheral surface of the cage and is a load support range between a guide shaft and a bearing for a linear motion rolling guide configuration, and a bearing in the path. The circulation path in the bearing is connected to both ends in the axial direction, and the contact surface 3a between the circulation path retainers, which is formed in an elliptical shape in the axial direction, the running guide surface 3b of the path retainer, and the inside of the retainer. A hole 3c for inserting the formed roller, and a hole 3c formed between the semi-cylindrical bottom surface of the hole 3c and the cage running guide surface 3b,
Each of the rectangular holes 3d for maintaining contact between the outer circumferential surface of the inner roller of the cage and the rolling surface of the roller is applied to a ball instead of a roller as a rolling element to which the cage is applied. The outer circumferential surface of the cage 4 shown in attached FIG. 1(D) and FIG. 5, which was formed for the purpose of , the same spherical surface as 3a on the outer circumferential surface of the cage 3, and the cage 2 for running in the path.
Unlike the guide surface 4b in the cage 3, which is formed into a rectangular shape in the running direction of the cage, the guide surface 4b consisting of a pair of orthogonal planes is parallel to the rolling surface of the balls in the path in the running direction. It is formed into a rectangular shape corresponding to a pair of guide surfaces with a short distance between the planes, and a holding surface is provided at the center of one guide surface of the pair of rolling surfaces corresponding to the rolling surfaces of the balls. The insertion opening 4c for the ball into the container is formed by maintaining a slight clearance between the outer peripheral surfaces of the balls to be fed into the hole 4c, and by forming the bottom surface into a hemispherical shape.
Between the spherical bottom surface of c and the guide surface parallel to the guide surface formed with the holes 4c, there is a ball-to-ball rolling hole corresponding to the hole 3d for maintaining contact with the roller and rolling surface in the cage 3. A round hole 4d is formed between the running surfaces, and the cage 4 is applied to a large number of balls, and the axial length between the guide shaft and the bearing is formed corresponding to the running guide surface 4b formed on the outer periphery of the cage. When supplied into the circular circulation path, the cage 4 and the balls supplied into the cage avoid direct contact between the balls, as in the case of the cage applied to the rollers. The spherical contact surface 4a minimizes mutual interference between the cages, and together with the outer circumferential travel guide surface 4b, smooth circulation within the circulation path is achieved during linear motion guide operation. Ball holder. 3) In a linear motion rolling guide configured by applying the roller cage described in claim 1 to a large number of rollers in a bearing, the guide method shown in attached FIGS. 12 and 13 and attached FIG. 14. A raceway surface 6 of a V-groove roller consisting of two perpendicular planes formed in a single row or in parallel on one side of the rectangular shaft and the upper surface of the rectangular shaft, and a raceway surface 6 symmetrically on each of the raceway surfaces 6. , a V-groove raceway surface 7 formed on the bearing body 10, which also consists of two orthogonal planes, and an internal circular arc shape in the bearing that is connected to both axial ends of the square rolling surface path of the roller, and the circular arc shape. In order to avoid interference between both end surfaces in the axial direction with respect to the inner circumferential surface of the circulation path, there is a Applying the roller cage to each of a large number of rollers whose axial length is slightly shortened,
V-shaped rollers formed on the guide shaft 9 and the bearing body 10 are arranged so that the axes of the rollers are alternately orthogonal to each other along with the cage, and are arranged corresponding to the two pairs of rolling surfaces formed in the square path. Rolling surface 6
and 7, and the vertical direction or the horizontal direction in each of the attached examples, which is orthogonal to the approaching direction of the raceway surfaces 6 and 7 and the rolling direction of the rollers on the raceway surfaces 6 and 7. To support the bearing load and when the bearing is in operation, the large number of rollers in the circulation path are arranged in a single row on the guide shaft and the bearing, with a pair of V-groove rollers that are easy to form with high precision. Molded with a slight clearance between the two pairs of rolling surfaces on the running surface,
The running guide surface on the outer periphery of the cage of the present invention ensures a high degree of perpendicularity between the axes of the rollers with respect to the rolling direction, and minimizes the sliding friction between both axial end surfaces of the rollers and the inner circumferential surface of the path during operation. In addition, the contact pressure between the cages during traveling in the circulation path is caused by the cylindrical surface formed on the outer peripheral surface of the cage or between the spherical surfaces, and is accompanied by the contact pressure in the circulation path including the curved portion. Avoiding interference between the cages and realizing smooth rolling and running of the cage rollers during bearing operation, the single row between the guide shaft and the bearing, and the parallel V-shaped rolling surface;
The cage according to the present invention is applied to each roller in the circulation path connected to the raceway surface and arranged to achieve smooth operating characteristics under the action of a bearing load in three directions within a cross section perpendicular to the bearing operating direction, and a guiding shaft. A linear motion rolling guide that is characterized by superior characteristics such as guiding accuracy, load resistance, and durability compared to conventional products that have a ball interposed between the bearing and the bearing. 4) In a linear motion rolling guide configured by applying the roller retainer according to claim 1 to a large number of rollers in a circulation path within the bearing, the shaft for linear motion guide configuration and the structure between the bearings are provided in attached No. 15.
Corresponding to the rolling surfaces 6 of a pair of V-groove axial rollers consisting of two orthogonal planes formed symmetrically on both sides of the square shaft 9 shown in the figure, and shown at 10 in the attached figure above, A small amount of play is ensured in parallel to both sides of the frame-like bearing body 10 that operates while being guided by both sides of the guide shaft 9, and on both sides of the guide shaft 9. The guide shaft is placed between the raceway surfaces of a pair of V-groove axial rollers formed symmetrically on each of the V-groove raceway surfaces and consisting of two orthogonal planes, as shown in 7 in the attached drawing. A roller rolling path is formed symmetrically on both side surfaces of the roller 9 and is formed of a pair of axially rectangular internal circumferential surfaces of the load bearing area, and then, at both axial ends of the pair of rolling paths, A semicircular arc continuous to the rectangular inner circumferential surface of the passage and a linear passage continuous to the other end of the semicircular arc form a circulation passage for the bearing inner rollers in an axially oval shape with the load bearing area passage. Then, the cage of the roller of the present invention is applied to each of a large number of rollers whose axial length is slightly shorter than the outer diameter in the path, and the roller axes are alternately crossed with the cage. Or, if they are arranged crosswise at a ratio of one for every two or one for every three, etc., and arranged alternately, the load capacity will be equal in the vertical and horizontal directions between the guide square shaft and the bearing. Correspondingly, the above-mentioned equal load capacity is maintained in the left and right directions, and the load capacity is set in a ratio of 2 to 1 or 3 to 1 in the up and down directions, depending on the number of rollers that carry the load. , it is possible to set a reasonable bearing load capacity corresponding to the magnitude of the load acting on the bearing in two directions, up and down, and in addition to smooth running of the rollers in the path by applying the cage of the present invention, Unlike conventional linear motion rolling guides, which are constructed using balls that require the formation of two pairs of rolling surfaces between the guide shaft and the bearing, the guide shaft and the bearing are formed into a V-groove shape with two orthogonal planes. The pair of raceway surfaces can rationally support the four-directional loads acting on the bearing (up, down, left and right), and the height between the mounting surface of the linear motion guide shaft and the top surface of the bearing is low. A high-performance linear motion rolling guide, which is characterized in that it can be applied to various machines that use a linear motion rolling guide and where the distance between a reciprocating table and a pedestal is restricted. 5) A linear motion rolling guide constituted by applying the roller retainer according to claim 1) to a large number of rollers in a bearing internal circulation path, as well as a linear motion rolling guide according to claim 4), for guiding purposes. Corresponding to the rolling surfaces of the rollers formed on both sides of the square shaft, the guide shaft is formed on the inside of both sides of the frame-like bearing body with a certain amount of play on both sides of the guide shaft. The rolling path of the square roller in the axial direction of the load bearing area roller, which is formed between the rolling surface of the roller formed on both sides of the square shaft and the rolling surface of the roller formed symmetrically, is connected to both ends of the bearing in the axial direction, In a linear motion rolling guide configured by forming a circulation path for axially oval rollers, the rolling surfaces of the rollers formed on both sides of the guide square shaft are formed by the linear roller according to claim 4). in a single row on each side of the square guide shaft for the moving rolling guide arrangement;
Also, unlike the pair of rolling surfaces formed symmetrically between both side surfaces, there are two pairs of rolling surfaces formed symmetrically on each side surface of the square guide shaft, and in parallel between both sides of the shaft. Regarding the raceway surfaces, in the embodiment shown in the attached FIG. 16, for all the raceway surfaces, a V-shaped raceway surface 6 consisting of two orthogonal planes is defined as shown in the attached FIG. 18. In the embodiment, a corner between both side surfaces and the upper surface of the guide square shaft 9, and a corner located midway between the both sides and parallel to the mounting surface of the square shaft 9, respectively;
and an inclined V-groove raceway surface 6a consisting of two orthogonal planes.
In the embodiment shown in the attached FIG. 21, a pair of rolling surfaces are located at the corners of both side surfaces and the top surface of the guide square shaft, and are composed of planes inclined at 45 degrees with respect to both side surfaces and the top surface of the square shaft. Surface 6b and
Similarly, the above two pairs of raceway surfaces formed by the V-groove raceway surface 7 consisting of a pair of orthogonal two planes located in the middle of both side surfaces of the square shaft 9 are also shown in the embodiment shown in the attached FIG. 22. are also located at the corners of both side surfaces and the top surface of the guide square shaft 9, and have a pair of inclined V-groove rolling surfaces 6a consisting of two surfaces parallel to and orthogonal to the mounting surface of the shaft 9. , and a pair of V-groove raceway surfaces 6 formed of two orthogonal planes located midway between both side surfaces of the guide square shaft 9 to form the two pairs of raceway surfaces, and each of these implementations As shown in the example, guide rollers are formed on both sides and inside the upper surface of each bearing body 10 formed in the shape of a pedestal, corresponding to the rolling surfaces of the two pairs of rollers formed on both sides of each of the square guide shafts 9. Axle 9
A bearing surface is formed with a constant clearance between both side surfaces and the upper surface of the bearing surface, and a corner of the bearing surface and the inner upper surface of the bearing is formed symmetrically on each of the two pairs of rolling surfaces of the guide shaft 9. did,
At both ends of the bearing axial direction of the axial rolling path formed between the V-groove raceway surfaces, a semicircular arc shape and a linear circulation path connected to the other end of the semicircular arc shape form an axially elliptical shape. In each circulation path to be formed, a cage of the present roller is applied to a large number of rollers whose axial length is slightly shorter than the outer diameter, and a large number of rollers are arranged with the cage. Attachment 1
In the embodiments shown in FIGS. 6 and 18, in all of the rectangular rolling paths of the two pairs of rollers on both sides of the guide shaft 9, as shown in FIGS. 11 (A) and (C), When the axes are arranged so that they alternately intersect, please refer to attached No. 2.
As shown in FIGS. 5(B) and (F), the bearing load capacity of the linear motion guide of the present application is similar to that formed on both sides of the guide shaft 9 in the embodiment described in claim 4) of the present application. Load capacity is equal in the vertical and horizontal directions of the bearing, as shown in (A) in the attached Figure 25, when the axes of the rollers are alternately arranged in a rectangular circulation path. In comparison with (B) in the figure corresponding to the above attached Figure 16
), the bearing load capacity that is equal to the top, bottom, left and right sides of the bearing is twice that of case (A) above in the figure, and also (F) in the figure.
The equal load capacity of the bearing in the vertical and horizontal directions is approximately 2.5 times the equal load capacity in (A) in the figure. Next, attached Figures 16, 18, 21, and 22.
In the illustrated embodiment, one of the square rolling paths in the axial direction between the bearing-side rolling surfaces formed symmetrically on the rolling surfaces of the two pairs of rollers on both sides of the guide shaft 9. The rollers are arranged so that their axes intersect with each other alternately as shown in the attached Figures 11 (A) and (C), and the other pair of rollers in the path are arranged as shown in the attached Figure 11 (A) and (C) above. As shown in (B) and (D) in Figure 11, when the axes of the mutually spaced rollers are arranged in parallel, the load capacity between the guide shaft and the bearing is as shown in the above attachment for each of the attached examples. As shown in FIGS. 25(C), (G), (D), and (H), FIGS.
), respectively in (B) and (F) in the above figure,
The equal load capacity in vertical and horizontal directions is as shown in figure (C).
In Figure (B), the load capacity for loads acting from below decreases, while the load capacity for loads acting from above increases; The load capacity in the left and right direction decreases,
The configuration is such that the load capacity for loads acting from above to below increases, and also in the figures (D) and (H) corresponding to the embodiments FIGS. 21 and 22, the above (C) and (D)
Similarly, the load capacity for loads acting from below or from the left and right direction decreases, and the load capacity for loads acting from above increases; The increase in the bearing load capacity against the load acting from above the bearing in Figures (C) and (G) in the attached Figure 25, which is shown by changing the arrangement method of the rollers in the circulation path, is due to the increase in the bearing load capacity against the load acting from above the bearing. When the arrangement method of the two pairs of upper and lower rolling path inner rollers is changed between the upper and lower paths, the bearing load capacity corresponding to the bearing load acting from above and below is also changed, and the bearing load capacity corresponding to the bearing load acting from above and below is also changed. A corresponding increase in load capacity can be achieved, and in addition to the arrangement method of the rollers in the circulation path of each of the above embodiments, in the alternating cross arrangement between the rollers in the path, a one-body one-one cross arrangement and a two-to-one arrangement are possible. , change to a cross arrangement such as 3 to 1, or adopt a cross arrangement method such as 1 to 1, 1 to 2, 1 to 3, etc. in parallel arrangement between rollers to diversify the bearing load capacity. be able to. Therefore, in a linear motion rolling guide constructed by applying the roller cage according to claim 1 to a large number of rollers in the bearing, the rolling surfaces of two pairs of V-groove rollers formed on both sides of the guide shaft. 2 formed symmetrically on the pedestal-like bearing corresponding to the rolling surface.
In a conventional product of this kind constructed using the above-mentioned rollers, the rolling paths of the two pairs of square rollers of the load bearing area rollers formed between the pair of V-groove raceway surfaces are formed on both sides of the guide square shaft. In comparison with a linear motion rolling guide in which a rolling path for the pair of rollers is formed on the surface, the load capacity of the bearing for the linear motion guide configuration is increased, and the bearings for the guide shown in the attached examples are improved. Due to the differences in the formation and arrangement of the rolling paths of the two pairs of square rollers between the square shaft and the bearing, and the selection of the arrangement method of the cage inner rollers in the paths, the direction of the main load acting on the bearings is determined. The bearing is characterized in that the ratio between the vertical and horizontal load capacities of the bearing can be optimized in accordance with the magnitude of the load value and the preload value set corresponding to the main load value. A circulating linear motion rolling guide configuration. 6) Cage 4 for rolling guide balls according to claim 2)
In the linear motion rolling guide shown in the attached FIGS. 23 and 24, which is constructed by applying the above to a large number of balls in a bearing, a constant play is maintained between both sides of the rectangular guiding shaft 9 and between the two sides. , when the ball cages are arranged on each of the bearing surfaces formed on the inside of both side surfaces of the pedestal-shaped bearing body 10, together with the rolling surfaces in the load supporting range of the balls, on the rolling surfaces. an axially rectangular load area running path formed between inclined V grooves 6c and 7c formed symmetrically with a slight clearance between the running guide surfaces 4b of the retainer on the outer peripheral surface; Arranged together with the retainer 4 in a circulation path formed in an axially oval shape with a semicircular arc extending to both ends of the running path in the axial direction of the bearing, and a linear path extending to the other end of the semicircular arc. A large number of balls 20
During the operation of the linear rolling guide, direct contact between adjacent spheres is avoided via the retainer 4 in the circulation path between the guide shaft and the bearing, and on the spherical outer peripheral surface 4a of the retainer 4, Due to the mutual contact of the cages in the path and the traveling guide surface 4b on the outer circumferential surface of the cage, the movement between the guide shaft and the bearing in the path within the cage continues smooth circular rolling in the path. Damage to the balls and raceway due to the unavoidable repeated elastic collisions between the raceway in the load bearing area and the circulation path in the bearing, between the raceway and the circulation path wall, and between the balls. Direct-acting rolling guide characterized by avoiding wave noise. 7) In a linear rolling guide configured by applying the roller retainer according to claim 1 to a large number of rollers in a circulation path within the bearing, a V-groove shape formed on the guide shaft and consisting of two orthogonal planes. The bearing surface, which corresponds to the rolling surface of the rollers and is formed with a certain amount of play, corresponds to the V-groove raceway formed on the guide shaft and is formed symmetrically with respect to the rolling surface. The rolling path of the square rollers in the axial direction, which is also formed on the V-groove raceway surface, is connected to both ends in the axial direction of the bearing, and has a semicircular arc shape, and the linear circulation path that is connected to the other end of the semicircular arc shape. As shown in the perspective view of FIG. 19 and the projected view of FIG. For the arc-shaped path, V-shaped guide grooves 17a and 18a were formed in each of the semicircular arc-shaped path component parts 17 and 18 shown in the attached figures above, and the parts 17 and 18 were overlapped. For a straight path that forms an arcuate path and continues to the other end of the arcuate path, the arcuate V-shaped grooves 17a and 1 formed in the arcuate path forming parts 17 and 18 are used.
V-shaped joint surface 17b, which is connected to V-shaped grooves 17 and 18 and is formed with a certain level difference and parallelism between the two intersecting planes forming the V-shaped grooves 17a and 18a. Corresponding to the rectangular joint formed by Joint surface 17 formed on parts 17 and 18
A cylindrical part 19 which maintains a constant thickness between the rectangular circulation path 19a and molds a parallel joint surface 19b, which fits into the joint formed by the rectangular inner peripheral surface in the axial direction formed by b and 18b. This forms a circulation path with the cage applied to the inner rollers of the bearing, and also forms a circulation path with the cage applied to the inner roller of the bearing.
At the corners, corresponding to the shape of the outer circumferential surface of the cage applied to the rollers in the path, in cage 1 and cage 2 shown in attached FIGS. 1(A) and (B), there is a projection 1e for reinforcing the cage. A rectangular groove-shaped flank is formed with a slight play between The axial cylindrical hole 10d of the bearing main body 10 shown in the attached FIG.
In the concave portion 15g of No. 5, the cylindrical component 19 for forming a linear path range in the axial direction and the semicircular arc path range forming component formed by overlapping parts 17 and 18 are placed in place. However, when forming the circulation path of the rolling element retainer in which the retainer is applied to the rolling elements of the present application, the above attachment No. 19 shall be applied.
An axial round hole 10d formed in the bearing body 10 in the figure,
The concave portion 15g formed in the side plate 15 can be formed and applied in accordance with the type and size of the linear motion guide, and the path component parts 17 to 19 include the rolling elements in the circulation path and the rolling elements. The bearing body 10 for the linear motion rolling guide configuration of the present invention and the bearing side plate 15 that have the same cage dimensions and shape applied to the
In this case, the round hole in the axial direction and the recess 15g in the side plate 15 can be formed and used, and for the purpose of making the linear motion guide of the present application more compact, the width of the bearing can be reduced;
In order to avoid difficulty in running the cage in the path due to a decrease in the cage turning radius at the semicircular curved portion in the circulation path in the bearing due to the reduction in bearing width, the attached Figs.
When increasing the turning radius of the in-path holder by the three-dimensional forming method of the axially oval path shown in the figure, the cylindrical component 19 for configuring the circulation path is attached to the attached No. 18. As shown in the embodiments of FIGS. 19 to 19, the components are arranged at both sides and the corners of the upper and lower surfaces of the pedestal bearing main body 10, and when the cylindrical path component 19 is placed inside the pedestal bearing, 19, and the guide shaft and the inter-bearing load area rolling path are connected at an angle to the upper and lower surfaces of the bearing body 10 by path components 17 and 18, and are formed between the path components. A method for forming a cage circulation path in a bearing in a linear motion rolling guide according to the present application, which is characterized by increasing the cage turning radius in a semicircular arc path range in the circulation path. 8) The rolling element cage according to claim 1) or 2) is made of nylon-based material having various properties necessary for a cage material for rolling bearings, such as formability, strength, wear resistance, and corrosion resistance. Application to the above-mentioned rolling elements for linear motion rolling guide configurations, characterized in that they are molded by injection molding from polymeric materials such as polyacetal, as well as various fiber-reinforced materials, solid lubricant-added composite materials, etc. A cage intended for.