CN100419286C - Linear Motion Devices and Linear Guides - Google Patents

Abstract

A separator for a linear guide having a guide rail, a slider provided on the guide rail so as to move relative to each other, and a plurality of roller-shaped rolling elements combined with the slider; the separator The separator includes: a separator main body having recessed surface portions on both sides in the front-rear direction thereof, the recessed surface portions contacting the circumferential portion of the rolling element; and at least one pair of arm portions, the at least one pair of arm portions When the arm parts are in the same direction, they are parallel to each other on both sides of the separator body, wherein the length of the arm part is equal to or less than the center distance of two adjacent rolling elements with respect to the side direction of the separator body, and the separator body is sandwiched between between adjacent rolling elements.

Description

Linear Motion Devices and Linear Guides

This application is a divisional application of the invention patent application with the title of "separator and linear guide using the separator and linear motion device" and application number 200410008549.1 submitted to the Chinese Patent Office on February 10, 2004.

technical field

The present invention relates to a linear guide, and more particularly, the present invention relates to a separator (separation element), a linear guide provided with the separator, and an apparatus using the linear guide .

The invention also relates to a direct-acting device for use in industrial machinery, for example, a linear guide bearing, a ball screw, a ball spline and a linear ball bush.

Background technique

A linear guide using roller-shaped rolling elements as rolling elements includes: a rail for guiding an object that moves linearly; and a slider movably arranged on the rail. When the slider moves over the guide rail in the longitudinal direction, a plurality of roller-shaped rolling elements are combined with slider rollers in the longitudinal direction of the guide rail to form one raceway on the guide rail and another raceway formed on the slider between.

Compared with linear guides using spherical rolling elements, this linear guide has greater stiffness and load-carrying capacity. When adjacent rolling elements contact each other, the respective rolling elements rotate in opposite directions at the contact area. Therefore, the frictional force generated in the contact area creates a limit to the smooth rolling of the rolling elements. In the linear guide described above, axial fluctuation, so-called skew, occurs in the rolling elements, thereby impairing the operability of the linear guide.

To solve the above-mentioned problems, JP-A-2001-132745 and JP-B-40-24405 provided hereinafter disclose a linear guide having Separators to prevent mutual contact and skewing of the rolling elements.

However, the linear guide disclosed in JP-A-2001-132745 utilizes a separator sandwiched between roller-shaped rolling elements, a separator main body, and a flange portion, wherein the front-rear direction of the separator main body There are recessed surfaces on both sides in contact with the peripheral surfaces of the roller-shaped rolling elements; the flange portions extend in opposite directions from either side of the separator body and contact one end surface of the rolling elements. Therefore, the rotational resistance of the rolling elements increases at one end of the separator main body, thereby lowering the rotational balance of the rolling elements. Therefore, the effect of suppressing skew is insufficient.

In the linear guide disclosed in JP-B-40-24405, a structure is adopted in which separating elements are used as separators, wherein center-facing rolling elements are arranged on both sides of each separating element. Extended disc web. The webs of the separating elements contact and support each other in the vicinity of the centers of the rolling elements. Thus, a gap is created between any adjacent rolling elements and between any adjacent separating elements. Therefore, the center-to-center distance of two adjacent rolling elements with a separating element interposed between them is larger than necessary. Thus, this may reduce the number of rolling elements in the load zone, resulting in a reduction in load carrying capacity. Furthermore, in the case of using the linear guide disclosed in JP-B-40-24405, the lateral width of the separation element is larger than the axial length of the rolling element. Thus, a gap is created between the end faces of the rolling elements and the web. In this way, the effect of suppressing the occurrence of the above-mentioned skew is not large.

In a linear guide in which a plurality of rolling elements are arranged, the rolling elements circulate in uninterrupted motion and each rolling element rolls in a single direction. When adjacent rolling elements contact each other, the rolling elements rotate in opposite directions in the contact area. Therefore, the forces that are generated and press the rolling elements in the contact area prevent smooth rolling of the rolling elements that are in contact with each other. This impairs the smooth operation of the linear guide.

Compared with the case where spherical balls are used as rolling elements, when cylindrical or cylindrical rollers are used as rolling elements, the hardness and load-bearing capacity (allowable bearing load) of the rolling elements can be improved. However, axial undulations in running rollers are so-called skew (a phenomenon in which the longitudinal axis of a cylindrical or cylindrical roller cannot be kept perpendicular to the direction of motion of the roller, resulting in skewing), which can impair rolling operability of the element, which further impairs the operability of the linear guide.

For this reason, the linear guide is configured to prevent the rolling elements from directly contacting each other by interposing a separator (separation element) between the rolling elements so that the rolling elements roll (run) smoothly, thereby improving the operability of the rolling elements And reduce the noise generated by rolling elements during operation.

For example, separators sandwiched between rollers are described in JP-B-40-24405, JP-UM-A-52-110246, and JP-B-56-2206 provided below.

JP-B-40-24405 discloses a separating member (separator) using a separating member as a bearing using a roller. The separating element has a recessed contact portion cooperating with a cylindrical surface of the roller and an arm portion (web). Said arms (webs) are arranged on respective sides of the separating element, the arms being arranged on each side of the separating element and extending to the center of the roller, the separating element being aligned with the center of the arm in the direction of linear movement. Such separating elements have their arms in contact with arms extending from adjacent separating elements.

However, the structure of the separation element disclosed in JP-B-40-24405 is such that an arm portion disposed in the next separation element transmits to the next separation element the force that rolls and moves when the roller is passed to the separation element. In practical applications, separating the components creates the following problems.

When the motion of the rolling elements transitions from a linear portion to a redirected portion, a change occurs in the area where the arms contact each other, thereby increasing the distance between the rollers. Initially, in order to increase the load-carrying capacity of the linear guide, the rollers and separating elements are arranged relatively close together in the deflection section in order to arrange a maximum number of separating elements in one load-bearing area. For this reason, through the action of increased force, a force greater than necessary acts on the rest of the arms that are in contact with each other, thereby preventing the smooth movement of the rollers and separating elements and destroying the operability .

As described in JP-B-40-24405, in the case where the separating element transmits the force by bringing the arms into contact with each other, a gap is created between a roller and a separating element located at the before or after the rollers; this is not sufficient to prevent skewing. Furthermore, the number of rollers arranged in the load zone is also limited by the gap. Thus, the carrying capacity cannot be sufficiently improved.

In linear guides, a slide moves relative to a rail while multiple rolling elements roll along a continuous, endless path. When the slider moves relative to the guide rail, each rolling element moves while rolling in one direction, whereby adjacent rolling elements come into contact with each other. This causes problems in that smooth movement of the rolling elements is hindered, wear of the rolling elements increases rapidly, and noise increases.

Therefore, there is currently known a linear guide that smoothly rolls rolling elements to suppress early wear of the rolling elements, and a separator is arranged between adjacent rolling elements to brake the linear guide and suppress noise diffusion (eg See JP-A-11-247855, JP-A-2000-291668, JP-A-2001-317552, JP-A-2002-089651, JP-A-2002-039175, JP-A-2002-156018).

A known conventional separator has an arm or the like for supporting adjacent rolling elements at predetermined positions. For example, according to the technique disclosed in JP-A-11-247855, a rolling element chain is constructed by connecting adjacent separators with rolling elements interposed between the adjacent separators. The rolling elements are arranged in parallel in a continuous circulation path by interconnecting with separators. Therefore, axial fluctuation (skew) of the rolling elements and mutual interference between the rolling elements are weakened, so that the rolling elements can stably circulate.

According to the techniques disclosed in JP-A-2000-291668, JP-A-2001-317552, JP-A-2002-089651, JP-A-2002-039175 and JP-A-2002-156018, the groove or the A bore-formed lubricant reservoir portion is formed in the separator for storing lubricant. Since the lubricant reservoir portion is formed in the separator, the rolling elements can smoothly roll, thereby braking the linear guide while preventing premature wear of the rolling elements and eliminating noise generation.

However, according to the technology disclosed in JP-A-11-247855, the separator is not provided with grooves, through holes or the like, according to JP-A-2000-291668, JP-A-2001-317552, JP-A-2002 - 089651, technology disclosed in JP-A-2002-039175, JP-A-2002-156018, the similar part is used to store lubricant. Accordingly, these disclosed techniques provide improvements in smooth rolling motion of rolling elements, suppression of premature wear of rolling elements, and braking of linear guides while eliminating noise generation.

Meanwhile, according to the techniques disclosed in JP-A-2000-291668, JP-A-2001-317552, JP-A-2002-089651, JP-A-2002-039175 and JP-A-2002-156018, the separator does not An arm or the like is provided, which is used to positively adjust the position of the rolling element according to the technique disclosed in JP-A-11-247855. Therefore, while effectively suppressing axial fluctuations (skew) in the rolling elements and mutual interference between the rolling elements, the problem of stable cyclic motion of the rolling elements remains unsolved.

The inventors of the present invention have developed a separator which can completely solve the above-mentioned problems.

The assembly operation of manually inserting the rolling elements into the continuous circulation path while sandwiching the separator between adjacent rolling elements is time consuming. Therefore, automation of assembly operations is required as productivity increases.

Therefore, one possible method is to line up the separators by using an automatic alignment machine such as a feeder, and continuously automate the assembly operation by using such as a robot.

Although separators can completely solve the aforementioned problems, it is still necessary to provide multiple separators and lubricant reservoir parts. The lubricant reservoir part is formed by a recess or a through hole. An experiment with self-aligning separators was performed. In some cases, the arms fit into through holes or the like that act as lubricant reservoirs, which can cause the separators to become entangled with each other and eventually fail to align the separators.

As mentioned above, there are still some problems to be solved before realizing that the separator has the functions of adjusting the position of rolling elements and storing lubricant, and the automation of production needs to be considered.

As shown in FIG. 41, a linear guide bearing device is known as a conventional direct acting device, and has an axially extending guide rail 501 and a slider 502, which is held by It is provided so as to straddle the guide rail 51 and be relatively movable in the axial direction.

Two axially extending raceway surfaces 503 are formed on either side surface of the guide rail 51 in the transverse direction of the guide rail 51, so four raceway surfaces 503 are formed in total. A raceway surface 505 opposite to the raceway surface 503 is formed on each inner side surface of the sleeve portion 504 of the slider main body 502A of the slider 502 .

A plurality of cylindrical rollers 506 as rolling elements are cyclically loaded in rotation between the raceway surfaces. The slider 502 is axially relatively movable on the guide rail 501 by the rolling motion of the cylindrical roller 506 .

When the slider 502 moves, the cylindrical roller 506 sandwiched between the guide rail 501 and the slider 502 turns and moves toward the axial end of the slider 502 . However, in order to continuously move the slider 502 axially, the cylindrical roller 506 must constantly rotate.

A through hole 507 is formed on the sleeve portion 504 of the slider main body 502A so as to penetrate the entire sleeve portion 504 . A circulation pipe 8 is fitted into each through hole 507, wherein the inner side of the circulation pipe 8 forms a passage (rolling element passage) 508a for the cylindrical roller 506. A pair of end caps 509 as rolling element circulation parts are fixed to respective axial ends of the slider main body 502A by using screws or the like. A redirection passage 510 (as shown in FIG. 42B ) which communicates the raceway surfaces 503, 505 with the rolling element passage 508a and is formed into a semi-ring shape is formed on each end cap 509, thereby providing Cylindrical rollers 506 form a continuous endless path.

A plurality of cylindrical rollers 506 that rotate along a continuous endless path rotate in one direction about the roller axis. When adjacent cylindrical rollers 506 are in contact with each other, the speed directions of the rollers in the contact area are opposite to each other. The forces generated by the mutual contact hinder the smooth rolling motion of the cylindrical rollers 506 .

As shown in FIG. 41, in this case, separators (separation elements) 520 are interposed between adjacent cylindrical rollers 506, thereby suppressing the cylindrical rollers 506 from coming into direct contact with each other. Therefore, the operation of the slider 502 will be smooth, and the noise generated during the operation of the slider will also be reduced. 42 to 44, wherein the separator 520 includes a separator body 521 and an arm 522, the separator body 521 is sandwiched between adjacent cylindrical rollers 506, and the arm 522 is arranged so that the cylindrical roller 506 The shaft end surfaces of the arm portions 522 are sandwiched between the arm portions 522 , and the arm portions 522 are integrally formed with the separator main body 521 . A recessed portion 521 a conforming to the shape of the outer circumference of the cylindrical roller 506 is formed in a region of the separator main body 521 that is opposed to the outer peripheral surface of the cylindrical roller 506 . In FIG. 41 , reference numeral 523 denotes a separator guide that is interposed between the outer end surface of the guide rail 501 and the inner end surface of the slider 502 .

When the cylindrical roller 506 rotates in a space defined by the raceway surfaces 503 and 405, the redirection passage 510 and the rolling element passage 508a, the arm portion 522 of the separator 520 moves along the direction of rotation of the cylindrical roller 506. A guide groove 524 is guided, wherein the guide groove is formed on the separator guide 523 , the rolling element passage 508 a and the redirection passage 510 .

In addition, in order to absorb the fluctuation in the channel length direction due to the phase change of the rolling elements in the circulation channel (see JP-A-2002-21849), the applicant of the present invention has proposed to use artificial rubber such as ^Hytrel® or Pelprene ^@ (manufactured by Toyobo Corporation). Further, grease and lubricating oil or the like will swell the separator. Depending on the contact position between the rolling elements and the separator, the pitch between the rolling elements will greatly change, thereby causing problems that adversely affect operability, low-noise characteristics, and durability. Therefore, the contact position between the rolling element and the separator is defined to be equal to or less than 50% of the diameter of the rolling element, preferably in the range of 30% to 50% (when the parameter "contact position" is changed to the parameter "contact angle" , the "contact angle" within the range of the "contact position" is equal to or less than 30°, and the contact angle at the optimum position is 17.5° to 30°) (see JP-A-2003-49834).

However, depending on the radius of curvature "f" of the separator recess (determined by the value of (groove radius R of the recess)/(radius Dw of the rolling element)) or the bottom end of the groove of the separator recess The thickness 2 δ value, the contact position between the rolling element and the separator in JP-A-2002-21849 cannot always maintain the optimum value. For example, when the radius of curvature "f" of the recessed portion of the separator is 0.54, the radius Dw of the rolling element is 8mm, and the thickness 2δ of the recessed portion is 1.2mm (this value ensures that the load capacity required number of rolling elements), the contact position between the rolling element and the separator exceeds 50% of the diameter of the rolling element (corresponding to a contact angle of 30°), and 52% (corresponding to a contact angle of 31° ) is an optimal value (the dimensional difference between the expanded length in the radial direction of the separator and the expanded thickness in the thickness direction of the separator is zero (see Figure 45); the expansion in the radial direction results in a reduction in the pitch between the rolling elements , the expansion in the thickness direction leads to an increase in the pitch between the rolling elements).

Contents of the invention

The present invention has considered the foregoing problems, and aims to provide a separator for a linear guide that prevents contact between rolling elements and suppresses skew without reducing load capacity.

The present invention has considered the problems existing in the related prior art, and aims to provide a separator for a linear guide that can effectively suppress the reduction in load capacity and suppress the occurrence of skew, and adopts a simple structure to improve operability, and also provide a linear guide including the separator and a device including the linear guide.

The present invention has considered the problems posed above, and aims to provide a separator for a linear guide and a linear guide that attenuate the axial undulation (skew) inside the rolling element and the rolling element Interference between the rolling elements, by turning the rolling elements in a more stable manner and rolling the rolling elements more smoothly, thereby suppressing early wear of the rolling elements, suppressing the generation of noise, and improving the productivity of the linear guide.

The present invention has been considered to solve these problems and aims to provide a direct-acting device that suppresses the impact of expansion (expansion is caused by lubricant oil and grease or the like) between the rolling elements. This device can easily achieve improvements in operability, low-noise characteristics, and low-cost durability when fluctuating in pitch.

To achieve these objects, a first aspect of the present invention provides a separator for a linear guide having a guide rail, a slider arranged on the guide rail so as to be movable relative to each other, and multiple a roller-shaped rolling element combined with a slider, the separator has a separator body and at least a pair of arm portions, and both sides in the front-rear direction of the separator body have recessed surfaces contacting the circumferential surface of the rolling element part; when the at least one pair of arms is arranged in the same direction, they are parallel to each other on both sides of the separator main body, wherein the length of the arms is equal to or less than two adjacent arms with respect to the side direction of the separator main body The center distance between the rolling elements of which the separator main body is sandwiched between the two adjacent rolling elements.

Due to this configuration, it is possible to prevent the gap between the rolling elements and the separator main body, and finally reduce the number of rolling elements provided in the load-bearing area. In JP-B-40-24405, due to the length between the separator arms L is smaller than the center distance between two adjacent rolling elements, so the linear guide disclosed in JP-B-40-24405 also achieves this effect. Therefore, contact and skew between rolling elements can be suppressed without reducing load capacity. In addition, this also prevents the rotational resistance of the separator from being biased toward the rolling elements, which is also the characteristic of the linear guide disclosed in JP-A-2001-132745. Therefore, the effect of suppressing skew can be sufficiently obtained.

A second aspect of the present invention provides a separator for a linear guide according to the first aspect, wherein the height of the arm portion is about 20% to 60% of the diameter of the roller-shaped rolling element. By adopting this configuration, the separator main body is reinforced with the arm portion, and a sufficient contact area between the end surface of the rolling element and the raceway contacting the end surface is secured.

A third aspect of the present invention provides a separator for a linear guide according to the first aspect or the second aspect, wherein the side length of the separator main body is slightly shorter than the axial length of the roller-shaped rolling element, and the rolling One of the left and right side surfaces of the element contacts a surface formed on the inner side surface of the slider so that one of the left and right side surfaces of the rolling element is adjacent to the raceway of the slider, wherein the certain surface is in contact with the roller. Tao is formed simultaneously. Due to this configuration, the position of the rolling elements becomes more stable, thereby exerting an effective effect on suppressing skewing of the rolling elements.

A fourth aspect of the present invention provides a separator for a linear guide, wherein the linear guide has a guide rail, a slider provided on the guide rail so as to be movable relative to each other, and a plurality of sliding members Combining roller-shaped rolling elements, the separator has: a separator main body and a clearance groove, wherein both sides in the front-rear direction of the separator main body have recessed surface portions in contact with the circumferential portions of the rolling elements, and the clearance groove forms At the center of the recessed surface portion in the circumferential direction of the rolling element. Due to this configuration, the contact area between the separator and the rolling elements is limited to the left and right sides of the separator. Therefore, skewing of the rolling elements is suppressed, thereby improving the operability of the linear guide.

A fifth aspect of the present invention provides a separator for a linear guide according to the first or fourth aspect, wherein a through hole is formed at the center of the recessed surface portion to penetrate in the front-rear direction of the separator main body Recessed surface portion. With this configuration, lubricant can be stored in the through hole, and the lubricant stored in the through hole can be stably supplied into the rolling elements.

According to the first aspect, the separator of the sixth aspect of the present invention is a separator for a linear guide, further comprising a bridge portion for connecting the separator main body with the arm.

By adopting this configuration, the separators can prevent mutual contact. Thus, the separator can be operated smoothly, and furthermore, the rolling elements can also be operated smoothly. Since skewing of the rolling elements is suppressed, smoother operation can be performed. The rattling of the rolling elements against each other when entering the load-bearing area is also suppressed. Ultimately, noise and vibration generated during operation are suppressed.

If the distance between the rollers is shortened by increasing the number of rollers arranged in the load area in order to increase the load capacity, the roller contact portion of the separator body will become thinner in the moving direction (ie, the linear moving direction). As a result, the separator body will be weakened. However, according to the present invention the engagement between the upper and lower parts of the separator body is enhanced by the bridging portion between the arm and the separator, thereby strengthening the separator body.

Therefore, the distance between the rollers can be shortened while maintaining the required strength. Therefore, even if the separator main body is sandwiched between the rollers, the reduction in the number of rollers provided in the loading area can be minimized, and the drop in load capacity can be minimized.

The roller end surfaces are guided by the arms, thus the chances of the rollers coming out of the separator body and skewing will be minimized.

Furthermore, in the case where the separator is used as a linear guide, if the arm portion is guided, skewing of the rollers can be suppressed more effectively, thereby enabling smoother operation of the rollers and the separator.

A seventh aspect of the present invention provides a separator for a linear guide according to the sixth aspect, wherein, with respect to the height of the recessed surface, wherein the height is from a center of rotation connecting adjacent rolling elements The distance between the dotted line of , to the end surface of the recessed surface portion of the separator body, wherein the end surface is substantially parallel to the direct action surface of the rolling element, in the redirection portion; in this redirection portion, the movement of the rolling element The direction is changed around the preset center of motion; the height Ho of the recessed surface is greater than the height Hi of the recessed surface, where the height Ho refers to the end from the imaginary line connecting the centers of rotation of adjacent rolling elements to the end (the end is relative to the movement In terms of the center), the height Hi refers to the distance from a dotted line connecting the rotation centers of adjacent rolling elements to the nearest end (the nearest end is relative to the center of motion).

An eighth aspect of the present invention provides a separator for a linear guide according to the sixth aspect, wherein, with respect to the width of an end surface of the separator main body, wherein the end surface is substantially parallel to the The direct action surface of the rolling element, in the redirection part, the direction of motion of the rolling element is changed around the preset center of motion. The width "a" of the end of the separator body; the end being relative to the center of motion, is greater than the width "b" of the most proximal end of the separator body; the most proximal being relative to the center of motion.

If the separator is constructed in the manner described in the seventh and eighth aspects, the capacity of the separator body to accommodate the rollers will be increased. Therefore, skewing will be effectively suppressed, and roll separation can be effectively prevented. In particular, since the function of accommodating the rollers is enhanced at the redirection portion, when such a separator is used for a linear guide, the rollers can be prevented from coming off even if the slider is disengaged from the guide rail. Therefore, the ease of maintenance and assembly is improved.

A ninth aspect of the present invention provides a separator for a linear guide according to any one of the sixth to eighth aspects, wherein when the arms are configured to move from the center of the separator main body toward the When the rotation centers of adjacent rolling elements in the moving direction extend the same length, when the arm length on one side is represented by L, the diameter of the rolling element is represented by Dwe, and the center-to-center distance of adjacent rolling elements is represented by kDwe, from the center of motion The radius between the loci of movement to the center of rotation of the rolling elements located in the redirecting section is denoted by R, and the radius from the center of motion to the envelope surface, which is located closer to the center of motion than the dotted line, is denoted by Ri. Defined by the arm, the dotted line connects the centers of adjacent rolling elements (the height of the arm in the direction perpendicular to the raceway surface of the rolling element is represented by A), the arm forms a contour line, so that the length of one side of the arm Li (i.e. the length of an inner arm) where the arm is located closer to the center of motion than the dotted line connecting the centers of adjacent rolling elements, the length Lo of the other side of the arm (i.e. the length of the outer arm) , where the arm is located on the opposite side of the center of motion with respect to the dashed line connecting the centers of adjacent rolling elements, satisfying the following equation:

θ=sin ⁻¹ {kDwe/(2R)}, 0.3/2×Dwe≤A≤(R-Ri), Li<(kDwe/2-Asinθ), Lo<kDwe/2.

A tenth aspect of the present invention provides a separator for a linear guide according to any one of the sixth to eighth aspects, wherein when the arms are configured to When extending different lengths from the main body of the separator to the center of the adjacent rolling elements, the maximum value Ls of the total length of the arms extending on each side of the separator relative to the direction of motion is smaller than the rotational center distance kDwe of the adjacent rolling elements.

If the separators are constructed in the manner described in the ninth and tenth aspects, the arm lengths of adjacent separators are arranged such that they do not touch each other throughout the entire circulation path of the rollers. Thus, smooth operation of the rollers and the separator can be performed smoothly.

An eleventh aspect of the present invention provides a separator for a linear guide according to any one of the sixth to tenth aspects, wherein the contact surfaces on both sides of the separator body are at a certain Contact adjacent rolling elements at a location where the dimension between the groove contacting surfaces of the recessed surface portion is smallest.

By so configuring, even if expansion occurs, the effect on the dimensions between the contact surfaces of the recesses is minimal. Furthermore, the risk of the rollers coming off the separator, which would be caused by increasing the gap between the chains of rollers in which the separator is sandwiched, can be effectively prevented.

A twelfth aspect of the present invention is characterized in that there is provided a separator for a linear guide according to any one of the sixth to eleventh aspects, wherein a recessed lubricant reservoir is formed on a recessed surface. part of the contact surface. By configuring in this way, smooth operation of the rollers and the separator is enabled, wear of the rollers and the separator is suppressed, and generation of operation noise and the like is further suppressed.

The linear guide of the present invention is characterized in that it includes separators for the linear guide, which are provided between rollers as rolling elements, and these separators may be formed by any one of the first to twelfth aspects. aspect to limit.

By employing such a configuration, there is provided a linear guide that can effectively prevent a drop in load-carrying capacity and effectively suppress skewing, and improve operability by adopting a simple structure.

A linear guide according to the invention is characterized in that the linear guide is configured as a guiding arm. In this way, if the arm portion is guided, skewing of the rollers can be effectively suppressed, thereby enabling smooth operation of the rollers and the separator.

A device (a processing device in any of its various forms) according to the invention is characterized in that it comprises a linear guide according to the above aspect.

By employing such a configuration, there is provided a linear guide that can effectively suppress a load-bearing capacity drop and prevent skewing, and that can improve operability with a simple structure.

In order to solve the above problems, a thirteenth aspect of the present invention provides a separator for a linear guide according to the first aspect, wherein the guide rail has a roller guide surface, the slider has a bearing roller guide surface, A pair of redirection passages and a roller return passage, the carrying roller guide surface and the roller guide surface opposite to the roller guide surface jointly form a roller track, a pair of redirection passages communicate with the two ends of the roller track, the roller The return passage communicates with the pair of diversion passages, and the continuous circulation path is composed of the roller path, the pair of reversal passages and the roller return passage, and the linear guide has a guide groove in the continuous circulation passage, and the guide groove Continuous in the direction in which the rolling elements are set, the pair of arms are guided by guide grooves; the lubricant reservoir part is open at each recessed surface part, the opening of the lubricant reservoir is smaller than the outer dimension of the arms, This prevents the arm from fitting into the lubricant reservoir portion.

A fourteenth aspect of the present invention provides a separator for a linear guide according to the thirteenth aspect, wherein the maximum dimension of the opening portion is smaller than the maximum dimension of the arm portion, wherein the maximum dimension is perpendicular to the longitudinal direction of the arm portion Dimensions of the cross-sectional portion of the arm.

The invention features a linear guide featuring the use of a separator. The separator is used in the linear guide defined by the thirteenth or fourteenth aspect.

If the separators of the invention are used in a linear guide, the sides of each roller can be sandwiched between the recessed surfaces of adjacent separators. and secured by the recessed surface of the adjacent separator. Further, the positions of the rollers can be aligned by the arms formed on the separator. Therefore, if the separator of the present invention is used for the linear guide, axial fluctuation (skew) in the roller elements and mutual interference between the roller elements can be reduced, thereby enabling more stable circulation of the rolling elements.

The lubricant reservoir portion is open on the roller contact surface. Therefore, if the separator of the present invention is used for the linear guide, the rolling elements can roll more smoothly, and early wear of the rolling elements and generation of noise can be suppressed.

Furthermore, according to the thirteenth aspect of the present invention, the opening portion of the lubricant reservoir is smaller than the outer shape of the arm portion, thereby constituting the separator. According to the fourteenth aspect of the present invention, the maximum dimension of the opening portion is smaller than the maximum dimension of the arm portion, wherein the maximum dimension is a dimension of a cross section perpendicular to the longitudinal direction of the arm portion. Therefore, fitting of the arm into the lubricant reservoir can be prevented. For example, even if the separators are automatically aligned by means such as a feeder or the like, it is possible to prevent the separators from being entangled with each other. Thus, there is provided a separator for a linear guide that facilitates automation of production and can improve the productivity of the linear guide. There is provided a linear guide which has many advantages due to the use of the separator for the linear guide as defined in the thirteenth and fourteenth aspects.

The phrase "the arm fits into the lubricant reservoir part" is used here to mean that the arm of one of the separators fits into the lubricant reservoir part of the other separator so that the separators are connected to each other. stuck.

Further, the word "external dimensions of the arm" means any dimension that facilitates "fitting of the arm into the lubricant reservoir portion". For example, if the cross-section of the arm perpendicular to the longitudinal direction is only a rectangle, the dimensions that facilitate fitting are the lengths corresponding to the four sides and the length of the diagonal of the rectangle. If the cross-section is circular, this dimension corresponds to the diameter of the circle, and if the cross-section has another combined geometric shape, this dimension is the dimension of the parts of a shape that is raised in a direction that facilitates the assembly of the arms superior.

According to the separator for a linear guide of the present invention, not only a linear guide but also a separator used with the linear guide which can improve the linear guide piece productivity.

In order to achieve the above objects, a fifteenth aspect of the present invention provides a linear motion device having: a guide rail including a rolling surface; a slider including a rolling surface opposed to the rolling surface of the guide rail, and passing a plurality of rolling elements are guided by the rails, the rolling elements are interposed between rolling surfaces for relative movement relative to each other; and a separator is interposed between adjacent rolling elements and includes a recessed surface portion, the recessed surface A portion is formed in each of the spacer portions opposed to the rolling elements, wherein the contact position between the separator recessed surface portion and the rolling elements is set at a contact angle of 19° to 35°. within range.

A sixteenth aspect of the present invention provides a separator for a linear motion device, which has: a guide rail including a rolling surface; a slider including a rolling surface opposed to the rolling surface of the guide rail, and passing a plurality of rolling elements are guided by the rails, the rolling elements are interposed between rolling surfaces for relative movement relative to each other; and a separator is interposed between adjacent rolling elements and includes a recessed surface portion, the recessed surface A portion is formed in each of said spacer portions opposite said rolling elements, wherein the cross-sectional portion of the recessed surface portion forms a gothic arch shape; the diameter of the rolling elements is denoted by Dw, The contact angle between the separator and the rolling element is represented by θ; the radius of the clip-end arched groove of the concave surface part is represented by R; the groove bottom thickness of the concave surface part of the separator is represented by 2δ, and the groove bottom thickness of the concave surface part is represented by 2δ The radius of curvature is represented by "f", and the contact angle θ of the separator satisfies the following equations (1) to (3):

0.5Dw*sinθtanθ＝δ+R(cosθ ₀ -cosθ)(1)

θ ₀ = sin ^-1 [{(2f-1)/(2f)}sinθ] (2)

f＝R/Dw (3)

A seventeenth aspect of the present invention provides a linear motion device having: a guide rail including a rolling surface; a slider including a rolling surface opposed to the rolling surface of the guide rail, and is formed by a plurality of rolling elements guide rails, rolling elements interposed between rolling surfaces for relative movement with each other; and a separator, interposed between adjacent rolling elements and including recessed surface portions formed in relation to the In each spacer part opposite to the rolling element, the cross-sectional part of the concave surface part forms a single arc shape; the diameter of the rolling element is represented by Dw, and the contact between the separator and the rolling element The angle is represented by θ; the arc-shaped groove radius of the concave surface part is represented by R; the groove bottom thickness of the concave surface part of the separator is represented by 2δ, and the curvature radius of the concave surface part is represented by "f". The contact angle θ satisfies the following equations (4) to (5):

0.5Dw*sinθtanθ＝δ+R(1-cosθ) (4)

f＝R/Dw (5)

According to the seventeenth aspect, an eighteenth aspect of the present invention is to provide a separator for a linear guide, wherein the contact position range between the concave surface portion of the separator and the rolling element is set at ±10° In the range.

A linear guide comprising the separator defined by any one of the first to eighteenth aspects may be used.

According to the present invention, considering the radial length of separator expansion caused by lubricating oil or grease or the like, and the expanded thickness of the separator in the thickness direction (that is, the expanded radial thickness) (radial expansion causes The pitch of the separator is reduced, and the expansion in the thickness direction causes the pitch between the rolling elements to increase), the concave part of the separator contacts the rolling elements at a certain contact angle, at which the separator in the thickness direction The change in , thereby reducing the dimensional change of the separator caused by the expansion causing the change in the pitch between the rolling elements. Therefore, pitch variation between rolling elements caused by the influence of expansion caused by lubricating oil and grease or the like is suppressed, thereby easily achieving performance in operability, low noise, and low-cost durability aspect of improvement.

Description of drawings

Figure 1 is a perspective view of a linear guide;

Fig. 2 is a partial front sectional view of the linear guide shown in Fig. 1;

Fig. 3 is a cross-sectional view along the line III-III shown in Fig. 2;

Figure 4 is a side view of the separator shown in Figure 3;

Figure 5 is a plan view of the separator shown in Figure 3;

Figure 6 is a front view of the separator shown in Figure 3;

Fig. 7 is a longitudinal cross-sectional view along line VII-VII shown in Fig. 6;

Fig. 8 is a view showing a separator guide surface formed on the inside surface of the slider main body;

Fig. 9 is a perspective view (including a partial cross section) showing a simple structure of a linear guide (a linear guide) of an embodiment of the present invention;

Fig. 10 is a view (including a partial cross-section) representing the linear guide in the present embodiment, which is viewed along the linear motion direction shown in Fig. 9;

Fig. 11 shows the view of the roller and the separator in the present embodiment, wherein this figure is viewed along the direction perpendicular to the surface of the raceway;

Fig. 12 represents the view of the roller and separator shown in Fig. 11, and wherein this figure is to observe along the direction of linear movement;

Fig. 13 is a cross-sectional view along the A-A line shown in Fig. 12;

Figure 14 represents the view of the roller and separator shown in Figure 11, wherein this figure is viewed along the direction parallel to the roller axis (axis);

Figure 15 represents the view of the length of the "arm" in this embodiment;

Figure 16 represents the view of the length of the "arm" in this embodiment;

Figure 17 represents the view of the roller chain among the present embodiment;

Figure 18 represents the view of the contact angle defined between the "separator" and the "roller" in this embodiment;

Figure 19 represents the view of the "recessed surface" height of the present embodiment;

Figure 20 represents a view of the "drop" amount;

Fig. 21 shows the relationship between "the distance S from the reference position to the center of the roller" and the "drop amount B";

Figure 22 shows the view of an example of the R slope of the separator main body in the present embodiment;

Figure 23 shows the view of an example of the R slope of the separator main body in the present embodiment;

Figure 24A shows the view of an example of the lubricant reservoir of the present invention;

Figure 24B shows the view of the lubricant reservoir shown in Figure 24A, this view is to observe along the direction of linear motion;

Figure 25 A shows the view of another example of the lubricant reservoir of the present invention;

Figure 25B shows a view of the lubricant reservoir shown in Figure 25A, viewed along the direction of linear motion;

26 is a descriptive view showing a partial cross-sectional view of a portion of a linear guide having a separator for the linear guide of the present invention;

Figure 27 is a cross-sectional view of the linear guide along X-X shown in Figure 26;

Fig. 28 is a descriptive view showing in an enlarged manner the basic characteristics of the linear guide shown in Fig. 26;

Fig. 29 is a descriptive view showing in an enlarged manner the basic characteristics of the linear guide shown in Fig. 26;

30 is an enlarged view of a separator (for a linear guide) of the present invention, wherein FIG. 30A is a front view of the separator, FIG. 30B is a plan view of the separator, and FIG. 30C is a right side view of the separator;

Fig. 31A, B are partially enlarged views showing that the separator (for the linear guide) of the present invention constitutes a roller chain, which is sandwiched between adjacent rollers;

32A, B are descriptive views showing another embodiment of the separator (for linear guides) of the present invention;

33A, B are descriptive views showing another embodiment of the separator (for linear guides) of the present invention;

34A, B are descriptive views showing another embodiment of the separator (for linear guides) of the present invention;

35A, B are descriptive views showing another embodiment of the separator (for linear guides) of the present invention; and

36A, B are descriptive views showing how the separators of the present invention (for linear guides) fit together;

Figure 37 is a descriptive view showing a linear guide bearing, which is an example of this embodiment of the present invention;

Fig. 38 is a graph showing the relationship between the contact angle θ and the rolling element radius Dw corresponding to different values of δ at which the dimensional change of the separator due to expansion will be become smaller;

Fig. 39 is a graph showing the relationship between the contact angles θ and δ of each roller element radius Dw, where the dimensional change of the separator due to expansion becomes smaller at the contact angle θ;

Fig. 40 is a descriptive view showing a linear guide bearing of another embodiment of the present invention;

Fig. 41 is a partial sectional view showing a linear guide bearing using a roller-shaped roller as a rolling element, wherein the bearing is an example of a direct acting device;

Figure 42A, B represent the view that the separator is clamped between adjacent cylindrical rollers, wherein Figure 42A represents the linear motion region, and Figure 42B represents the redirection path region;

Fig. 43 represents the view of separator, and wherein this view is to observe along the direction of rotation of cylindrical roller;

Figure 44 is a top view of Figure 43;

Figure 45 is a side view of Figure 44; and

Fig. 46 is a graph showing the relationship between the contact angle θ and the difference in size between the expanded length in the thickness direction of the separator and the expanded radial length of the separator;

Detailed ways

Referring to the accompanying drawings, an embodiment of the present invention will be described below.

1 to 8 show an embodiment of the present invention. Fig. 1 is a perspective view of a linear guide. As shown, the linear guide 10 includes a guide rail 11, a slider 12 movably arranged on the guide rail 11, and a plurality of rolling elements 13 combined with the slider 12 (see FIGS. 2 and 3). A concave raceway 14 is formed on both left and right side surfaces of the guide rail 11 across the longitudinal direction of the guide rail 11 .

As shown in FIG. 1 , the raceway 14 includes raceway surfaces 141 and 142 . The included angle between the raceway surface 141 of the raceway surfaces 141 and 142 and the side of the guide rail 11 is greater than 90° (eg, 135°), wherein the raceway surface 141 is at a high position in the figure. Further, the raceway surface 142 at the lower position in the figure forms an included angle greater than 90° (such as 120°) with the side of the guide rail 11 in the direction opposite to the raceway surface 141 .

The slider 12 includes a slider body 121 and end caps 122, 123, wherein the end caps 122 and 123 are respectively connected to respective ends of the slider body 121 in the front-rear direction by using a plurality of locking screws. The slider body 121 has a lower surface 121 a opposite to the upper surface of the guide rail 11 . On the lower surface 121a of the slider main body 121, a rolling element fixing member 30 is attached. The slider body 121 has left and right inner side surfaces opposite to sides of the guide rail 11 . Rolling element fixtures 31 and 32 (see FIG. 2 ) are attached to each inner side surface of the slider main body 121 . A protruding raceway 16 is formed on each inner side surface of the guide rail 11 in the longitudinal direction.

The raceway 16 has raceway surfaces 161 and 162 (see FIG. 2 ). The angle formed between the raceway surfaces 161 and 162 of the raceway surface 161 and the inner surface of the slider main body 121 is greater than 90° (eg, 135°), wherein the raceway surface 161 is disposed at an upper position. Further, the angle formed by the raceway surface 162 at the lower end in the figure and the inner side surface of the slider main body 121 in the direction opposite to the raceway surface 161 is greater than 90° (such as 135°). The raceway surfaces 161 and 162 are disposed opposite to the raceway surfaces 141 and 142 of the raceway 14 . A rolling element raceway 17 (see FIG. 3 ) for rolling the rolling element 13 longitudinally on the guide rail 11 is formed between the raceway surfaces 141 and 161 and between the raceway surfaces 142 and 162 .

The slider body 121 has four through holes 18 penetrating the slider body 121 in the longitudinal direction of the guide rail 11 (see FIG. 2 ). A rolling element circulation assembly 19 fits into each through hole 18 . The rolling element circulation assembly 19 is formed in a cylindrical shape from a resin material. As shown in Figure 3, a rolling element return channel 21 - the channel 21 is connected with the rolling element redirecting channel 20 formed on the end caps 122 and 123 to form a rolling element redirecting channel - formed in each rolling element Each central portion of the circulation assembly 19.

When the slider 12 moves along the longitudinal direction of the guide rail 11 , the rolling element 13 rolls in the rolling element raceway 17 , and further rolls in the rolling element redirecting channel 20 and the rolling element returning channel 21 . Further, the rolling elements 13 are made in the shape of cylindrical rollers. The rolling elements 13 rolling between the raceways 141 and 161 are supported by the rolling element fixing assemblies 30 and 31 . The rolling elements 13 rolling between the raceways 142 and 162 are fixed by the rolling element fixing assemblies 31 and 32 . Further, each rolling element 13 is made of metal, ceramic or similar material. Further, a separator 22 (see FIG. 3 ) is interposed between roller-like rolling elements, wherein the separator 22 is made of a material softer than that of the rolling elements (such as resin).

As shown in FIGS. 4 to 6 , the separator 22 includes a separator body 221 and a pair of arm portions 222 , 222 disposed on each end of the separator body 221 . A separator guide groove 26 (refer to FIG. 2 ) is formed on the rolling element redirecting passage 20, the rolling element return passage 21 and the rolling element fixing assemblies 30 to 32, wherein the separator guide groove 26 is used to follow the direction of the rolling element 13. The rolling direction guides the arm 222 of the separator 22 .

The arm portions 222 , 222 are integrally formed with the separator 22 such that both ends of the arm portions 222 , 222 protrude in the longitudinal direction of the separator 22 . As shown in FIG. 4, the length L of the arm portions 222, 222 is shorter than the center-to-center distance of two adjacent rolling elements 13, 13 between which the separator main body 221 is sandwiched. . Preferably, the length L is approximately 50% to 98% of the rolling element diameter. The height H of the arms 222, 222 (see Fig. 4) is approximately 20% to 60% of the roller element diameter.

The lateral length L ₁ (see FIG. 5 ) of the separator body 221 is slightly shorter than the axial length of the rolling elements 13 . Therefore, at least one of the arm portions 222 , 222 is arranged to contact the shaft end surface of the rolling element 13 . The separator main body 221 has recessed surface portions 23, 23 provided on respective sides of the separator main body 221 with respect to the front-rear direction of the separator main body 221, the recessed surface portions 23, 23 contacting the rolling Circumferential portion of element 13. A clearance groove 24 is formed at the center of each recessed surface portion 23 in the circumferential direction of the rolling elements 13, the width of which is about 1/3 of the axial length of the rolling elements. A through hole 25 is also formed at the center of each recessed surface portion 23 to penetrate the recessed surface portion 23 in the front-rear direction of the separator 22 .

The separator main body 221 has both side surface portions 221a, 221b in the lateral direction (see FIGS. 5 and 6). One side surface of both side surface portions 221a, 221b is adjacent to the raceway surface 161, and contacts the separator guide surface 33a (see FIG. 8 ) formed on the inner side surface of the slider body 121, or is adjacent to the raceway surface 161. The track surface 162 and contacts the separator guide surface 33b. The separator guide surfaces 33a, 33b are integrally ground by a rotary grinder (not shown), and are ground simultaneously with the raceways 161, 162 . Either one of the left and right side surface portions of the rolling element 13 contacts the separator guide surfaces 33a and 33b. A plurality of bolt through holes 27 (see FIG. 1 ) are formed on the upper surface of the guide rail 11 at substantially equal intervals along the longitudinal direction of the guide rail 11 in the drawing. In the drawing, screw holes 28 for installing the slider are formed in a plurality of regions of the upper surface of the slider body 121 .

As described above, the gap between the rolling elements 13 and the separator main body 221 is prevented, and finally the reduction in the number of rolling elements provided in the bearing area is suppressed, and the linear guide disclosed in JP-B-40-24405 also This is advantageous because the length L between the arms 222 of the separator body 22 is shorter than the center-to-center distance of two adjacent rolling elements 13 , 13 . Therefore, skewing and mutual contact between the rolling elements can be suppressed without reducing the load carrying capacity. Also, the rotation resistance of the separator 22 is suppressed from being biased toward the rolling element 13, and the linear guide disclosed in JP-A-2001-132745 has such an advantage. Therefore, the effect of suppressing skew can be effectively produced.

Since the height H of the arm portion 222 is 20% to 60% of the diameter of the rolling element 13, the separator main body 221 can be reinforced by the arm portion 222, ensuring that there is a gap between the end surface of the rolling element 13 and the raceway contacting the end surface. full contact area.

Furthermore, since the clearance groove 24 is formed at the center of the recessed surface portion 23 in the circumferential direction of the rolling element 13, the contact area between the rolling element 13 and the separator 22 is limited on the left and right sides of the separator. Therefore, the operability of the linear guide can be improved while skewing of the rolling elements 13 can be suppressed. Further, since the through hole 25 is formed at the center of the recessed surface portion 23 to penetrate the recessed surface portion in the front-rear direction of the separator main body 221, lubricant can be stored in the through hole 25 and the lubricant stored in the through hole 25 The agent can be stably supplied into the rolling element 13. Separator guide surfaces 33 a , 33 b contacting side portions of the rolling elements 13 are provided on the inner side surface of the slider main body 121 . Therefore, the positions of the separator 22 and the rolling elements 13 become stable, thereby suppressing skewing of the rolling elements 13 .

The present invention is not limited to the above-described embodiments. For example, in this embodiment, the length L between the arm portions 222 is shorter than the center-to-center distance of two adjacent rolling elements 13 , 13 . However, the length L between the arm portions 222 may be equal to the center-to-center distance of two adjacent rolling elements 13 , 13 . In the preceding embodiments, the width of the clearance groove 24 is approximately one third of the axial length of the rolling element 13 . However, this width is not limited to approximately one-third. For example, the width may be approximately one-quarter to one-half the width of the slot.

An embodiment of the invention is described by the following figures.

FIG. 9 schematically shows the structure (including a partial cross-sectional portion) of a linear guide 301 according to the first embodiment of the present invention.

As shown in FIG. 9 , in the linear guide 301 in the present embodiment, a sliding member 330 is provided to fit around the guide rail 320 in a linearly movable manner and straddle it. Reference numeral 370 denotes an end cap, and 380 denotes a side seal.

FIG. 10 is a view (including a partially cutaway portion) of the guide rail 320 and the slide member 320 viewed along the linear motion direction shown in FIG. 9 . As shown in FIG. 10 , a track groove 321 is formed on either side of the guide rail 320 . The raceway groove 321 is formed on both side surfaces of the guide rail 320 and forms a concave shape having a substantially V-shaped cross section.

As shown in FIGS. 9 and 10, the sliding member 330 assembled around the guide rail 320 (wherein the guide rail 320 extends in a direction perpendicular to the plane of FIG. Opposite to the raceway groove 321, the convex shape of the convex portion 331 forms a convex shape with a V-shaped cross section.

The surface of the raceway groove 321 having a V-shaped cross section constitutes raceway surfaces 322A, 322B for the roller 340 . The surface of the raised portion 331 constitutes the raceway surface 332A, 332B for the roller 340, wherein the raised portion 331 faces the raceway surface 332A, 332B and has a V-shaped cross section. The surface of the raceway is preferably ground with high precision.

A plurality of rollers 340 as cylindrical or cylindrical rolling elements are interposed between the raceway surface 322A (or 322B) of the raceway groove 321 and the raceway surface 332A (or 332B) of the convex portion 331 . A separator (separation element) 350 is interposed between rollers 340 . FIG. 10 shows only the right portion of the guide rail 320 and the right portion of the sliding member 330 relative to the center of the guide rail 320 . However, the left portion of the guide rail 320 shown in FIG. 10 and the left portion of the slide member 330 relative to the center of the guide rail 320 are configured in the same manner as the right portion (ie, axially symmetrically about the center of the guide rail 320 ).

Here, the separator 350 interposed between the rollers 340 in this embodiment will be described.

As shown in Figure 11, the separator 350 of the present embodiment includes a separator main body 351 sandwiched between rollers 340, an arm portion 352 for guiding the end face 341 of the roller 340, wherein the roller 340 is arranged on the separator main body 351 sides, and a bridging portion 353 for connecting the separator main body 351 and the arm portion 352. The separator 350 can be integrally formed, such as using a resin material.

As shown in Figures 12, 13 and 14, the separator main body 351 is configured so that the recessed roller accommodating portion 354 is disposed on each side of the separator main body 351, and each recessed roller accommodating portion 354 is provided in contact with each side. The cylindrical outer peripheral portion of the roller 340 and accommodates the outer peripheral portion. Grooves 356 and through holes 357 serving as lubricant reservoirs are formed on the surface 355 of the receiving portion 354 which contacts the roller 340 . This embodiment shows an example of only one groove 356 . However, multiple grooves 356 may be formed depending on the desired lubricating properties. Similarly, multiple through holes 357 can also be formed. Also, either one of the groove 356 and the through hole 357 may be eliminated depending on the desired lubricating properties. Alternatively, both the groove 356 and the through hole 357 can be eliminated.

Rollers 340 - which are sandwiched between raceway surfaces 322A and 332A, and which roll through slide member 330 and thus through the load-bearing area (see FIG. 15 ) where a load is applied to rollers 340 - - and the separator 350, sandwiched between the rollers 340, is returned to the space between the (recirculating) raceway surfaces 322A and 332A (eg load area) through the circulation channel 333A (see Figures 9 and 10).

Rollers 340, which are sandwiched between raceway surfaces 322B and 332B and roll through the load-bearing area, and separator 350, sandwiched between rollers 340, pass through circulation channel 333B (see FIGS. 9 and 10 ) returns to the space between the (circulating) raceway surfaces 322B and 332B (ie, the load area).

As shown in FIGS. 9 and 10 , the circulation channel 333A is provided with a circulation pipe 334A to smoothly circulate the rollers 340 and the separator 350 so that the rollers 340 and the separator 350 roll on the raceway surfaces 322A and 332A. The circulation passage 333B is provided with a circulation pipe 334B to smoothly circulate the rollers 340 and the separator 350 so that the rollers 340 and the separator 350 roll on the raceway surfaces 322B and 332B. The circulation pipes 334A, 334B are provided with guide passages 335A, 335B that accommodate the rollers 340 and the separator 350 and circulate the rollers 340 and the separator 350 smoothly. The arm guide groove 336 is open on each circulation pipe so as to face the guide passages 335A, 335B, wherein the arm guide groove 336 guides the arm of the separator 350 during the circulation movement of the roller 340 and the separator 350 Section 352.

The circulation pipes 334A, 334B are preferably made of resin in view of smooth circulation operation to be achieved or manufacturing cost. Redirecting portions 337A, 337A are arranged on each end of the circulation pipe 333A along the direction of linear movement. Redirecting portions 337B, 337B are arranged on respective ends of the circulation pipe 333B along the linear movement direction of the circulation pipe 333B. In order to suppress mutual interference between the redirecting sections 337A, 337B, the circulation channels 333A, 333B are preferably arranged in a so-called chain manner.

As shown in FIG. 10 , this embodiment is provided with end surface guide members 361 , 362 and 363 for guiding the end surface 341 of the roller 340 and the arm portion 352 of the separator 350 . Therefore, skewing of the roller 340 or the like generated during rolling motion can be effectively suppressed, thereby enabling the roller 340 to operate smoothly.

The sliding member 330 of the present embodiment is provided with a roller end surface guide portion 338 for guiding the end surface of the roller 40 . Thus, skewing or the like occurring during the rolling motion of the roller 340 can be effectively suppressed, so that the roller 340 can be operated smoothly. The roller end guide portion 338 is ground with high precision and formed simultaneously with the rolling surfaces 332A, 332B.

The structure and working effect of the separator 350 in this embodiment will be described in detail below.

As shown in FIGS. 11 to 14 , each separator 350 in this embodiment has an arm portion 352 extending toward the rotation center (axis) of the adjacent roller 340 . The arm portion 352 and the separator body 351 are connected together by a bridge portion 353 . Therefore, the strength of the roller contact portion of the separator main body 351 can be improved. In particular, if the distance between the rollers is shortened in order to increase the bearing capacity by increasing the number of rollers provided in the bearing area, the roller contact portion of the separator body 351 will be thinned in the moving direction (ie, the direction of linear motion). As a result, the separator body 351 will be weakened. However, as shown in FIG. 14, the connection between the upper part and the lower part of the separator main body 351 will be strengthened by the bridge part 353 provided between the arm part 352 and the separator main body 351, thereby strengthening the separator main body 351. . For this reason, the distance between the rollers can be shortened without compromising the required strength. Therefore, even if the separator 350 is interposed between the rollers, the amount of reduction in the number of rollers provided in the load-carrying area can be minimized, and the drop in load-carrying capacity can be minimized.

Arm portion guide grooves 361A, 362A, and 363A respectively formed in the respective end surface guide members 361 , 362 , and 363 guide the arm portion 352 . Thus, the chances of the rollers 340 becoming detached or skewed from the separator body 351 can be minimized. As previously described, since the bridge portion 353 reinforces the separator body 351, the recessed surface depth Depth of the separator body 351 (ie, the number of accommodated rollers, see FIG. 17 ) is increased. This increase in depth is also effective in suppressing the chance of roll separation or suppressing skew.

Also, in the present embodiment, the fixing characteristics of the rollers are improved, thereby suppressing the rattling of the rollers 340 colliding with each other entering the bearing area where a load is applied to the rollers 340 . Finally, the impact sound energy generated by the rollers 340 and end caps 370 colliding with each other is reduced, thereby providing a low-noise linear guide and thus a device using the same.

As shown in FIG. 13, the "height of the arm portion 352" is preferably equal to or greater than 30% of the diameter of the roller in consideration of the aforementioned reinforcing effect. At the same time, under the premise of ensuring the contact area between the end surface 341 of the roller 340 and the end surface guide members 361, 362 and 363 for guiding the roller end surface 341, in order to guide the roller 340 smoothly, the arm portion 352 The height is preferably equal to or less than 50% of the roller 340 diameter. In particular, the "height of the arm portion 352" in the direction perpendicular to the raceway surface is preferably 30% to 50% of the roller diameter.

The "arm length" in the moving direction of the arm 352 will be described below (see FIG. 14 ).

The "arm length" in the moving direction of the arm 352 is set to a certain length so that the arms 352 of adjacent separator main bodies 351 can be prevented from contacting each other throughout the circulation path. This enables the smooth operation of the roller 340 and the separator body 351 , further enabling the smooth linear movement of the sliding member 330 .

Therefore, with respect to the length L (see FIG. 14 ) of the arm 352 provided on one side of the separator 350, the arm 352 of the separator 350 extends the same length toward the center of rotation of the roller 340 on both sides with respect to the direction of motion, As shown in Figure 15, assuming that the diameter of the roller is represented by Dwe, the center-to-center distance of adjacent rollers is represented by kDwe, wherein the separator 350 is sandwiched between two adjacent rollers, the radius of the moving track from the center of motion O to the center of motion of the rollers Denoted by R (where the roller is located at roller redirection portion 337A or 337B), from the center of motion O to the envelope surface - which is located closer to the center of motion than the dotted line and is defined by the arm 352 ( The height is defined by A) where the dotted line connects the centers of adjacent rollers - the radius is denoted Ri. At this time, the length Li of one side of the arm 352 (i.e. the length of the inner side of the arm), the position of this side is closer than the distance from the dotted line to the center of motion, wherein the dotted line connects the centers of adjacent rollers and the other side arm The length Lo (i.e. the length of the outer arm), which is set on the opposite side of the center of motion with respect to the dotted line connecting the centers of adjacent rollers, must satisfy the following equation:

θ=sin ^-1 {kDwe/(2R)}

0.3/2×Dwe≤A≤(R-Ri)

Li＜(kDwe/2-Asinθ)

Lo<kDwe/2

In particular, if the contour line of the arm portion 352 satisfying Li and Lo in the above equation is cut into an R-shape or an ellipse, mutual contact between the arm portions 352 can be avoided throughout the circulation path.

The most effective adaptive shape can be obtained when Li=kDwe/2-Asinθ and Lo=kDwe/2 are satisfied.

As shown in Figure 16, when the end portion of the arm portion 352 forms a single arc shape (the radius of the single arc is represented by A) in its moving direction, if the arm portion 352 side (that is, the length of the inner side of the arm portion) The maximum value Limax of the length Li is set to kDwe/2 where the side is located closer to the center of motion O than the dotted line connecting the centers of adjacent rollers, the arm 352 will interfere with the adjacent arm 352 (see dotted line in Figure 16). Here, kDwe denotes the center-to-center distance of adjacent rollers between which the separator 350 is sandwiched.

In order to avoid interference, it is assumed that the radius of the moving track from the center of motion O to the center of rotation of the roller, which is set at the roller redirection portion 337A or 337B, is represented by R, from the center of motion O to the envelope surface - the envelope surface The position at is closer to the center of motion than the dotted line connecting the centers of adjacent rollers—the radius of which is indicated by Ri—and is defined by the arm 352 (height A). At this time, the maximum value Limax of the inner arm length Li must satisfy the following equation:

θ'=sin ^-1 (kDwe/2R)

Limax＝kDwe/2-A×(1-cosθ′)/cosθ′

When the arms 352 of the separator 350 are configured to extend different lengths toward the centers of rotation of adjacent rollers relative to the direction of linear motion, the maximum length Ls (i.e. the total length the arms extend on each side of the separator) is required to be less than the corresponding The center-of-rotation distance kDwe of adjacent rollers arranged on each side of the separator 350 .

Referring to Figs. 17 and 18, a "gap (interval)" will be described below which is generated when the chain consisting of a plurality of rollers 340 and separators 350 moves to one side with respect to the moving direction.

The "gap" - which occurs when a chain of rollers 340 and separators 350 are set to one side relative to the direction of motion (see Figure 17) - cannot be eliminated in order to absorb fluctuations by To maintain smooth operation, such fluctuations in the length of the roller chain will occur as the rollers change their direction at the deflection section (337A or 337B).

On the contrary, if the "gap" is larger than the required value, the ability of the arm portion 352 to guide or fix the roller 340 will be impaired, and the effect of suppressing the roller from coming off and suppressing skew or the like will be impaired.

Therefore, according to the contact angle α defined between the roller 340 and the recessed surface 355 formed on either side of the separator body 351 and contacting and receiving the adjacent roller 340, it is considered to improve The role of accommodating rollers, when α = 0 (degrees) (that is, when the concave surface forms a single arc groove shape, and only has a single point of contact), "gap" - when the roller chain is biased relative to the direction of motion This gap is created when the recessed surface is on one side—it is best set to be equal to or less than one-half of the depth Depth of the recessed surface, or when the recessed surface forms a pinch-end arch (as shown in Figure 18, with two contacts point), the gap is preferably set to be equal to or less than one-half of the product of the depth of the recessed surface Depth and cosα.

Referring to Figures 19 to 20, the height of the recessed surface of the separator 350 (see Figure 13 or the like) will now be described.

As shown in FIG. 20, when the separator 350 is not sandwiched between the rollers 340, a phenomenon of a contact point occurs at the redirection portion (337A, 337B), the contact point exists between the rollers, and the roller is relatively The trajectory of the center of rotation moves toward the center of motion O (see the value of "Descent Amount B" in Figure 20). This phenomenon occurs as the separator 350 descends when the separator 350 is sandwiched between the rollers 340, as shown in FIG. 19 . The lowering of the separator 350 causes the separator 350 to contact the inner circumferential portion of the redirection portion (337A, 337B) at the redirection portion.

In this embodiment, with respect to the height of the recessed surface, which is the distance from the dotted line connecting the centers of adjacent rollers to the end face of the separator 350, the height Ho of the recessed surface in the redirected portion is more than the recessed The height Hi of the surface is larger, where height Ho is the distance from the imaginary line connecting the centers of rotation of adjacent rollers to the end of the separator 350 (this end being relative to the center of motion O), where height Hi is the distance from the point connecting the centers of rotation of adjacent rollers. The distance from the dotted line of the center of rotation to the nearest separator 350 (the nearest end is relative to the center of motion O).

Referring to Figures 19 and 20, a more specific embodiment is given. Here, when the separator 350 is sandwiched between adjacent rollers, the center-to-center distance of the adjacent rollers is represented by kDwe; the radius of the motion trajectory from the center of motion O to the center of the rollers located at the redirecting portion (337A or 337B) Indicated by R; taking a certain point as a reference point, where the roller moves from the movement track of the center of the roller to the redirection part, then the distance from the reference point to the center of the roller is represented by S (before the roller enters the redirection part This value is a negative value); the amount of descent of the separator 350 from the center of the roll track near the redirection portion is denoted by B. At this time, the descending amount of the separator 350 is defined by the following equation.

θ ₇ =tan ^-1 (-R/S)

θ ₈ ＝tan ^-1( -R/kDwe×sinθ ₃ )

θ ₃ =cos ^-1 {(2R ² +S ² -kDwe ² )/(2R×(R ² +S ² ) ^1/2 )}

B＝kDwe/2×sin(θ ₇ -θ ₈ )

In particular, if the above formula is used, the basic specifications of the roller 340 and the separator 350 are determined. The lowering amount B of the separator is only determined by the position of the rollers. For example, when kDwe=4.2mm and R=6.05mm, according to the above equation, the drop amount B of the separator is shown in FIG. 21 .

In order to prevent the separator 350 from contacting the inner peripheral portion of the redirecting portion, which occurs when the separator 350 descends toward the center of motion, the height of the recessed surface of the separator 350 is set to satisfy the following relationship: Hi<roller diameter/ 2-B and Ho-Hi≤B.

Similarly, for the width of the separator main body 351 (i.e. the size of the separator main body in the direction of movement), in the redirection portion, the end of the separator (the end is relative to the dotted line connecting the centers of rotation of the adjacent rollers) ), preferably greater than the width "b" of the most proximal end of the separator, (wherein the most proximal end is relative to the imaginary line connecting the centers of rotation of adjacent rollers, as shown in Figure 19). Curved surfaces formed on both sides of the separator 350 and fitted to the outer peripheral surfaces of the adjacent rollers 340 are assumed to have a negative curvature (ie, a concave surface) with respect to the width. Therefore, if the recessed surface height Hi, Ho is set to satisfy the aforementioned requirements (i.e. satisfy the relationship Hi<roller diameter/2-B and Ho-Hi≤B), the width of the separator main body 351 in the redirection portion (i.e. the separator The dimension in the moving direction) "a" is larger than the width "b".

Usually, the separator has a complicated shape, so the separator is considered to be manufactured at low cost in many cases. For this reason, plastics or elastomers, which can be molded, are used as materials for manufacturing the separator. However, the linear guide is a mechanical component, which usually uses lubricants or anti-corrosion agents during use or storage. Therefore, when the separator is made of elastic material or elastomer, it is difficult to completely eliminate swelling. Therefore, when the separator is sandwiched between the rollers, it will have a considerable influence on the center-to-center distance of the axes of rotation of the rollers. In a separator, the height is greater than the dimension between the recessed surfaces disposed on either side of the separator and accommodating the rollers in mutual contact. For this reason, if expansion occurs, the elongation in the height direction of the roller is large. The spacing between recessed surfaces tends to become smaller under the influence of elongation. Consequently, there would be a risk of the rollers coming off the separator, caused by the increased gap between the rolling chains in which the separator is sandwiched.

Therefore, in the present embodiment, in order to minimize the influence of the expansion of the space between the recessed surfaces, the contact surface 355 is formed so that the contact portion between the roller 340 and the recessed contact surface 355 of the separator 350 is at a position where At this position, the dimension between the recessed contact surfaces 355 formed on both sides of the separator 350 is the smallest. In particular, when the recessed contact surface 355 is a single arc, the optimum dimension of the contact surface 355 is R (radius), which is greater than half of the largest diameter of the roller 340 .

Since plastic or elastomer is more deformable than metallic materials, the gap between the roller chains between which the separator is sandwiched is likely to change elastically, so that roller detachment is likely to occur. For this reason, as shown in FIGS. 11 and 12 , skewing can be suppressed by making the axial length of the separator body 351 in the roller axial direction smaller than the roller length. Further, by making the width "a" larger than the width "b" shown in FIG. 19, an optimum value of the accommodation depth can be secured. By making the width "a" greater than the width "b" shown in FIG. 19, the roll-accommodating effect of the redirecting portions 337A, 337B will be enhanced. Therefore, the roller detachment phenomenon that occurs when the slide member 330 is moved away from the guide rail 320 is suppressed.

As shown in FIGS. 22 and 23, in the separator 350, the edge of the concave surface portion of the separator main body 351 is provided in an R slope or the like. The C slope can also be used instead of the R slope.

This embodiment describes a configuration in which there is a groove 356 and a through hole 357 serving as a lubricant reservoir, as shown in FIG. 12 . Also, the structure of the lubricant reservoir is not limited to this embodiment. More specifically, for example, the structures shown in Figs. 25A-25B can be employed.

In FIGS. 25A-25B, reference numeral 358 denotes a scroll groove formed on a recessed contact surface 355 near a contact portion between the contact surface 355 and the roller 340, thereby providing a wider range. Improves the effectiveness of the lubricant reservoir internally. In order to reduce manufacturing costs by eliminating errors in machining operations, scroll grooves 358 may be formed on the entire contact surface 355 .

In the linear guide in the present embodiment that has been described so far, the contact surface 355 of the separator main body 351 of the separator 350 is formed in a concave shape. Therefore, the roller 340 is well accommodated. Further, even if the separator 350 is sandwiched between the rollers, the distance between the centers of rotation of adjacent rollers can be minimized, and the number of rollers disposed in the loading area can be minimized.

The contact surface 355 has a concave shape, and the roller 340 is fixed on the arm 352 of the separator 350 . Further, there are guides 361 , 362 and 363 which guide the side surface 341 and the arm portion 352 of the roller 340 , and a roller end surface guide portion 338 which guides the end surface 341 of the roller 340 is provided. Therefore, detachment of the rollers can be effectively suppressed, and skewing can be sufficiently suppressed, thereby improving the operability of the linear guide. As a result, impact sound energy is reduced, and a low-noise operating linear guide is provided, thereby providing a low-noise operating device using the linear guide.

Further, if the contact surface 355 of the separator 350 has the groove 356, the through hole 357, and the scroll portion 358, the lubricating property is improved, and wear of the roller 340 and the separator 350 is suppressed.

In the separator main body 351 in this embodiment, if the arm portion 352 is prevented from contacting the separator main body 351, and if the axial length of the separator main body 351 in the roller axial direction is increased as much as possible, the stability of the roller is not impaired. In the case of motion, it can effectively restrain the unsuitable motion of the roller. Therefore, the rollers can be smoothly braked and skewing of the rollers can be effectively suppressed.

The structure described in this embodiment is just an example, and this embodiment can be modified within the scope of the technical spirit of the present invention.

Embodiments of a separator for a linear guide, and embodiments of a linear guide of the separator are combined in the present invention throughout the invention and will be described in detail below.

Fig. 26 is a descriptive view showing a partial sectional view of a linear guide with which the separator for the linear guide in the present invention is also combined. Fig. 27 is a cross-sectional view of the linear guide along the line X-X shown in Fig. 26 .

26 and 27, the linear guide 410 has a guide rail 412 and a slider 416, the guide rail 412 has a roller guide surface 414; the slider 416 straddles the guide rail 412 in a relatively movable manner, and has a bearing A roller guide surface 418 , which bears the roller guide surface 418 , is disposed opposite the roller guide surface 414 .

Two roller guide surfaces 414 are formed on either side surface of the guide rail 412 in the longitudinal direction; that is, a total of four roller guide surfaces 414 are formed in the longitudinal direction. The slider 416 is composed of a slider body 417 and an end cap 422 , wherein the end cap 422 is connected to any axial end of the slider body 417 .

When the slider body 417 and the end cap 422 are axially continuous with each other, they have a substantially C-shaped cross-section. A pair of redirection channels 424 are formed in the end cap 422 in connection with the ends of the carrying roller guide surface 418 . The slider 416 is composed of a slider body 417 and an end cover 422 connected to the shaft end of the slider body 417 .

A space - the space is defined between the roller guide surface 414 of the guide rail 412 and the bearing roller guide surface 418 of the slider body 417, wherein the bearing roller guide surface 418 is disposed opposite to the roller guide surface 414 - constitutes A roller path 426 . Each of the four continuous circulation passages 428 is constituted by a pair of redirection passages 424, a roller return passage 420 and a roller path 426, wherein the four circulation passages 428 are annularly continuous with each other.

A plurality of cylindrical rollers 446 serving as rolling elements are carried in the circulation channel 428 . The separator body 451 of the separator 450 is sandwiched between the adjacent rollers 446 , wherein the separator 450 is composed of the separator body 451 and the arm portion 452 . More specifically, the rollers 446 are sandwiched between the roller contacting surfaces 454a, 454b of the separator bodies 451 of adjacent separators 450 . Skewing of the roller 446 in the alignment direction can be suppressed by the pair of arm portions 452 , 452 . In this manner, the rollers 446 are constrained by the separator 450 , thereby forming a chain of separators 450 and rollers 462 .

In addition, a certain region of the linear guide 410 in which the roller chain 462 is integrated will be described in detail below.

As shown in FIGS. 26 and 28, except for the area where the bearing roller guide surface 418 is formed, the inner side of the slider main body 417 is covered by a separator guide 440 made of synthetic resin or the like. . Also, a small gap is formed between the separator guide 440 and the guide rail 412 disposed opposite to the separator guide 440 .

A groove into which the carrying roller guide surface 418 and the separator guide 440 are inserted is formed in a substantially C-shaped inner portion of the slider body 417 . More specifically, the groove is formed because the separator guide wall 436b is formed by the separator guide 440 . The distance W1 between the separator guide walls 436b which are disposed opposite to each other in the axial direction of the roller 446 is slightly larger than the length L of the cylindrical portion of the roller 446 . A guide groove 438b engaged with the arm portion 452 of the separator 450 is continuously formed on the separator guide wall 436b in the longitudinal direction. The width G of the separator guide wall 436b is slightly larger than the height U of the arm portion 452, so the arm portion 452 is slidably engaged inside the guide groove 438b.

As shown in FIGS. 27 and 29 , the roller return channel 420 is formed in the C-shaped thick sleeve portion of the slider body 417 so as to be spaced from and parallel to the load guide surface 418 by a certain distance. The roller return passage 420 is formed by a through hole 432 whose annular cross-section extends continuously in the longitudinal direction and into which the circulation pipe 430 is inserted.

The circulation pipe 430 is a pipe made of synthetic resin or the like. The cross-section of the inner space of the continuous circulation pipe 430 in the longitudinal direction is a rectangle, which is adapted to the cylindrical shape of the roller 446 protruding in the longitudinal direction, so that the roller 446 can penetrate the entire circulation pipe 430 . More specifically, the width W2 of the rectangular cross-section is slightly greater than the length L of the barrel portion of the roller 446 . The height H of the rectangular cross-section is slightly greater than the diameter Dw of the roller 446 . Therefore, the roller 446 and the separator 450 can move smoothly in the space of the circulation pipe 430 .

The wall portion of the circulation pipe 430 , which is disposed opposite to both sides of the roller 446 moving in the circulation pipe 430 , also serves as the separator guide wall 436 a. A guide wall 438a is continuously formed on the separator guide wall 436a in the longitudinal direction, and has a width such that it guides the arm portion 452 in an engaging manner. In particular, the width J of the guiding groove 438a is slightly larger than the height U of the arm portion. Accordingly, the arm portion 452 of the separator 450 is slidably engaged inside the guide groove 438a.

As shown in FIG. 27 , a pair of curved redirection channels 424 are formed on the end cap 422 , wherein the redirection channels 424 connect with the load roller guide surface 418 and communicate with the roller return channel 420 . The redirection channel 424 is formed by a continuous and curved through hole in the longitudinal direction.

In particular, the cross-section of the inner space of the diversion channel 424 is a rectangle, which is adapted to the shape of the cylindrical portion of the roller 446 protruding in the longitudinal direction, so that the roller 446 can pass through the diversion channel 424 . The walls of the deflection channel 424 also serve as separator guide walls, wherein the deflection channel 42 is arranged opposite to the sides of the rollers 446 moving in the deflection channel 42 . A dimension between the separator guide walls disposed opposite to each other in the axial direction of the roller 446 is slightly larger than the length L of the cylindrical portion of the roller 446 . The height of the rectangular cross-section is slightly greater than the diameter Dw of the roller 446 . Therefore, the roller chain 462 composed of the roller 446 and the separator 450 can move smoothly in the inner space of the redirection passage 424 . In the redirection channel 424, the entire roller chain 463 is moving when rolling. Therefore, considering that the radius of curvature matches the rotation range of the arm portion 452 , the width of the guide groove in the redirection channel 424 is slightly widened. The redirection channel 424 has the same cross section as the circulation pipe 430 of the roller return channel 420 . Therefore, the description of the cross-sectional portion of the redirection channel 424 is omitted here.

Next, referring to FIGS. 30A-31B , the separator 450 will be described in detail below. FIG. 30 is an enlarged view of the separator 450 , FIG. 30A is a front view of the separator 450 , and FIG. 30B is a plan view of the separator 450 . Figure 30C is a right side view of the separator. FIG. 31 is a partially enlarged view showing that the roller chain 461 is constituted by separators 450 interposed between rollers 446 .

The separator 450 is integrally formed of elastic synthetic resin. As shown in FIG. 30A , the separator 450 includes a separator body 451 and arms 452 , 452 .

The height V of the separator body 451 is smaller than the diameter Dw of the roller 446 . A roller contact surface 454 a is disposed opposite to an adjacent roller 446 , wherein the roller contact surface independently contacts the adjacent roller 446 . The other roller contact surface 454b is disposed opposite to the adjacent roller 446, wherein the roller contact surface 454b independently contacts the adjacent roller 446 in the direction opposite to the roller contact surface 454a. The roller contact surfaces 454a, 454b are formed by grooved surfaces adapted to the outer peripheral surface S (ie, grooved surfaces in this embodiment), so that the rollers 446 can be rotatably supported and fixed on adjacent separators 441, wherein the outer peripheral surface S is the rolling surface of the roller 446.

30B and 30C, in order to store the lubricant, the lubricant reservoir 456 penetrating from the roller contact surface 454a to the roller contact surface 454b is formed on the roller contact surfaces 454a, 454b from the opening portion 456a, each opening portion 456a has a predetermined shape (ie, rectangular in this embodiment) and predetermined dimensions.

A pair of arm portions 452, 452 are capable of rolling stably in the continuous endless channel 428 in a direction in which the rollers 446 are continuously aligned with the axes of the rollers 446 that are parallel to each other. More specifically, the arm portions 452 , 452 extend from the end of the separator body 451 toward the center of the adjacent roller 446 and protrude along the end surface of the roller 446 . Further, each arm portion 452, 452 has a predetermined height U guided by the guide groove 438a, 438b. As shown in FIG. 30B , the interval E between the pair of arm portions 452 is slightly larger than the length L of the cylindrical portion of the roller 446 . The height U (see FIG. 30A ) of the arm portion 452 is slightly smaller than the width of the guide grooves 438a and 438b. Accordingly, the arm portion 452 of the separator 450 is slidably engaged inside the guide grooves 438a and 438b.

Generally, in order to increase the amount of lubricant stored in the lubricant reservoir 456 and reduce the contact area between the lubricant reservoir 456 and the roller 446, the size of the opening portion 456a of the lubricant reservoir 456 is increased so that, when The lubricating effect is enhanced when the sliding resistance is reduced. Therefore, making the opening portion 456a larger within a certain range can achieve this effect. However, within this range, the rigidity of the separator main body 451 of the separator 450 can be ensured.

However, it is not that the separator is used in a certain product to achieve the required effect and function of the separator. For example, it is an important requirement to adopt a functional shape that contributes to an increase in productivity. In particular, an important issue faced was the use of a functional shape that would enable increased productivity in the assembly operation of sandwiching separators 450 between adjacent rollers 446 and then separating these sandwiched The device 450 is inserted into the continuous circulation channel 428.

For the separator 450, adopting a geometry enables the use of an automatic alignment machine, such as a feeder or the like, in order to easily align the separator and continuously assemble the aligned separator by using a robot or the like.

As shown in FIG. 30C , in order for the separator 450 to completely solve these problems, the separator 450 is configured to have an arm portion 452 having a structure constituting a roller chain 462 and a lubricant reservoir 456 . Maximum Dimensions of Lubricant Reservoir 456—comprising Height Y and Width Z, and Diagonal Dimensions of Lubricant Reservoir 456, Where Height Y and Width Z Define the Inside Diameter of Lubricant Reservoir 456 Rectangular Opening 456a— Smaller than another maximum dimension, which includes a height U and a width T, and a diagonal dimension, where the height U and width T define the outer dimensions of the arm portion 452 . Specifically, the arm portion 452 has an outer shape such that the free end of the arm portion 452 cannot fit into the opening portion 456a of the portion of the lubricant reservoir 456 formed on the roller contact surfaces 454a and 454b.

The effect of using the linear guide 410 of the separator of the present invention will be described in detail below.

In the linear guide 410 having the aforementioned configuration, when the slider 416 moves on the guide rail 412 in the axial direction of the guide rail 412, the roller 446 moves in the continuous circulation passage 428 while rolling, and the separator 450 also moves along with the roller. 440 move together in the continuous loop channel 428. At this time, the separator main body 451 of the separator 450 in the continuous circulation passage 428 pushes the roller 446 provided in front of the separator main body 451 in the moving direction of the separator main body 451 . Further, the roller 446 pushes another separator main body 451 disposed in front of the roller 446 in its moving direction. In short, the entire roller chain 462 circulates repeatedly in the continuous circulation channel 428 .

The roller chain 462 moves in the roller path 426 in the opposite direction to the movement of the slider 416 . The roller chain 462 enters a deflection channel 424 through the end of the roller path 462 connected to the deflection channel 424, in which the roller chain 462 changes its direction of motion. The roller chain 462 then enters the roller return channel 420 through the redirection channel 424 and moves in the same direction of movement as the slider 416 . The roller chain 462 then enters another redirection channel 424 in which the roller chain 462 changes its direction of motion again. The roller chain 462 then enters the roller path 426 . The roller chain 462 can repeat this cycle operation.

According to the linear guide 410, the separator main body 451 is interposed between the rollers 446, thereby preventing the rollers 446 from directly contacting each other, thereby suppressing noise and abrasion generated when the rollers 446 rub against each other. Further, the rollers 446 are sandwiched between the roller contact surfaces 454a and 454b of the adjacent separators 450 of each roller 446, and are fixed by the two contact surfaces. Roller 446 is adjusted by arm 452 of separator 450 . Therefore, the respective rollers 446 are kept in a normal state in which the central axes of the rollers pass through the separator 450 parallel to each other. When the rollers 446 are in a predetermined position and have a predetermined pitch, the rollers 446 can rotate and move stably in the circulation channel 428 .

Rollers 446 encounter resistance in roller path 426 . However, each roller 446 is pushed by the separator main body 451 disposed therebelow. Thus, roller 446 can move smoothly in roller path 426 . Further, the interval between the separator guide walls 436 b in the roller path 426 is slightly larger than the length of the cylindrical portion of the roller 446 . Accordingly, when the arm portion 452 of the separator 450 is engaged with the guide groove 438b of the separator guide wall 436b, the arm portion 452 of each separator 450 is guided. Thus, the deflection of each separator body 454 in the roller path 426 is more stably suppressed, and the hindrance of the smooth movement of the roller chain 462 caused by the undulation of the rolling chain 462 arrangement is also suppressed.

The arm portion 452 of the separator 450 is guided in the circulation passage 428 along the guide grooves 438a and 438b. Accordingly, fluctuations generated when the separator 450 moves are restricted, and fluctuations of the rollers 446 fixed between the arms 452 of the separator 450 can be restricted. Therefore, the entire roller chain 462 can move in the circulation passage 428 accurately and smoothly. Therefore, the axial fluctuation (skew) of the roller 446 can be effectively suppressed, so that no stress acts on the rolling chain 462 .

Also, the arm portion 452 of the separator 450 is engaged with the guide grooves 438a and 438b. The rollers 446 fixed between the separator bodies 451 are also supported and fixed by the roller contact surfaces 454a and 454b. Therefore, even if the slider 416 is removed from the guide rail 416, the roller 446 is prevented from being disengaged from the slider 416. Referring to FIG.

Also, a lubricant reservoir 456 for storing lubricant is formed by through holes formed on the roller contact surfaces 454a, 454b of the separator 450 . Since the separator 450 is used in the linear guide 410, the roller 446 can roll more smoothly, suppressing early wear of the roller 446 and generation of noise.

Further, the separator 450 is configured such that the opening portion 456 a of the lubricant reservoir is smaller than the outer dimension of the arm portion 452 . In particular, the maximum dimension of the lubricant reservoir 456—comprising the height Y and width Z of the lubricant reservoir 456, and the diagonal dimension, wherein the height Y and width Z define the rectangular opening 456a of the lubricant reservoir 456 - less than another maximum dimension, wherein the maximum dimension includes height U and width T, and a diagonal dimension, wherein the height U and width T define the outer dimension of arm 452 . Accordingly, arm portion 452 is prevented from fitting into lubricant reservoir 456 . For example, even if the separators 450 are automatically aligned by using a feeder or the like, entanglement between the separators 450 can be prevented. In particular, even if the separators 450 have accumulated in a bin or pile before being fed into the feeder, the separators 450 do not tangle within the bin or pile. Therefore, automation of production is facilitated, thereby providing a separator for a linear guide that can improve the productivity of the linear guide 410 .

The separator for the linear guide and the linear guide are incorporated in the present invention, and they are not limited to this embodiment.

For example, in this embodiment, the lubricant reservoir 456 penetrating from the roller contact surface 454a to the roller contact surface 454b is provided at one location. However, the separator of the present invention is not limited to this embodiment.

For example, as shown in FIG. 32, in another embodiment, the lubricant reservoir 456 penetrating from the roller contact surface 454a to the roller contact surface 454b can be arranged at multiple locations (such as three locations in the figure).

As shown in Figure 33, in another embodiment, a recess formed by a plurality of small indentations (indicated by a plurality of dots in the figure) is integrally formed in the main contact area between the roller and the separator, wherein In this embodiment the dimples are placed along the lubricant reservoir, thereby improving lubricity.

The formation position and shape of the lubricant reservoir are not limited to those described in this embodiment as long as the lubricant reservoir opening portion is smaller than the outer dimension of the arm, thereby inhibiting the arm from fitting into the lubricant reservoir. For example, when the roller contact surface formed on the separator main body 451 is a pinch-end arch shape or tapered, and when the roller contact surface contacts the roller, any contact angle can be produced on the roller contact surface, and the lubricant reservoir is formed in The contact portion with the corresponding contact angle. In particular, as shown in FIG. 34, in another embodiment, lubricant reservoirs may be formed in multiple locations (eg, six locations in the figure) in the oval groove.

As shown in FIG. 35 , in another embodiment, the small dimple shown in FIG. 33 is combined with the configuration shown in FIG. 34 . Therefore, any changes can be made to the embodiment within the scope of the present invention.

Also, in the present embodiment, regarding the dimensional relationship between the opening portion 456a of the lubricant reservoir 456 and the arm portion 452 preventing it from entering the opening portion, by making the size of the opening portion 456a smaller than the size of the arm portion, it is possible to achieve A rectangular relationship between width and height. However, this embodiment is not limited thereto.

The gist of the invention is that any shape can be used as long as it prevents a separator from fitting into another separator. In particular, considering the relationship between the shapes which facilitate the fitting of the arm into the lubricant reservoir portion, it is only required that the opening portion be substantially smaller than the outer dimensions of the arm. Accordingly, the maximum dimension (diagonal dimension if the opening portion is rectangular) of the opening portion 456a is smaller than the maximum dimension (diagonal dimension if the opening portion is rectangular) of the arm portion 456, wherein the arm portion The dimension 456 is the dimension of the cross-section lying perpendicular to the longitudinal direction of the arms 456, preventing the separators from fitting together. For example, if the arm has a ring-shaped cross-section viewed in the longitudinal direction of the arm, it is only required that the maximum dimension of the opening portion be smaller than the diameter of the ring. Moreover, if the arm has another combined geometry, the maximum dimension of the open portion is smaller than the maximum dimension of a single part shape of a shape obtained by embossing the arm in a direction that facilitates the assembly of the arm .

Here, the phrase "the opening portion is substantially smaller than the outer dimension of the arm" means that, as shown in FIG. Free ends are formed, in which case the separators 450 can be easily disengaged from each other even if the rounded ends of the arms 452 fit into the lubricant reservoir 456 . Thus, the phrase is also meant to include shapes that cannot cause mutual jamming. The reason is that if the relationship shown in Fig. 36A could be established, mutual fit between separators 456 would not occur. As shown in FIG. 36B, which shows an example in which the opening portion is larger than the outer dimension of the arm portion 452, this example can be expressed as an example in which mutual fit between the separators is produced.

Referring to the drawings, an embodiment of the present invention will be described below. Fig. 37 is a descriptive view showing a linear guide bearing which is also an embodiment of the present invention. Fig. 38 is a graph showing the relationship between the contact angle θ and the rolling element diameter Dw at different values of δ at which the change in size of the separator due to expansion becomes smaller. Fig. 39 is a graph showing the relationship between the contact angles ? and ? at which the dimensional change of the separator due to expansion becomes small at different values of the rolling element diameter Dw. Fig. 40 is a descriptive view depicting a linear guide bearing according to another embodiment of the present invention. Only the difference between the embodiment and the conventional linear guide bearing shown in FIG. 41 will be described.

As shown in FIG. 37, a linear guide bearing as an example in an embodiment of the present invention includes a separator main body 531 sandwiched between adjacent cylindrical rollers (rolling elements) 506, and a separator (separation element) 530, wherein the separator 530 is set so that the two-axis end faces of the cylindrical roller 506 are sandwiched between the separators 530. Arms (not shown) are integrally formed on each separator body 531 . A recessed surface portion 531 a fitting the outer circumferential shape of the cylindrical roller 506 is formed on a portion of the separator main body 531 disposed opposite to the outer circumferential surface of the cylindrical roller 506 .

An easily pourable material with high strength and self-elasticity is preferable as the manufacturing material of the separator 530 . For example, polyamide or elastomer can be used. Polyether ether ketone (PEEK), which has low self-elasticity but leaks a small amount of air leakage, can be used in the manufacture of vacuum equipment.

Also, a lubricant storage structure for the cylindrical roller 506 , such as a recess or an oil sump, is formed on the surface of the portion of the recessed surface 531 a that contacts the cylindrical roller 506 .

Here, in this embodiment, if the cross-section of the concave surface portion 531a is a pinch-end arch shape, the diameter of the cylindrical roller is represented by Dw, and the distance between the concave surface 531a of the separator main body 531 and the cylindrical roller 506 is The contact angle is represented by θ, the radius of the tip arch groove of the recessed surface 531a is represented by R, the groove bottom thickness of the separator recessed surface 531a is represented by 2δ, and the radius of curvature of the recessed surface is represented by "f", then the separation The contact angle θ of the device satisfies the following equations (1) to (3):

0.5Dw sinθtanθ＝δ+R(cosθ ₀ -cosθ) (1)

θ ₀ = sin ^-1 [{(2f-1)/(2f)}sinθ] (2)

f＝R/Dw (3)

In direct-acting devices, it is known that when a separator is sandwiched between rolling elements, the effective number of rolling elements of the load-bearing part becomes smaller, thereby affecting the load-carrying capacity and stiffness.

For example, take carrying capacity as an example. When the rolling elements are rollers, the ratio of the bearing capacity to the number of rollers is 0.75 (while, when the rolling elements are balls, the ratio of the bearing capacity to the number of rolling elements is 2/3). A reduction in load-carrying capacity and stiffness is unavoidable compared to a direct-acting device that does not use a sandwiched separator. However, the drop in load carrying capacity is required to be minimized. Generally, the drop rate of bearing capacity must be controlled at or below 10%. In particular, the filling rate of the rolling elements should be maintained at at least 88% or about 88%.

Usually, the number of rolling elements of direct acting devices is 10 to 20 in the load-bearing part per chain. Therefore, Table 1 shows the allowable ability to secure the bottom thickness 2δ (mm) of the recessed surface portion of the separator within a certain range in which the filling rate is maintained at 88%. Here, 2δ=[number of rolling elements×(1−filling rate of rolling elements)×diameter DW of rolling elements/(number of rolling elements−1)].

Table 1

Here, for example, when the rolling element diameter is 2 mm, the value of δ varies within a range of 0.055 mm to 0.165 mm. Fig. 37 shows the calculation results of the contact angle θ using formulas (1) to (3) at different values of δ when the diameter Dw of the rolling element is taken as a horizontal axis. At this point, the change in size of the separator due to expansion is minimal.

In Figure 37, considering the range of δ values set by the diameter Dw of each rolling element, the contact angle θ is most suitable between 19° and 35°, and the rolling elements are determined by the load capacity or stiffness shown in Figure 1 Adjustment.

When the diameter Dw of the rolling element is 10 mm, already exceeding 8 mm in Table 1, the upper limit of the contact angle θ is close to 40°. Determining the contact angle θ, which satisfies equations (1) to (3), can determine the optimal contact angle θ at which the deflection of the separator 530 caused by expansion can be reduced to minimum. Figure 39 shows the same information with the parameters in Figure 38 changed.

As described above, in this embodiment, by making the concave surface 531a of the separator 530 contact the cylindrical roller 506 at the optimum contact angle θ, the dimensional change generated between the cylindrical rollers 506 is caused by the expansion of the separator 530. Caused, can be reduced to a minimum, such dimensional changes are unavoidable for resin materials. Therefore, deterioration of the operability of the direct acting device due to the circulation of the cylindrical roller 506 and the separator 530 can be suppressed. Moreover, it is also easy to improve low noise and durability at low cost.

Referring to Fig. 40, a linear guide bearing in another embodiment of the present invention will now be described. As shown in FIG. 40, the linear guide bearing includes a separator body 541 interposed between adjacent cylindrical rollers (rolling elements) 506, and a separator 540, wherein the separator 540 is arranged so that the cylindrical rollers 506 The two-axis end faces of the separators 540 are sandwiched between the separators 540, and have arms (not shown) integrally formed on each separator body 541. A recessed surface 541 a conforming to the shape of the outer peripheral surface of the cylindrical roller 506 is formed on a portion of the separator main body 531 disposed opposite to the outer peripheral surface of the cylindrical roller 506 .

Here, in this embodiment, if the cross-section of the concave surface portion 541a is a single arc shape, the diameter of the cylindrical roller 506 is represented by Dw, and the diameter between the concave surface 541a of the separator main body 541 and the cylindrical roller 506 is The contact angle of the recessed surface 541a is represented by θ, the radius of the single arc-shaped groove of the recessed surface 541a is represented by R, the groove bottom thickness of the separator recessed surface 541a is represented by 2δ, and the radius of curvature of the recessed surface 541a is represented by "f" It means that the contact angle θ of the separator 540 satisfies the following equations (4) to (5), wherein the contact position range between the concave surface 541a and the cylindrical roller 506 is ±10° or less.

0.5Dw sinθtanθ＝δ+R(1-cosθ) (4)

f＝R/Dw (5)

The reason why the contact position range between the concave surface 541a and the cylindrical roller 506 is ±10 or less will be described below. When the contact position is set in a wide range, the deformation of the resin is initially large. However, the shape of the concave surface 541a is a single arc. Therefore, if the range of contact positions is set too wide, the cylindrical roller 506 is liable to make a large movement, resulting in an increase in frictional resistance. Therefore, it is inappropriate to set the range of contact positions wider. Therefore, the range of contact positions is set to a regular amount. On the other hand, the configuration and operational effects of this embodiment are the same as those of the foregoing embodiments. Therefore, explanations of the configuration and operational effects of the present embodiment are omitted here.

The present invention is not limited to the present embodiment and various changes are easily made within the scope of the gist of the present invention.

For example, various embodiments have been described in which the roller element is a roller. However, even when the rolling elements are implemented with rollers, the same effect can be achieved as long as the contact angle θ satisfies the above equation.

A linear guide bearing has been used in various embodiments as an example of a linear motion device. However, the invention is not limited to linear guide bearings. For example, the present invention can be applied to linear motion devices such as ball screws, ball splines and linear spherical bushings.

As described above, the invention of claim 1 prevents a decrease in the number of rollers provided in the load bearing area due to the gap created between the rolling elements and the separator. Therefore, contact and skew between rolling elements can be suppressed without reducing the load carrying capacity.

Besides producing the advantages of the present invention, the present invention reinforces the separator body by means of the arms and ensures sufficient contact between the end faces of the rolling elements and the raceways contacting the end faces of the rolling elements.

According to the present invention, the positions of the rolling elements become more stable, thereby effectively suppressing the skewing of the rolling elements.

According to the invention, the contact area between the separator and the rolling elements is limited to the left and right sides of the separator. Therefore, skewing of the rolling elements can be suppressed, thereby improving the operability of the linear guide.

According to the present invention, lubricant can be stored in the through hole, and the lubricant stored in the through hole can be stably delivered to the rolling elements.

According to the present invention, there is provided a linear guide capable of improving operability while suppressing skewing of rolling elements.

As described above, the present invention provides a separator for a linear guide, which can effectively suppress load-bearing capacity drop and skew, and can improve operability with a simple structure, and provides a separator including the separator A linear guide and a device comprising the linear guide.

Claims (3)

1. A linear motion device comprising - guide rails including rolling surfaces; a slider comprising a rolling surface opposite to that of the guide rail and guided by the guide rail via a plurality of rolling elements interposed between the rolling surfaces for relative movement; and a separator interposed between adjacent rolling elements and including a recessed surface portion formed in each of said spacer portions opposed to said rolling elements, The cross-section of the concave surface is a single arc shape; the diameter of the rolling element is represented by (Dw), and the contact angle between the separator and the rolling element is represented by (θ); the single arc groove of the concave surface part The radius is represented by (R); the groove bottom thickness of the concave surface part of the separator is represented by (2δ); the curvature radius of the concave surface part is represented by (f), and the contact angle (θ) of the separator satisfies the following equation (4) to (5): 0.5Dw sinθtanθ＝δ+R(1-cosθ) (4) f=R/Dw (5). 2. A linear motion device according to claim 1, wherein the contact position between the concave surface portion of the separator and the rolling element is within the range of ±10°. 3. A linear guide comprising the linear motion device of claim 1.

Images