JP5988555B2 - Finite rolling motion guide device - Google Patents

Description

  The present invention relates to a finite rolling motion guide device having a finite stroke, such as a finite linear motion guide device, a finite rolling spline, and a slide rail.

  As a conventional finite rolling motion guide device of this type, for example, a finite linear motion guide device as described in Patent Document 1 is known. As shown in FIG. 6 (A), this finite linear motion guide device has a track rail 103, a moving block 105 that can move relative to the track rail 103, and a facing surface between the track rail 103 and the moving block 105. A plurality of rolling elements 107 interposed between the rolling surfaces 104 and 106 provided so as to be freely rollable and a cage 109 as a rolling element holding member for holding the rolling elements 107 are provided. . There is no circulation structure of the rolling elements 107, and the operation stroke of the moving block 105 is limited to the movable range of the cage 109. In the illustrated example, the length of the cage 109 is made longer than the length of the moving block 105 so that the operation stroke of the moving block 105 is made as long as possible.

6 (B) and 6 (C), the moving block 105 has moved by a predetermined amount in the left direction in the figure from the position of FIG. 6 (B) to the position of FIG. 6 (C) with respect to the track rail 103. The state is shown schematically.
When the moving block 105 moves, the rolling element 107 rolls in the moving direction of the moving block 105 with respect to the track rail 103, and rolls in the direction opposite to the moving direction of the moving block 105 with respect to the moving block 105. Therefore, the cage 109 moves following the moving block 105 while moving backward relative to the moving block 105.
Here, the movement amount of the cage 109 relative to the track rail 103 is defined as the cage movement amount Sa, the displacement amount of the cage 109 relative to the movement block 105 is defined as the cage displacement amount Sb, and the movement amount of the movement block 105 relative to the track rail 103 is defined as the operation stroke So. The cage displacement amount Sb is the distance that the moving block 105 has moved forward relative to the cage 109, and the operation stroke So is the sum of the cage displacement amount Sa and the cage displacement amount Sb.

FIG. 6D is a schematic diagram showing the relationship between the track rail 103, the moving block 105, and the rolling element 107.
That is, the contact diameter D of the rolling element 107 with respect to the rolling surface 104 of the track rail 103 and the contact diameter D of the rolling element 107 with respect to the rolling surface 106 of the moving block 105 are the same. The distance traveled L is the same as the distance traveled by the rolling element 107 relative to the moving block 105, that is, the distance L traveled by the moving block 105 relative to the rolling element 107. The contact diameter D is a diameter of a cross section orthogonal to the rotation center axis at the contact portions Cp and Cq with the rolling surfaces 104 and 106 of the rolling element 107.
6 (B) and 6 (C), the cage 109 moves together with the rolling elements 107, so the cage movement amount Sa and the cage displacement amount Sb are the same, and the cage 109 has a ratio of 1/2 of the operating stroke So. It moves following the moving block 105 while shifting backward.

JP 2009-85303 A

However, when the cage displacement amount Sb increases, the cage 109 and the moving block 105 are increased.
Since the overlap amount A decreases and the number of rolling elements 107 that load the load decreases and the load capacity cannot be secured, the cage displacement amount Sb naturally has a limit. In the conventional configuration, the operating stroke So of the moving block 105 is only twice the cage displacement amount Sb, so that the operating stroke So of the moving block 105 cannot be increased so much.

An object of the present invention is to provide a finite rolling motion guide that can take as large an operating stroke as possible of the moving member with respect to the raceway member by providing a difference in the contact diameter of the rolling elements with respect to the rolling surfaces on the raceway member side and the moving member side. To provide an apparatus.

To achieve the above object, the present invention includes a track member, the moving member relatively movable with respect to the track member, the track member and the moving member respectively between the rolling surfaces provided on the facing surfaces of the In a finite rolling motion guide device having a configuration including a plurality of rolling elements interposed so as to be freely rollable with respect to the rolling surface of the rolling elements, and a rolling element holding member that holds the rolling elements.
Movement of the rolling elements, the contact diameter of the contact portion for contacting a rolling run surface of the moving member, smaller than the contact diameter of the contact portion for contacting a rolling run surface of the track member, the moving member with respect to the track member When the amount is the operating stroke of the moving member , and the amount of displacement of the rolling element holding member with respect to the moving member is the holding member displacement amount, the ratio of the holding member displacement amount to the operating stroke is made smaller than 1/2.

According to the present invention, the operating stroke of the moving member the amount of movement of the moving member relative to the track member, when the holding member displacement amount a shift amount of the rolling element retaining member with respect to the moving member, the proportion of the holding member displacement amount with respect to the operating stroke is 1 Therefore, the rolling element holding member moves longer following the movement of the moving member than in the conventional case. If the holding member shift amount is the same, the moving member operates in comparison with the conventional case. The stroke can be made longer.

1A and 1B show the principle structure of a finite linear motion guide apparatus according to Embodiment 1 of the present invention, in which FIGS. 1A and 1B show an example of a ball contact structure, FIG. (D) is an operation explanatory view of a moving block and a cage. FIG. 2 shows a specific configuration example of the finite linear motion guide apparatus of FIG. It is. FIGS. 3A and 3B show the principle structure of a finite linear motion guide apparatus according to Embodiment 2 of the present invention. FIGS. 3A and 3B show an example of a contact structure of a step roller, and FIG. (D) is an operation explanatory view of a moving block and a cage. 4A and 4B show a specific configuration example of the finite linear motion guide device of FIG. 3, in which FIG. 4A is a partially broken perspective view, and FIG. FIG. FIGS. 5A to 5C are diagrams showing various forms of contact structures between various rolling elements and their rolling surfaces. FIG. 6A is a perspective view of a conventional finite linear motion guide device, FIG. 6B and FIG. 6C are operation explanatory views of a moving block and a cage, and FIG. 6D is an explanatory view of a rolling state of a rolling element.

The present invention will be described in detail below based on the embodiments shown in the drawings.
[Embodiment 1]
1 and 2 show a finite linear motion guide device as a finite rolling motion guide device according to Embodiment 1 of the present invention.
In FIG. 2, reference numeral 1 denotes an entire finite linear motion guide device, and a track rail 3 as a first member and a moving block 5 as a second member guided so as to be relatively movable along the track rail 3. And a number of balls 7 as rolling elements interposed between the ball rolling grooves 4 and 6 as rolling surfaces provided on the opposing surfaces of the track rail 3 and the moving block 5, and a ball 7 and a cage 9 as a rolling element holding member for holding 7.
The track rail 3 is a long member having a rectangular cross section, and a total of four ball rolling grooves 4 and 4 are formed in a straight line over the entire length on the left and right sides. In the illustrated example, the recess 31 is formed on the side surface of the track rail 3 over the entire length of the track rail 3, and the ball rolling grooves 4 and 4 are formed at the upper edge and the lower edge of the recess 31.

On the other hand, the moving block 5 is a block body including a block main body 52 facing the upper surface of the track rail 3 and a pair of legs 51, 51 facing the left and right side surfaces of the track rail 3. A total of four ball rolling grooves 6 and 6 are formed on the inner side surfaces of the leg portions 51 and 51 facing each other. In the illustrated example, on the inner side surface of each leg 51, a ridge 53 is formed corresponding to the recess 31 of the track rail 3, and the ball rolling grooves 6 and 6 are formed on the upper and lower sides of the ridge 53. The ball rolling grooves 4 and 4 are formed to face each other.
The ball 7 is interposed between the four ball rolling grooves 4 and 6 facing each other of the track rail 3 and the moving block 5 so as to freely roll, and the moving block 5 is arranged on the left and right side surfaces of the track rail 3. Each of the two rows is held movably through a total of four rows of balls.
In this example, with the lower surface of the track rail 3 placed horizontally, the rotation center axes M, M of the upper and lower balls 7, 7 are opened outward with respect to a horizontal line H passing through the middle of the upper and lower balls 7, 7. It is inclined at an angle of 45 ° in the direction, and has a structure with high rigidity against loads from all directions, up, down, left and right. Of course, the rotation center axes M and M may be inclined in the inward opening direction.

  The cage 9 is a long member interposed one by one between the left and right side surfaces of the track rail 3 and the opposing surfaces of the legs 51, 51 of the moving block 5, and the cage 9 is longer than the moving block 5. It has a long structure. In the illustrated example, the cage 9 has a U-shaped cross section, and the bent portion 91 fits into the concave portions 31 on the left and right side surfaces of the track rail 3, and the holding formed on the upper and lower holding pieces 92, 92 across the bent portion 91. The balls 7 and 7 in the upper and lower rows are held in the holes 9a and 9a.

In this embodiment, the ball rolling groove 4 on the track rail 3 side is a circular arc groove having a single arc, and the ball rolling groove 6 on the moving block 5 side is a Gothic arch groove in which two arcs are combined. Yes. The ball rolling grooves 4 and 6 will be described in detail below.
1A and 1B schematically show the contact state between the ball rolling grooves 4 and 6 and the ball 7. 1A is a cross-sectional view in the longitudinal direction of each ball rolling groove 4, 6, that is, a direction orthogonal to the rolling transition direction of the ball 7, and FIG. 1B is a BB line in FIG. It is sectional drawing cut | disconnected along. In each figure, the ball 7 is not cross-sectional.

The ball rolling groove 4 on the side of the track rail 3 has a single circular arc shape slightly larger than the diameter of the ball 7, and the contact portion C ₀ of the ball 7 is the deepest position of the ball rolling groove 4, This is a region centered on the intersection of the orthogonal line N passing through the center of the ball 7 and the ball rolling groove 4 perpendicular to the rotation center axis M during movement. Contact diameter d ₁ of the contact portion C ₀ is the diameter of the ball section when cut to the rotation center axis M direction perpendicular street ball 7 contacts portions C ₀ of the ball 7, in this case, the ball 7 Diameter.

The ball rolling groove 6 on the moving block 5 side is constituted by two arc-shaped ball rolling surfaces 61 and 62 arranged symmetrically with respect to a line N perpendicular to the rotation center axis M of the ball 7. The two ball rolling surfaces 61 and 62 have a radius of curvature slightly larger than the radius of curvature of the ball 7, and the ball 7 comes into contact with the respective ball rolling surfaces 61 and 62.
The contact portions C ₁₁ and C ₁₂ are located in the middle of the two ball rolling surfaces 61 and 62, and their contact diameters d ₂ are the same. The contact diameter d ₂ is a diameter of a ball cross section when passing through the contact portions C ₁₁ and C ₁₂ and cutting in a direction orthogonal to the rotation center axis M of the ball 7.

FIG. 1B shows the relationship between the movement amount of the ball 7 and the moving block 5 during one rotation of the ball 7. Here, the distance that the ball 7 travels with respect to the track rail 3 is the ball movement amount La, the distance that the movement block 5 travels with respect to the ball 7 is the ball shift amount Lb, and the distance that the movement block 5 travels with respect to the track rail 3 is the block movement. Let it be the quantity Lo. In the figure, the lengths of La, Lb, and Lo become longer when the length corresponding to one rotation of the ball 7 is accurately described, and are therefore reduced and shortened.
The ball movement amount La is a distance that the ball 7 rolls on the ball rolling groove 4 of the track rail 3 at the contact portion C ₀ , and the length of the circumference having the contact diameter d ₁ as a diameter, that is,
La = d ₁ π
It is.
The ball shift amount Lb is the distance that the ball 7 rolls on the ball rolling groove 6 of the moving block 5 at the contact portion C ₁₁ (C ₁₂ ), and the length of the circumference that makes the contact diameter d ₂ , That is, Lb = d ₂ π
It is.
The block movement amount Lo is the sum of the ball movement amount La and the ball shift amount Lb.
Lo = La + Lb = d ₁ π + d ₂ π
Indicated by
The contact diameter _{d 1} of the track rail 3 side is larger than the contact diameter _{d 2} of the movable block 5 side, the ball moving distance La is greater than one-half of the block moving amount Lo (La> Lo / 2) , ball deviation The amount Lb is smaller than half the block movement amount Lo (Lb <Lo / 2).

1 (C) and 1 (D), the moving block 5 moves relative to the track rail 3 from the position of FIG. 1 (C) to the position of FIG. 1 (D) by a predetermined amount in the left direction in the figure. This state is schematically shown.
Here, if the movement amount of the cage 9 relative to the track rail 3 is the cage movement amount Ua, the displacement amount of the cage 9 relative to the movement block 5 is the cage displacement amount Ub, and the movement amount of the movement block 5 relative to the track rail 3 is the operation stroke Uo. The cage displacement amount Ub is the distance that the moving block 5 has moved forward with respect to the cage 9, and the operation stroke Uo is the sum of the cage displacement amount Ua and the cage displacement amount Ub.
The cage movement amount Ua, the cage displacement amount Ub, and the operation stroke Uo are proportional to the ball movement amount La, the ball displacement amount Lb, and the block movement amount Lo in FIG. The ratio (Ub / Uo) of the cage displacement amount Ub to the operation stroke Ua of the block 5 is smaller than half. From the viewpoint of the followability of the cage 9 with respect to the moving block 5, this means that the cage 9 can follow the movement of the moving block 5 longer than in the past.

Assuming that the cage displacement amount Ub reaches the same position as the conventional example shown in FIG. 6C, conventionally, the operation stroke So of the moving block 105 was only twice the cage displacement amount Sb. As shown in FIG. 1D, in the present invention, the cage movement amount Ua becomes longer than the cage displacement amount Ub by the amount that the cage 9 follows the movement of the moving block 5 for a long time, and the operation stroke Uo is set to the cage displacement amount. The length can be longer than twice Ub.
As described above, according to the finite linear motion guide device of the present embodiment, the cage 9 moves longer following the movement of the moving block 5 than in the conventional case, and the operating stroke of the moving block 5 is reduced. Can be longer.

In particular, a simple configuration in which a normal ball 7 is used as a rolling element, the ball rolling groove 4 on the track rail 3 side is a circular arc groove, and the ball rolling groove 6 on the moving block 5 side is a combination of gothic arch grooves. Thus, the operation stroke of the moving block 5 can be lengthened.
Further, since the length of the cage 9 is longer than the length of the moving block 5, the operating stroke of the moving block 5 can be further increased in combination with the followability of the cage 9 to the moving block 5.

[Embodiment 2]
3 and 4 show a finite linear motion guide apparatus according to Embodiment 2 of the present invention.
The second embodiment uses a step roller 27 as a rolling element, and the basic configuration as a finite linear motion guide device is the same. In the following description, the difference will be described, the same components are denoted by the same reference numerals, and description thereof will be omitted except for parts necessary for the description of the difference.

In FIG. 4, in the finite linear motion guide device 201, as in the first embodiment, the step rollers 27 are provided in two rows on the left and right side surfaces of the track rail 3, and a total of four rows are provided on the left and right side surfaces of the track rail 3. Two roller rolling surfaces 204, 204 are provided on the upper and lower edges of the recessed portion 31 formed on the upper and lower side surfaces of the protruding portion 53 provided on the inner side surface of the leg portion 51 of the moving block 5. Roller rolling surfaces 206 and 206 facing the roller rolling surfaces 204 and 204 are provided, and a step roller 27 is rotatably interposed between the roller rolling surfaces 204 and 206.
Also in the second embodiment, with the lower surface of the track rail 3 placed horizontally, the rotation center axes M, M of the upper and lower step rollers 27, 27 are on a horizontal line H passing through the middle of the upper and lower step rollers 27, 27. On the other hand, it is inclined at an angle of 45 ° in the outward opening direction, and has a structure with high rigidity against loads from all directions, up, down, left and right.

3A and 3B schematically show a contact state between the roller rolling surfaces 204 and 206 and the step roller 27. FIG. 3A is a cross-sectional view in the longitudinal direction of the roller rolling surfaces 204 and 206, that is, a direction orthogonal to the rolling transition direction of the step roller 27, and FIG. 3B is a cross-sectional view taken along line BB in FIG. It is sectional drawing cut | disconnected along the line. In each figure, the step roller 27 is not cross-sectional.
The step roller 27 includes a cylindrical large-diameter portion 271 and a cylindrical small-diameter portion 272 having a smaller diameter than the large-diameter portion 271, and the small-diameter portion 272 has a step on the left and right side surfaces of the large-diameter portion 271. The rotation center axis M of the small diameter portion 272 and the large diameter portion 271 is on the same axis.
The large-diameter portion 271 is in rolling contact with the roller rolling surface 204 on the track rail 3 side, and is not in contact with the roller rolling surface 206 on the moving block 5 side. In this example, the roller rolling surface 206 on the moving block 5 side is provided with a concave groove 261 for allowing the large diameter portion 271 to escape.

The small diameter portion 272 contacts the roller rolling surface 206 on the moving block 5 side and is not in contact with the roller rolling surface 204 on the track rail 3 side.
The contact diameter d ₂ of the contact portions C ₁₁ and C ₁₂ of the roller rolling surface 206 on the moving block 5 side and the small diameter portion 272 is the contact portion C ₀ of the large diameter portion 271 with the roller rolling surface 204 on the track rail 203 side. smaller than the contact diameter _{d 1.}
Since the contact diameter d ₁ on the track rail 3 side is larger than the contact diameter d ₂ on the moving block 5 side, the roller moving amount La is larger than half of the block moving amount Lo (La> Lo / 2), and the roller shift The amount Lb is smaller than half the block movement amount Lo (Lb <Lo / 2). This relationship is the same as in the first embodiment.

3 (C) and 3 (D), the moving block 5 moves relative to the track rail 3 from the position of FIG. 3 (C) to the position of FIG. 3 (D) by a predetermined amount in the left direction in the figure. This state is schematically shown.
Similarly to the first embodiment, the cage movement amount Ua, the cage displacement amount Ub, and the operation stroke Uo are proportional to the roller movement amount La, the roller displacement amount Lb, and the block movement amount Lo in FIG. When 5 moves, the ratio (Ub / Uo) of the cage deviation amount Ub to the operating stroke Ua of the moving block 5 is smaller than half.
If the step roller 27 is used as in the second embodiment, not only the operation stroke of the moving block 5 can be lengthened, but also the line contact makes a high load capacity and the contact diameter is kept constant. So it works correctly.

[Other embodiments]
FIG. 5 shows another example of the rolling elements.
In FIG. 5A, the configuration of the rolling element is a step roller 37 having a configuration in which the center is recessed in a small diameter unlike the second embodiment.
The step roller 37 includes a central cylindrical small-diameter portion 372 and a large-diameter portion 371 that is larger in diameter than the small-diameter portions 372 provided on the left and right sides of the small-diameter portion 372. The rotation center axis M of the rolling surface of the part 371 is on the same axis.
In this configuration, the contact diameter _{d 2} of the contact portions _{C 10} of the movable block 5 side of the roller rolling surface 306 and the small-diameter portion 372, the contact portion _C 01 of the ball rolling grooves 304 of the track rail 3 side, C It can be made smaller than the contact diameter d _{1 of 02} .

FIG. 5B shows a roller on the track rail 3 side using a barrel-shaped roller 47 whose outer peripheral shape of the cross section including the rotation center axis M is an arc shape, in particular, a central portion swells from both ends as a rolling element. The rolling surface 404 has a planar shape, and the roller rolling surface 406 on the moving block 5 side has a Gothic arch groove shape in which two arcs are combined.
The roller rolling surface 406 on the moving block 5 side has a Gothic arch groove shape combining two circular arcs, and the roller rolling surface 404 on the track rail 3 side is a flat surface, whereby the roller rolling surface on the track rail 3 side. The position of the contact portion C _{0 in} contact with 404 and the position of the contact portions C ₁₁ and C ₁₂ in contact with the roller rolling surface 406 on the moving block 5 side are changed to contact the roller rolling surface 406 on the moving block 5 side. contact diameter _{d 2} of the contact portion _{C 11, C 12} to, in which is smaller than the contact diameter _{d 1} of the contact portion _{C 0} of the track rail 3 side of the roller rolling surface 404. The roller rolling surface 404 on the track rail 3 side may have a circular arc groove shape.

In contrast to the barrel roller 47, as shown in FIG. 3C, a drum roller 57 having a circular outer periphery in the cross-sectional shape passing through the rotation center axis M is used as a rolling element. You can also. Even in this case, the contact diameter d ₂ of the central contact portion C ₁₀ that contacts the roller rolling surface 506 on the moving block 5 side is changed to the contact portion C ₀₁ with the roller rolling surface 504 on the track rail 3 side, it can be made smaller than the contact diameter _{d 1} of C _02.
As described above, when a rolling element having a circular outer peripheral shape including the rotation center axis is used like the barrel roller 47 and the hourglass roller 57, the rigidity can be made higher than that of the ball. Further, as the barrel roller 47 and the drum roller 57, existing rollers can be used.
However, the form of the rolling element and the rolling element rolling surface is not limited to these examples. In short, various types of making the contact diameter on the moving block side of the rolling element smaller than the contact diameter on the track rail side are included. A form can be adopted.

In the finite linear motion guide apparatus according to each of the above embodiments, a pair of left and right ball rows and stepped roller rows are arranged so as to sandwich the left and right side surfaces of the track rail. The cross-sectional shape of the moving block, the number and form of the ball rolling grooves and roller rolling surfaces are arbitrary and can be changed as appropriate.
In the above description, the cage is longer than the moving block. However, the cage is shorter than the moving block, and the cage moves within the moving block length. The same applies to cases.
In each of the above embodiments, the case where the moving block moves with respect to the track rail has been described. However, the relationship between the track rail and the moving block is relative, and the track rail moves with the moving block fixed. However, the present invention can also be applied to the case where the cage moves following the track rail while shifting backward. In this case, the contact diameter on the track rail side may be made smaller than the contact diameter on the moving rail side.

Furthermore, in the above-described embodiment, the finite linear motion guide device has been described as an example of the finite rolling motion guide device. However, the present invention is not limited to the linear motion and can be applied to a curved motion guide device that moves in a curved line.
Further, the finite rolling motion guide device of the present invention is not particularly illustrated, but can be widely applied to various finite rolling motion guide devices such as a finite rolling spline and a slide rail.

1 finite linear motion guide device, 3 track rail (first member), 4 ball rolling groove (rolling surface), 5 moving block (second member), 6 ball rolling groove (rolling surface), 61 , 62 Ball rolling surface, 7 balls (rolling element), 9 cage (rolling element holding member), C ₀ contact part (track rail side), C ₁₁ , C ₁₂ contact part (moving block side), M rotation center axis , D ₁ contact diameter (track rail 3 side), d ₂ contact diameter (moving block 5 side), Ua cage movement amount, Ub
Cage deviation amount, Uo operation stroke, 27 step roller (rolling element), 204 roller rolling surface (track rail side), 206 roller rolling surface (moving block side), C ₀ contact portion (track rail side), C ₁₁ , C ₁₂ contact part (moving block side),
37 Step roller (rolling element), 304 Roller rolling surface (track rail side), 306 Roller rolling surface (moving block side), C ₀₁ , C ₀₂ contact portion (track rail side), C ₁₀ contact portion (moving block) Side), 47 barrel roller (rolling element), 404 roller rolling surface (track rail side), 406 roller rolling surface (moving block side), C ₀ contact portion (track rail side), C ₁₁ , C ₁₂ contact Part (moving block side), 57 drum-shaped roller (rolling element), 504 roller rolling surface (track rail side), 506 roller rolling surface (moving block side), C ₀₁ , C ₀₂ contact part (track rail side) , C ₁₀ contact part (moving block side)

Claims (5)

And the track member, rollably through relative to the the moving member relatively movable with respect to the track member, the track member and respective rolling run surface between the rolling surfaces provided on the facing surfaces of the moving member In a finite rolling motion guide device having a configuration including a plurality of rolling elements to be mounted and a rolling element holding member that holds the rolling elements,
Movement of the rolling elements, the contact diameter of the contact portion for contacting a rolling run surface of the moving member, smaller than the contact diameter of the contact portion for contacting a rolling run surface of the track member, the moving member with respect to the track member operating stroke of the moving member the amount, when the holding member displacement amount a shift amount of the rolling element retaining member with respect to the moving member, the rolling finite characterized in that the ratio of the holding member displacement amount with respect to the operating stroke smaller than 1/2 Exercise guidance device. 2. The finite rolling motion according to claim 1, wherein the rolling element is a ball, the rolling surface of the moving member has a Gothic arch groove shape, and the rolling surface of the track member has a circular arc groove shape. Guide device. The rolling element is a step roller including a cylindrical large-diameter portion and a cylindrical small-diameter portion having a diameter smaller than the large-diameter portion, and the small-diameter portion is formed on the rolling surface of the moving member. The finite rolling motion guide device according to claim 1, wherein the diameter portion is in contact with a rolling surface of the track member. The rolling element is a roller whose outer peripheral shape of the cross section including the rotation center axis when rolling is an arc shape,
By changing the position of the rotation center axis direction of the contact portion for contacting a rolling run surface of the raceway member and the contact portion which contacts the rolling run surface of the moving member, the contact portion which contacts the rolling run surface of the moving member The finite rolling motion guide device according to claim 1, wherein a contact diameter is smaller than a contact diameter of a contact portion that contacts a rolling surface of the raceway member. The rolling element retaining member finite rolling motion guide device according to any one of claims 1 to 4, characterized in that longer than the length of the moving direction of the moving member.

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