JPS58621A - Direct-acting guide - Google Patents

Abstract

PURPOSE:To heighten the accuracy of machining, by using a plane and a cylindrical surface as references to form a housing and a ball retainer for rolling balls round between the housing and a guide shaft and by providing grooves which have the same arc shape and extend at equal intervals on the inside of the housing. CONSTITUTION:A direct-acting ball bearing comprises a housing 1 of simple form, a cylindrical ball retainer 3, balls 2 and a guide shaft 8. The housing 1 has an axial opening in the center of the body shaped as a rectangular parallelepiped and has numerous grooves 10 having the same arc shape. The ball retainer 3 has numerous arc-shaped protrusions 14 extending on the peripheral surface of the retainer in the axial direction and corresponding to the axial opening of the housing 1. The retainer 3 also has guide grooves 15 extending on the peripheral surface to roll the balls 2 round. A small clearance is defined between the inside surface of the ball retainer 3 and the guide shaft 8. The balls 2 are fitted in circulation passages consisting of the arc-shaped axial grooves 10 of the housing 1 and the guide grooves 15 of the ball retainer 3.

Description

[Detailed Description of the Invention] With the spread of automatic control systems using small computers, the demand for high-performance linear motion guides has increased in various types of cutting machine tools, robots, etc. ing. The present invention is applied between a bearing that supports a reciprocating movable table and a shaft that guides a skeleton bearing.

The aim is to realize a high-performance linear motion guide that supports loads by interposing a large number of circulating balls. In other words, this one! In the conventional product of IIIIIIJ guide.

The structure and the shape of the component parts are complicated, and rational consideration is insufficient for linear motion guide accuracy and #1 characteristics such as load resistance, quietness, and dynamic rigidity required during operation.

In the present invention, we focused on improving the machining accuracy of the left and right bearings and the guide shaft to improve the precision of FL1 of the 2Il motion guide. If the shape is K.

Load-bearing to facilitate application in machinery.

Achieves thermal miniaturization while maintaining characteristics such as rigidity, and improves dynamic rigidity when fluctuating loads are applied to the bearing, such as when driving a table during heavy cutting or interrupted cutting in machine tools. Focusing on this, it is important to be able to easily and rationally set the preload required for this purpose.

In accordance with the above policy, the structure of the linear motion guide of the present invention is shown in the attached Figure 1, and in the front view and side view in the axial direction of the 2-factor embodiment, 1 supports the movable table, and there is a space between the guide shaft and the guide shaft. The main frame consists of a linear motion ball bearing.

2 has a small transfer between the main body of the mount and the guide shaft.

A ball supports the load; 3 is a ball holding part for forming a path for circulating the ball within the pedestal body; 4 is a companion part for positioning and fixing the ball holding part 3 in the gantry main body in the axial direction of the pedestal. Side plate, 5
is a screw for fixing the side @4 to the pedestal, 6 is a screw hole for fixing the pedestal to the moving table, and 7 is lI! Tast seal fixed to 1tL6, 8 is the guide shaft, and 9 is the ninth bolt hole for attaching the guide shaft to the pace. As shown in the figure, the linear motion guide of the present invention integrates the outer cylinder of a normal linear motion ball bearing and a bearing housing, and has an axial hole in the center of the rectangular parallelepiped. A stand main body 1 having a simple shape having a large number of circular arcs of the same shape, and a large number of circular arc-shaped protrusions in the axial direction on the outer circumferential surface for fitting into axial holes in the stand main body. 2. A cylindrical ball holding sleeve having a guide groove for circulating the balls and formed by providing a slight gap between the inner circumferential surface and the guide shaft 8.3. Holding one ball and the stand body with a dust seal inside between the ball @8 in the circulation path formed by the axial circular arc groove of the hole in the stand body and the guide groove for self-rolling on the outer circumferential surface of the stand holding part. These components of the present invention consist of a pedestal consisting of a side plate for axial positioning with the mount, and a guiding shaft applied to the pedestal and having a rectangular cross-sectional shape in the axial direction. It is formed based on a flat surface and a cylindrical surface, and consists of nine simple shapes, and it can be used not only for setting the reference plane required for fM precision machining, cylindrical precision cutting and other machining of each component part, but also for the inside of the frame body. This is due to the fact that the circular arc grooves in the axial direction of the hole have the same shape and are arranged at equal intervals on one cylindrical surface. It is easy to manufacture high-precision molds using the nI @ Cold Seki forging method using the circular arc grooves and the injection molding method of the ball holding part that fits into the hole, and the structure of the mount.

Eleven drifting paths for balls in three to several rows in the axial direction, which are essential to be formed within the mount, are formed by adapting them to the space between the axial hole of the mount body and the guide shaft, and nine ball holding parts are formed. It can be effectively formed using other methods.

Compared to conventional products, the overall size can be changed without reducing the functions required for the frame, making it possible to simplify the application of this AM motion guide to many types of machinery. In addition, when manufacturing the guide shaft that controls the n degree of the linear motion guide, the right-angled wtr surface shape in the axial direction is formed on the slope formed at the corner of the top surface and both side surfaces, or is formed close to the base mounting surface. The trapezoidal groove in the axial direction is formed, and the outside of the rolling groove of the ball formed on these slopes is a simple shape based on a rectangle, making it easy to set the reference plane during the precision machining mentioned above. From the butterfly, the above-mentioned axial slope 1 trapezoidal groove 1 sphere transfer arc #IK
By cold drawing from a rectangular cross-section material. Forming processing before quenching heat treatment and grinding processing can be easily performed.

Figures 3 and 4 show a front view and a side view of the mount body 1 in the ring direction.

The said axial hole having a number of axial arcs $10 around its periphery and an open end 11 at the bottom is molded, and for the said arc #10 around the #hole, a guiding shaft 80
Depending on the number of raw materials to be placed around the periphery and their symmetrical peripheral positions in the cross section at right angles to the axis, they are placed at equal intervals around the hole and in the radial direction from the center of the hole. In 1, the center is set at equal dividing points corresponding to the number of the circular grooves in the upward direction of the circular arc of the half pole R shown in the figure.

A circle IA, somewhat larger than the radius of sphere 2, is formed.

These circular arc grooves in the axial direction having the same size and shape, together with the guide groove for rolling the #i ball of the ball appropriately formed in the outer circumferential direction of the ball holding part 3, are used to control the load support range and the axial direction for the ball. In addition to forming a transfer branch path for the ball, the remaining arcuate groove conforms to the axial convex portion formed on the outer periphery Lfi of the ball holding portion 3.
This corresponds to the positioning of the ball holding part in the hermitage direction to the gantry body.

It is easy to form a large number of circular arc grooves in the axial direction as described above, so that the depth of each groove is uniform and shallow. After that, it can be done by cold pressing using a punch with the same shape as the hole after forming on the outer periphery. When comparing this with cutting using a broach, it was found that Due to the ease of processing, it is possible to form with higher precision, and in addition to reducing processing costs due to the superiority of tool durability, it is also possible to reduce the processing cost due to the rolling of the ball ts compared to the cutter J processing. You can also expect good results. Next, 12 in the figure is 6b for the microvolume transfer of one ball that is inclined in a conical shape toward both ends in the axial direction of the hole in the stand.
9.13 is the flank surface that is considered to be positive, and 9.13 is the axially both ends s of the frame.
This is a screw hole for fixing the side plate.

The attached figures 5 and 6 are an axial front view and a side view of the ball holding part 3, and 14 in figure 1 shows an axial circular arc groove 10 formed on the outer circumferential surface of the inner circumferential surface of the axial hole of the pedestal. Shaped to fit round axial convexity.

'15 is a guide groove for m* transfer of an axially oval ball similarly molded on the outer circumferential surface. An axial elongated hole 16 is formed in the range where the holding shaft rolls in the axial direction. Reference numeral 17 denotes a hole for supplying the ball into the guide groove from one end in the axial direction of the outer circumferential surface of the ball holder ρ guide $15 after the ball holder is fitted into the above-mentioned axial hole of the gantry body. Reference numeral 18 denotes a reinforcing sheet metal when the ball holding portion is made of resin material by injection molding.

Figures 7 and 8 are a front view and a side view of the sheet metal for reinforcing the ball holding part in the axial direction of the bamboo broom. The axially elongated hole 16 explained in connection with the ball holding part is formed at the position of the raw material in the inner mold support range.

Attached FIGS. 9(A) and 9(B) are a front view and a side view in the axial direction of the side plate 5 of the pedestal. A dust seal 7 for the shaft 8 is attached around the shaft 8 to maintain a certain amount of play. Further, reference numeral 19 indicates a bolt hole for fixing to the frame body.

Attached FIGS. 10 (A) and CB) are an axial front view and a side view of the guide shaft 8. As shown in FIG. fl+ surface addition, and trapezoidal axial grooves 21 are formed near the bottom of both sides,
22 rolling grooves in the axial direction of the ball 2 are formed on each slope and one side slope of the trapezoidal groove, and 9 in Figure 1 is a bolt hole for solid construction into the mounting base of the shaft, and the rolling groove of the ball 2 with respect to the shaft is formed. Depending on the arrangement of the dynamic grooves and the configuration of the mounting plate of the shaft in the ike machinery, a screw hole may be formed in the bottom of the shaft to fix the shaft to the pace.

Figure 11 shows the load acting on the linear motion guide surface via the mount of the present invention@intuitive guide, and the load resistance of the linear motion guide against this load.
Also, in the explanatory diagram of the restraint of the guide shaft with respect to the pedestal, the magnitude and direction of the load acting on the pedestal of the linear motion guide and the guide shaft differ due to the difference in the configuration of the movable table of the machinery. In the linear motion guide of the present invention, due to the structural characteristics.

・It is impossible to set an excessive load capacity against external forces from either the vertical direction or the horizontal direction for the cross section shown at right angles to the axial direction. In the embodiment shown in Figs. 1 to 11 above, the driving force in the load supporting range is arranged symmetrically at four locations on the guide shaft side, each in a direction inclined at 45 degrees with respect to the vertical plane including the fine details. , the structure is such that the load bearing capacity is equal in the vertical and horizontal directions, and in this case, the rolling groove of the ball required in the frame corresponds to the rolling groove of the driving force in the load support range for the shaft. teeth.

The numerous circles molded in the axial direction inside the frame body in Figure Bo, the same as the rolling grooves molded on the shaft on the left and right sides of a common vertical plane that includes the fineness of the hole that matches the fineness of the shaft in P Brocade. 45 including the axis
°It corresponds to a transfer groove located in an inclined direction,
In the linear motion guide of the present invention, the arrangement between the rolling grooves of the balls formed around the shaft 8 and the hole in the frame body is as follows.

The size of the hole in the axial direction in the mount body, as well as the dimensions and shape of the numerous arcuate grooves and arcuate projections formed in the axial direction around the hole and on the outer peripheral surface of the ball holding part.

In addition, by keeping the number of grooves and protrusions constant, and based on the above arrangement method, it is possible to select the arrangement of the rolling grooves of the ball formed on the shaft according to the direction of load action and its magnitude. be.

Attached FIGS. 12(A) to (F) show 91 examples of forming axial rolling grooves on balls arranged around the guide shaft explained in FIG. 11 above, and from these examples, With respect to the load capacity in the left and right directions of the shaft, the values of the load capacities in the upper and lower directions can be selected within a considerable range. The reason why the load capacity of both is shown as 4- is to keep the deformation of the frame symmetrical due to the setting of the preload, and the above-mentioned preload acting on the linear guide is When applying external forces including loads without considering the uniformity of the rigidity in the left and right directions, we also provide an example of an asymmetrical arrangement of the drive with respect to the shaft in order to accommodate the asymmetrical load capacity.] It is Noh.

Attached FIGS. 13(A) and 13(B) are explanatory diagrams of the preload setting method in the linear motion guide of the present invention, and FIG. 1(A) shows the ball 2 and the gantry main body 1. and shaft 8, the gap is set to zero, and the contact thickness pressure between them is also small.

In figure (B), the sphere diameter d in the setting condition of figure 9 (A) is increased by the amount d.

At this time, deformation occurs between the ball 2, the frame body, and the shaft 8 within their respective elastic ranges, and contact pressure is generated between them, so that no preload is set 7L. That is, the setting of the preload in the linear motion guide of the present invention is performed by selecting and applying the diameter of the upper B self-ball 2, and for this purpose, the gantry main body.

The sum of the contact pressure generated between the ball, the shaft, and the frame body in response to the elastic deformation produced by the ball and $1]K results in an appropriate preload as a linear motion guide. is necessary. The dimensional difference in the dimensions given to balls of the same nominal size, which is necessary for setting a single preliminary cover, is approximately 0.02+a+radicality, and due to this slight elastic deformation, it is necessary to In order to set the contact pressure between the turret and the pedestal body, as well as the shaft, the above-mentioned spheres and pedestal body are involved.

It is necessary to strengthen the rigidity of both sides of the pedestal, which has the largest elastic displacement at the contact portion, by 1% of the rigidity of the shaft. Steel, which has superior rigidity compared to cast iron, is used as the material for the mount body of the linear motion guide of the present invention, and the inner circumference, which corresponds to the outer diameter of conventional linear motion ball bearings, is used for the axial movement of the balls wJ.
Unlike the case where the stand is constructed by applying a sleeve made of tiles, 2 For example, in the size and shape of the 111 side of the stand main body in the embodiment shown in the attached Figures 1 and 2, the above method is not applied. The resulting deformation of the @ surface can accommodate the manufacturing tolerances of the selectable sphere diameter. Also, in Figure (B), this occurs with the setting of the preload. The value of the deflection angle Me that occurs symmetrically on both sides of the pedestal body, and the value of the displacement angle d' that occurs in the peripheral direction of the contact point between the transfer groove of the pedestal and the shaft and the ball corresponding to this, Fi, is also 0. It is a false value of around .1 degree, and the influence on the deformation of the mount body caused by the setting of the planned conger load and the change in the transfer conditions of the ball in the transfer groove is (a
It is also possible to ignore changes in sheathing and performance that are necessary for linear motion guides.

In addition, the linear motion guide of the present invention is related to setting an appropriate preload by selecting and applying the above-mentioned ball diameter. The most important thing to keep in mind is mold. In other words, the rolling groove of the ball formed around the axial hole of the main body of the mount is honed after the above-mentioned high degree of press working, so that the finishing process of the foot of the shrine is easy, and it is also used for guiding. For the rolling groove of the shaft, the shock surface during machining around the shaft must be determined with high precision, and the adjacent molding during grinding to j machining must be performed.

By number + 1 kifil + uf efficient grinding of positioning method.

Alternatively, the rolling grooves formed in the above-mentioned mount body and shaft are formed with high precision using a center support type machine, etc., and the rolling grooves in each hole and shaft are meticulously processed. The diameter of the circumscribed cylinder can be measured directly, using a suitable measuring jig, and easily measured by measuring the diameter of the circumscribed cylinder. This allows you to choose the diameter of the sphere accurately.

[Brief explanation of drawings]

#! 1 and 2 are an axial front view and a side view of the linear motion guide embodiment of the present invention, and 51IJ315!0 and 4 are axial front views of the mount body shown in FIGS. 1 and 2. Figures 5 and 6 are the axial front view and N side view of the ball holding part 3 in the stand shown in Figures 1 and 2, and Figures 7 and 8 are the 5th and 6th views. , an axial front view and a 94m view of the sheet metal 8 for reinforcing the ball holding part 3 shown in FIG. 6, and FIGS. 9(A) and (B).
10(A) and 10(B) are an axial front view and a gsIo diagram of the guide shaft 8, and FIG. 11 is a linear motion of the present invention. 12(A) to (F) are explanatory diagrams of the load capacity of the guide, and FIG. 13(A) ( B) is an explanatory diagram of a preload setting method in the linear motion guide of the present invention. In addition, each of the symbols in the figure is as follows: 1 gantry main body 2, ball 3, ball holder 4, gantry side plates 5, 11 fixing screws 6 on plate 4, screw holes 7 for fixing the gantry main body to the moving table, dust seal 8, Guide shaft 9, bolt hole 10 for fixing the shaft 8, arcuate groove 11 for transferring the ball inside the gantry body, open end 12 of the hole in the gantry body, flank face 13 in the axial front view of the hole in the gantry body, fixing the side plate 4. threaded hole 14, convex portion 15 on the outer circumferential surface of the ball holding part 3, #, a ball guide groove 16 facing the outside of the holding part, an elongated hole 17 in the guide $15, a ball supply hole 18 into the guide groove 15. Sheet metal 19 for reinforcing the ball holding part 3 Bolt holes 20 for side & 4 fixing, slope 21 formed on @8, trapezoidal groove 22 formed on the shaft 8, ball rolling groove 23 formed on the shaft 8. Screw hole R1 for mounting shaft 8 Distance r from the center of the axial hole of mount body 1 to the center of the arc $10 formed in the axial direction around the hole, Radius of arc 10, Prediction weight setting Inclination angle d' of the axial direction of the gantry main body l due to the rotation of the ball and the ball due to the preload 1 setting! Angle of deviation in the contact direction between EF11 surfaces Patent applicant Su 1) Minoru ¥7 (2) ¥8 Figure 9 (A) (B) (A) (B) Certain 17 Figure 12 (A) (8 ') (C) (D) (E) No. 130 (A) (B) Procedure Supplement iF + Akira, India s-mol/month 2f day Commissioner of the Patent Office Shima 1) Haru (1,l 1111 cases of assault) Displayed in 1982 Patent 111 ICI No. 094551, Name of the invention / Jit 1 guide r Sanno person / (1 I cow and ν 11 series / Samurai license delivery i order person fi: Location 1-23 Oto, Mono City, Naio prefecture No. 11 (prefecture name, ? own)
1"1 ze□rku)i゛-1 jyama11-life@J")'+3 i'f
4E 'fl]5 64j-101]2 7 F-1
t4 (4+jlj surface (41st 1, 12th fig.
, D, F] F) Complement 1: Contents of 1 + '-14 - Calculation 4 Figure 12 (D) (E) (F)

Claims (1)

[Scope of Claims] +11 A straight line constituted by interposing a plurality of cyclically rolling ball rows between a guide shaft and a frame adapted to the guide shaft that supports a moving table of one piece of machinery and makes reciprocating motion. In the motion guide, the mount main body IK, whose outer peripheral surface is a rectangular parallelepiped, has a cylindrical hole with an open end formed on the bottom surface of the mount in the direction of linear motion of the mount. A large number of circular arc tiles in the axial direction are formed into a strange ζ axis 1 with a radius r somewhat larger than the radius of the two balls 2 centered at each position equally divided in the peripheral direction on the circumference of a circle with a constant radius R. It is shaped to fit the circumferential position of the ball's rolling groove. The outer peripheral surface of the ball holding part 4 to be inserted into the hole has a large number of axial protrusions molded into the hole of the mount body so that it fits regardless of the neighboring circular arcs in the axial direction, and each of the load supporting ranges. An axially oval guide groove for circulating and rolling nine balls is formed corresponding to the ball rows,
The ball supporting the load in the guide groove is connected to the pedestal main body l and the shaft 3.
An elongated hole is formed in the axial direction from the groove bottom to the inner circumferential surface of the ball holding part within the range of rolling while maintaining simultaneous contact with the ball holding part. It is molded into a polygonal shape with a small gap between it and the 9 axes to accommodate the
In the peripheral direction, an open end is formed that is located at the open end of the hole on the bottom of the main body when inserted into the gantry main body, with a slight gap between it and the shaft 1, and a certain range in the peripheral direction of the main body is omitted. . In addition, the shaft 3, which has a cross-sectional shape based on a rectangle, has a top surface, a top surface, and both side surfaces of the shaft, corresponding to the vertical and horizontal load σ] that acts on the shaft through the mount. An arcuate groove for transferring the ball in the axial direction, which is formed by an arc somewhat larger than the outer circumference σ) of the 3 to 9 balls 2, is suitably formed on the corner and the slope of the trapezoidal trapezoid with both sides Ka-shaped near the bottom. . Next, in assembling the linear motion guide, a large number of Pla grooves in the axial direction are formed on the circumferential surface of the axial hole formed in the gantry main body 1. The two ball holders are inserted into the holes in the pedestal main body by matching the circular grooves with the same number of axial arcuate protrusions formed on the outer periphery of the holder, and then the axial arcuate grooves in the holes in the gantry main body are inserted. After supplying a large number of balls into the ms path of the balls formed by the axially oval circular rolling guide groove formed on the outer peripheral surface of the 1-ball holding part, The side plates 5 are fixed to both end faces, and the axial position of the ball retainer 4 with respect to the mount body 1 is completed to complete the assembly of the mount. A linear motion guide characterized in that the mount and the shaft are combined by fitting the ball with the rolling groove of the IK-molded ball into the shaft and combining the frame and the shaft. Great) Claim 1! (1) In the linear motion guide described above, a large number of circular arcs #$10 in the axial direction around the axial holes to which the ball holding portion 3 of the mount main body l is fitted are formed using a punch having the same shape as the holes formed by forming these circular arc grooves. Using [! ! After forming a cylindrical pilot hole, the above punch is used to form the cold pressing method! Direct motion guide with mold.