JPS59219520A - Linear slide bearing - Google Patents

Abstract

PURPOSE:To make the sence of a bearing race followable according to a curve in vertical and horizontal directions on a raceway track block, by holding the bearing race having a barrel type outward appearance rockably inside a race housing groove of a bearing body. CONSTITUTION:A groove-shaped sectional bearing body 1 having an almost oval- form hollow concave 3 and each of skirt parts 4 and 5 at both sides of it is installed in position beneath a ceiling part, and each of semicircular race housing grooves 6 and 7 open to the side of the hollow concave 3 is symmetrically formed in inner surfaces of these skirt parts 4 and 5. A symmetrical pair of bearing races 12 and 13 are attached to these housing grooves 5 and 7, while each of semicircular load ball grooves 14 and 15 forming a circulating passage together with ball passages 10 and 11 formed inside the body 1 are installed inner surfaces of these races 12 and 13. Each of bearing races 12 and 13 is formed into barrel type outward form and seated on symmetrical inclines 17 and 18 having load ball grooves 19 and 20 of a raceway track block 16 via load balls B1.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides a five-line sliding bearing that is effective for use in table saddles of machine tools, sliding surfaces of machining centers, or sliding surfaces of transport robots that support heavy objects and move back and forth. , especially those with self-centering function.

In a conventional linear sliding bearing, for example, as shown in FIG.
], 1, 112, respectively, by inserting bearing races 113, 114 having a rectangular cross section, which also extend in the longitudinal direction, and tightening each bearing race 113, 114 with a screw Il-, female, each bearing race 113, 1.
The load ball grooves 116, 117 of 14 and the load ball grooves 119, 120 of the track 118 form a load target passage, and the load pole passages 116, 117
, 119, 1.20 and the no-load bearing passage are interconnected and the passage is circulated in alignment, thereby causing the bearing body 110 to slide. When constructing a transportation robot using linear sliding bearings, for example, it is common to install and extend a plurality of tracks 118 coaxially in the longitudinal direction in order to expand the range of transportation work. However, orbital platform 1
18, each track base 118.18 may be interconnected due to installation errors or other causes. ...
The central axes of
18. A song that curves sideways or floats upwards may cause a curve. In such a case, according to the conventional configuration, the upper surfaces 113a, 114a and the back surfaces 113b, 114b of the bearing races 113, 114 are closely fixed to the wall surfaces of the concave grooves 11.1° 112 of the bearing body 110, respectively. Bearing body 11
0 passes through the curved part of the track 118I..., the contact pressure of the beer locally increases, and the load is reduced to the -ru groove 116,
117, 119, 120, or the sliding resistance of the bearing body increases when the track 118°... passes through the 9th section, causing the bearing body 11
This has resulted in inconveniences such as not being able to guarantee smooth linear sliding motion at zero.

Therefore, the present invention was made to solve the drawbacks of the prior art, and by holding the bearing race, which has a barrel-shaped appearance, in a race storage groove of the bearing body so that it can all swing relative to each other, the upper and lower parts of the track base, To provide a linear sliding bearing having a self-aligning function of the bearing race by making the direction of the bearing race follow the bending in the left and right direction.

The present invention having the above-mentioned object will be explained based on the illustrated embodiment. Reference numeral 1 indicates the entire bearing body, and the bearing body 1 is made of a block body with a groove-shaped cross section.
A substantially rectangular hollow recess 3 is provided below the ceiling portion 2, and at the same time, skirt portions 4 and 5 are provided on the left and right sides of the hollow recess 3.

Reference numeral 6.7 denotes a semicircular lace storage groove that is symmetrically provided on the inner surface of each skirt portion 4, 5 and opens toward the hollow recess 3 side, and the arcuate groove bottom of the lace storage groove 6, 7 is At one end, that is, at the lower end of the arc that is far from the ceiling part 2, there are strut horns (4) that protrude across the openings of the lace storage grooves 6 and 7.
)-8 and 9 are provided. Note that 0. is the center of curvature of the race storage grooves 6 and 70, and the center axis X of the bearing body 1,
The line Y, which forms an angle of about 55 degrees with -XI, is set above -Y.

10.11 is bored in the center of the skirt part 4.5,
This is a circular unloaded pawl passage having approximately the same curvature as the pawl and a diameter larger than the pawl diameter, and is provided in the axial direction over the entire length of the bearing body 1. As shown in FIGS. 3 and 6, the above-mentioned no-load pole passage 1
0.11 is the center axis of the pairing body 1)G
It is located on the intersecting line Y, -Y, which makes an angle of about 55 degrees with respect to Note that reference numeral 2a in the drawings is a screw hole drilled in the ceiling portion 2 of the bearing body 1 at a predetermined interval in the center in the longitudinal direction.

The bearing main body 1 having the above structure is made of a lightweight material such as synthetic resin, and by having such a lightweight structure, the inertia force can be reduced, so that the bearing body 1 does not have to be repeatedly started and stopped at high speed. Ideal for linear sliding bearings with high resistance.

12. The above race storage groove 6 of the 13fi bearing body 1
, 7, and are a pair of left and right bearing races shaped like semi-circular arcs.As clearly shown in FIGS. Bearing body no-load pole passage 10.11
A semicircular load goal groove 14 , which extends in the axial direction and corresponds to the axial direction.
15 is formed, and its center of curvature 02 coincides with the center of curvature O8 of the lace storage groove. This load pole groove 14.15 is aligned with the central axis X1-X of the bearing body 1.
, an angle of about 5 to the central axis X, , −X2, which coincides with ,
The center of curvature o2 is set on the intersection line Y2-y2 that forms a 5 degree angle. As a result of the contact angle β between the grooves 14 and 15 and the load pole B1 being set to 45 degrees, when the load is applied, the load day? - Since the contact area due to elastic deformation that occurs between the surface of the pole B1 and the groove surface of the load pole groove 14.15 increases, the load that each part on the contact surface bears is reduced, and the load capacity increases. become.

The load goal groove 14.15 described above is approximately i of the ball diameter.
The load sole groove 14°15 is formed by a circular arc groove with a radius of curvature of
By forming by arc groove! Even when reloading (pre-compression) is applied or loads are applied in each direction, each load pole B makes contact at two points in the contact direction, so there is no differential movement and the rollers are in good condition.
exercise. Furthermore, even when the heavy weight type is loaded, the pole is elastically deformed because the circular arc groove is in two-point contact, resulting in a wide contact width and increased rigidity. Two more rows of circulars
The ideal arrangement and two-point contact structure give the arc groove an appropriate contact angle, and there is a place for the elastic deformation of the goal to escape, so even if there is some misalignment of the mounting surface, it will be absorbed inside the bearing and will not be unreasonable. You can get smooth movement.

Further, the outer circumferential surfaces of the bearing races 12, 13 have a barrel-shaped external shape, as shown in FIGS. There is a longitudinal gap θ1. θ, and the lateral gap θ2. Since θ2 is formed, the bearing body 1 (7) 1/-th storage groove 6
, 7, the bearing races 12 and 13 perform relative rocking movements vertically and horizontally using their central portions as a fulcrum.

Therefore, even if the track 16 (to be described later) is bent, the bearing races 12 and 13 will move in the direction of the bend of the track 16 depending on the degree of 9 degrees when the song passes through the 9th section. By changing direction and following the track, and then, when reaching the normal straight line part of the track 16, changing direction again and returning to the normal direction, the central axis X2 X2 is aligned with the central axis Xs Xs of the track 16. It is something that makes you In this way, the alignment action of the linear sliding bearing according to the present invention is performed.

Reference numeral 16 denotes a track that is inserted into the inner wall recess 3 of the bearing body, and is attached to a movable part or a fixed part of a machine tool or the like using fixing means such as bolts.

As shown in FIG. 3, FIG. 12, and FIG. The load ball groove 19.20 has a semicircular load ball groove 19.20 extending from the center of curvature of 0.20 to the load ball groove 19.20. is the central axis line Xs that coincides with the central axis line X, -X of the bearing body 1. The intersecting line Y3 Y makes an angle of about 55 degrees with XA.
R, and the center of curvature of the race storage groove 6°7 and the load ball grooves 14 and 15 of the bearing race is 0. ,02. Therefore, these two loads are connected to the groove 14.15.
and 19.20 form two loaded sol passages. The load ball grooves 19, 20 of the track are similar to the load pole grooves 14, 15 of the bearing races 12, 13. It is constituted by a circular arc groove having a radius of curvature approximately equal to the radius of the arc. Furthermore, the said orbital platform 1
Similarly to the load goal grooves 1.4 and 15 of the bearing race 12.13, the load pole grooves 1.9 and 20 of No. 6 have a contact angle β' between the load pole B and the load goal groove 19.20. is set at 45 degrees, thereby increasing the load capacity.

Reference numeral B designates a pole that is interposed between the bearing races 12, 13 and the track 16 and moves in circulation, so that the loads of the bearing races 12, 13 and the track 1-6 are transferred to the rail path 1.
4, 15 and 19.20, the load pole B7 receives the load by rolling, and the unloaded bearing body 1 passes through the passage 10.
．． No load rolling inside 11? - Contains B2. Note that the difference between the loaded pole B1 and the unloaded pole B2 merely indicates whether the same pole is rolling in the loaded area or in the swallow load area.

Reference numerals 21 and 22 denote side covers that are attached to the front and rear end surfaces of the bearing body 1 by fixing means such as bolts, and are manufactured by injection molding or die casting using synthetic resin material or die casting alloy. The structure of the side lids 21 and 22 will be explained for one of the side lids 21 with reference to FIGS. 14 to 18. The entire rectangular hollow recess 23 is provided, and by providing skirt portions 24 and 25 on the left and right sides of the inner wall recess 23, the bearing body 1 has a shape similar to the inner peripheral shape of the bearing body 1. Furthermore, the side lid 21 has pole direction conversion grooves 26a and 26b formed in the inner cylinder of the lid body in a curved manner toward the outer surface of the lid body. 26b, as shown in FIG.
Y, and extends along the intersection line Y for a predetermined length. Each pole direction changing groove 26a.

The starting ends of 26b correspond to the groove ends of the bearing races 12, 13 and the loaded pole passages 14, 15, 19° 20 of the track base 16, and the terminal ends of the ends correspond to the groove ends of the unloaded goal passages 10, 11 of the bearing body 1. It corresponds to

In short, each of the sol direction conversion grooves 26a, 26b has its starting end communicated with the loaded pole passage 14, 15°19.20, and at the same time, its terminal end is communicated with the unloaded
10.11. Therefore, by means of the side cover 21 provided with this goal direction conversion groove, loads in a mutually corresponding relationship can be applied to the passages 14, 15, 19.2.
0 and the front side of the unloaded pole passage 10.11 are connected.

One side of the loaded pole passages 14, 15, 19.20 and the other side of the no-load pole passage 10.11 are connected to the one side cover 2 described above.
If they are connected by another side cover 22 having the same configuration as 1, for example, any loaded goal passage 14, 19 and any unloaded pole passage 10 will form a pole circulation passage (the 3rd (see figure).

27 and 28 are semi-circular race holding grooves provided on the inner surface of the side cover 21, and are aligned with the center axis X4-X4 of the side cover 22.
The center part is placed above the intersection line Y4-Y, which forms an angle of about 55 degrees with respect to Y4-Y. It has a larger radial distance than the race ends to allow rocking.

Reference numeral 29 denotes a race suppressor that is adjustably screwed onto the ceiling portion 2 of the bearing main body 1 via a fixing device such as a bolt 30, and this race suppressor 29 is formed of a plate-shaped body with a trapezoidal cross section. Consisting of a wedge body, each screw hole 2 in the ceiling part 2
It is supported by a bolt 30 screwed into 8. Then, the wedge surfaces 29a and 29b of the lace suppressor 29,
Bearing body 10 Upper inner surface 12a in the longitudinal direction of bearing races 12 and 13 installed in race storage grooves 6 and 7
.

13a, and when the race suppressor 29 in this state is pulled upward by screw operation, the race suppressor 29 wedges the longitudinally upper inner surfaces 12a of the bearing races 12, 13 facing each other, 13
It bites into the gap formed between a. the result,
Since the bearing races 12 and 13 have their longitudinally upper inner surfaces 12a and 13a pressed in the rotational direction by the race suppressor 29, one bearing race 12 is pressed counterclockwise in FIG. 13 is a longitudinally lower inner surface 12b on the opposite side that is pressed and rotated clockwise.

13b comes into contact with the stoppers 8 and 10. In this case, since the center of curvature O0 of the race storage grooves 6 and 7 and the center of curvature 02 of the load pole grooves 14 and 15 provided in the bearing races 12 and 13 completely match, the bearing race due to the race suppressor 29 Even if there is an error in the installation operation of bearing races 12 and 13, the load placed on the bearing races 12 and 13 will not cause the centers of curvature 02 of the grooves 14 and 15 to become misaligned. As described above, in the present invention, the left and right bearing races 12 and 13 can be integrally fixed by simply operating the single race pressing member 29.

To explain the function of the present invention based on the configuration on the side,
For example, when the Km sliding bearing unit of the present invention is assembled into the track base 16 of a machining center (not shown) and the required machinery and equipment are set on the bearing body 1, when the pairing unit is moved forward and backward, the bearing race 12 , 13 and the load poles 14, 15 of the track 16
, 19° 20. Load day when the load formed by -19°20 is in a state of being clamped in the loop passage? -Role B travels rearward while being guided by the load pole passage. Eventually, the load increases to the ball direction changing groove 26a of the side cover 22.

26b, the direction is changed from the linear direction to the rotational direction and fed into the no-load pole passage 10°11 of the bearing main body 1, becoming the no-load sole B2. Thereafter, the unloaded ball B2 traveling in the unloaded ball passages 10 and 1.1 is changed direction from the linear direction to the rotational direction by the pole direction conversion grooves 26a and 26b of the lid 21 on the opposite side. It returns again to the bearing races 12, 13 and the load pole passages 14, 15, 19, 20 of the track base 16, becoming the load pole B. Thereafter, the alignment circulation is repeated with the same operation.

Here, even when the track base 16 is bent in the left-right direction or the up-down direction, the pair of left and right bearing races 12 that are integrated by the race pressing body 29
, 13 are the gaps θ2. θ, and θ7.02, the curve of the track platform 16 changes direction in the upward direction and follows this. After passing through the vertical and horizontal curves of the track 16, the direction is changed again along the normal straight line of the track 16, and the center axis of the bearing race is adjusted to the normal direction. X2 X2 k Central axis line of track 16, -X3
This completes the centering action. Regarding the direction change of the bearing races 12 and 13 when the track 160 passes through the 9th part, if the track 9 of the track 16 is in the vertical direction, the race fixed to the bearing body 1 This is achieved by swinging the left and right pair of bearing races 12 and 13 relative to the suppressor 29, using the center portion as a fulcrum. On the other hand, when the track base 16 is bent in the left-right direction, the connection part to the bearing body 1, that is, the position of the screw hole 2 part is used as a fulcrum, and the race pressing body 29 and the integrated left and right pair 16- The direction change is performed by the bearing races 12 and 13 collectively swinging left and right.

In the linear sliding bearing of the present invention having the structure and operation as in JLJ, the bearing race having a barrel-shaped outside is held in the race storage groove of the bearing body so as to be relatively swingable. The direction of the bearing race can be made to follow the vertical and horizontal bends of the track 1f. Therefore, the local increase in contact pressure of the ball when the track passes through the 9th section can be completely prevented, and the sliding resistance of the bearing body is also reduced, thereby increasing the safety of the load pole passage. This has the effect of ensuring smooth sliding of the bearing body. Since the bearing race is formed by a semi-circular arc body with high threading resistance, there is no threading in the bearing race even when a load is applied, and as a result, the threads are transferred along the bearing race. Since the contact pressure of the balls can be kept completely uniform, smooth alignment and circulation of the balls is possible.

Furthermore, by simply adjusting a single race suppressor, the pair of left and right bearing races that are locked to the mounting surface of the side cover can be fixed at the same time, which greatly simplifies the installation process and allows for the production of the entire bearing unit. Cost can be reduced.

On the other hand, even if an error occurs when tightening with the race suppressor, the load on the race housing groove and the bearing race provided in the race housing groove can be adjusted so that the centers of curvature of the race housing groove and the bearing race coincide with each other. The center of curvature of the load pole groove will not be distorted, and therefore, even if an installation error occurs, the tube will not have uneven contact pressure, and has various effects.

[Brief explanation of drawings]

Figures 1 to 20 show examples of the linear sliding bearing according to the present invention. Figure 1 is a front view of the linear sliding bearing, Figure 2 is a plan view of the same, and Figure 3 is one of the bearings. A front view of the linear sliding bearing with the side cover removed, Figure 4 is Figure 1 IV
- mV line sectional side view, Fig. 5 is a cross-sectional plan view of Fig. 3 - v line, Fig. 6 is a front view of the bearing body, Fig. 7 is the same plan view, Fig. 8 is the same bottom view, Figure 9 is a side view of the same bearing race, Figure 0 is a front view of the bearing race, Figure 11 is one side view of the bearing race (1111
A side view of the bearing race, FIG. 12 is a front view of the center longitudinal section of the track, FIG. 13 is a side view of the same, FIG. 6g14 is a front view showing the outer surface of the side cover, FIG.
The figure is a bottom view of the same, Fig. 17 is a vertical cross-sectional side view taken along the line X-X in Fig. 15, Fig. 18 is an oblique cross-sectional end view taken along the line X-X in Fig. 15, and Fig. 19 is a central longitudinal cross-sectional front view of the lace press body. FIG. 20 is a plan view of the same, and FIG. 21 is a front view showing a conventional linear sliding bearing. Explanation of symbols 1... Bearing body 2... Ceiling part 2a... Screw holes 3, 23...
Hollow recesses 4, 5, 24, 25...Skirt portion
6, 7...Lace storage groove 8.9...Stopper
10.11...One passage with no load 12.1
3...bearing race], B2a, 1.
3 a... Upper side surface 12b, 13b... Lower side surface 14.15, 19.20... Load pole groove (load pole passage) 16... Track base 21.
22... Side cover 26a, 26b... Pole direction conversion groove 27. 28... Race holding groove 29... Race pressing body 29a, 29b... Wedge surface 3
o...is root B,...load hole
B2... No load M-le 0,,02.0. ...Center of curvature Xa, X2, Xs, Xa...
Central axis Y, Y2. Y4...Cross line
β, β'...Contact angle θ,...Gap (vertical direction) θ2...Gap (horizontal direction) Patent applicant
Hiroshi Teramachi

Claims (4)

[Claims] (1) A block body with a groove-shaped cross section in which skirt portions are provided on the left and right sides sandwiching a central recess, and a semicircular lace storage groove that opens to the central recess extension is provided on the inner surface of the skirt portion, and the lace storage groove is provided on the inner surface of the skirt portion. The bearing body has a stopper protruding from the lower arcuate end of the groove, and a no-load passage is bored in each of the skirt parts, and the bearing body is installed in the race storage groove of the bearing body so as to be able to swing relative to each other. a pair of left and right bearing races, each of which is a semicircular arc body having a barrel-shaped outer peripheral surface, and a load ball groove having a center of curvature that coincides with the center of curvature of the race storage groove is formed at the center of the inner surface of the semicircular arc body; A wedge body adjustably screwed onto the inner surface of the ceiling of the bearing body is brought into simultaneous contact with one inner surface of each of the bearing races, thereby causing each of the bearing races to a race suppressor that presses against the stopper (1111); and a load goal groove that is fitted into the central recess of the bearing body and has a center of curvature that coincides with the center of curvature of the load ball groove of each bearing race, and is provided on all left and right side surfaces of the load goal groove. and a lid body fixed to the front and rear ends of the bearing body, which includes a load ball passage formed by a groove that aligns the load of the bearing race and the wayway, and a no-load ball passage of the bearing body. A pair of front and rear individual lids each having a ball direction conversion groove and a race holding groove that supports both ends of the bearing race on the inner surface of the lid body, and a load ball passage and a bearing race that communicate with each other. A linear sliding bearing characterized in that the load consists of balls circulating in a loop passage. (2) The earring body is made of lightweight synthetic resin-1)
- Linear sliding bearing according to claim 1, characterized in that: - a force is applied. (3) The contact angle between the load pole passage and the pole is approximately 45
2. The linear sliding bearing according to claim 1, wherein the linear sliding bearing is approximately 100°. (4) The linear sliding bearing as set forth in claim 1 or 3, wherein the load pole groove forming the load pole passage is constituted by a circular arc groove.