JPS58622A - Direct-acting guide - Google Patents
Direct-acting guideInfo
- Publication number
- JPS58622A JPS58622A JP9455281A JP9455281A JPS58622A JP S58622 A JPS58622 A JP S58622A JP 9455281 A JP9455281 A JP 9455281A JP 9455281 A JP9455281 A JP 9455281A JP S58622 A JPS58622 A JP S58622A
- Authority
- JP
- Japan
- Prior art keywords
- shaft
- axial
- rollers
- guide
- axial direction
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C29/00—Bearings for parts moving only linearly
- F16C29/04—Ball or roller bearings
- F16C29/06—Ball or roller bearings in which the rolling bodies circulate partly without carrying load
- F16C29/0633—Ball or roller bearings in which the rolling bodies circulate partly without carrying load with a bearing body defining a U-shaped carriage, i.e. surrounding a guide rail or track on three sides
- F16C29/0669—Ball or roller bearings in which the rolling bodies circulate partly without carrying load with a bearing body defining a U-shaped carriage, i.e. surrounding a guide rail or track on three sides whereby the main body of the U-shaped carriage is an assembly of at least three major parts, e.g. an assembly of a top plate with two separate legs attached thereto in the form of bearing shoes
- F16C29/0673—Ball or roller bearings in which the rolling bodies circulate partly without carrying load with a bearing body defining a U-shaped carriage, i.e. surrounding a guide rail or track on three sides whereby the main body of the U-shaped carriage is an assembly of at least three major parts, e.g. an assembly of a top plate with two separate legs attached thereto in the form of bearing shoes with rollers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C29/00—Bearings for parts moving only linearly
- F16C29/001—Bearings for parts moving only linearly adjustable for alignment or positioning
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C29/00—Bearings for parts moving only linearly
- F16C29/04—Ball or roller bearings
- F16C29/06—Ball or roller bearings in which the rolling bodies circulate partly without carrying load
- F16C29/0602—Details of the bearing body or carriage or parts thereof, e.g. methods for manufacturing or assembly
- F16C29/0604—Details of the bearing body or carriage or parts thereof, e.g. methods for manufacturing or assembly of the load bearing section
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Bearings For Parts Moving Linearly (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は工作機械、産業機械等の各種機械類の構成にお
いて、往俵動移動台の直動案内を。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a linear motion guide for a reciprocating movable table in the construction of various types of machinery such as machine tools and industrial machinery.
移動台を支持する架台と、該架台を案内する軸との間に
、軸方向Ｋ１１１１転動する多数のころを介在させて構
成し、各種機械類の性能向上と。A large number of rollers that roll in the axial direction K1111 are interposed between a pedestal that supports a movable platform and a shaft that guides the pedestal, thereby improving the performance of various types of machinery.
構造の合理化に寄与することを目的としたもので１％に
従来品における転動体に球を用いるこの種直動案内と比
較し、負荷容量、剛性、並びに耐久性等に優れた直動案
内を実現しようとするものである。しかし上記球にかえ
てころを採用するこの種直動案内では、架台内に荷重を
支持して軸方向に転動した後繰返して循環するためのこ
ろの径路を合理的に形成すること力（困難であり、未だ
ころのみによるこの種直動案内は見うけられない。The aim is to contribute to streamlining the structure, and compared to this type of linear motion guide that uses balls as rolling elements in conventional products, this linear motion guide has superior load capacity, rigidity, and durability. This is what we are trying to achieve. However, in this type of linear motion guide that uses rollers instead of the balls mentioned above, it is necessary to rationally form a path for the rollers to support the load within the mount, roll in the axial direction, and then circulate repeatedly. This is difficult, and this type of linear motion guide using only rollers has not yet been seen.
本発明直動案内の特徴は、各々軸の上下、左右方向の荷
重を支持して循環する４組のころ夕１ｊの径路を架台内
に極めて合理的に形成して軸と架台のコンパクト化をは
かり、直動精度の向上はもとより、耐荷重性に優れ２％
に変動荷重下の案内精度の確保に必要とされる予荷重の
合理的な設定が容易なことで、この列構造の合理イヒと
ともに、直動案内の構成部品の形状を単純イヒし、高精
度、高能率加工方法の適用に留意し友ものである。The feature of the linear motion guide of the present invention is that the paths of four sets of rollers 1j, each of which supports and circulates the load in the vertical and horizontal directions of the shaft, are formed in the frame in an extremely rational manner, thereby making the shaft and the frame more compact. In addition to improving the linear motion accuracy of scales, it also has excellent load bearing capacity of 2%.
This makes it easy to rationally set the preload required to ensure guiding accuracy under fluctuating loads, which not only makes the row structure more rational, but also allows the simple shape of the component parts of the linear motion guide to achieve high precision. , it is a good idea to pay attention to the application of high-efficiency machining methods.
本発明直動案内の構造は、添付第１図と第２図の軸方向
正面図と側面図において、１は架台本体、２はころ、３
は周辺に互に交差した軸方向長円形状の、ころの循環転
勤用案内溝を有し。The structure of the linear motion guide of the present invention is shown in the axial front view and side view of the attached FIGS.
The roller has axially oval-shaped guide grooves for circulating the rollers that intersect with each other on the periphery.
周辺の部分を図示のようｉ軸方向に開瞼した丸軸、４は
軸３の軸端でころの転動溝に適応し。It is a round shaft with the peripheral part opened in the i-axis direction as shown in the figure, and 4 is the shaft end of the shaft 3, which is adapted to the rolling groove of the roller.
ころの循環転勤径路の形成用部品、５は架台本体ｌ内へ
の上記ころの循環転勤径路形成用構成部品３と４の軸方
向位置ぎめ用側板、６は両側面にころの転勤面を形成す
るために、軸方向の台形溝を成形した案内用軸、７は架
台と案内用軸６との間に介在させたダストシール、８は
移動台への架台取付用のねじ穴、９は側板５の架台本体
への固定ねじ、１０は取付ベースへの案内用軸６の固定
用ボルト穴である。図示のよ５に本発明直動案内は、架
台構成用の架台本体１と。Components for forming a circulating transfer path for rollers; 5 is a side plate for axial positioning of the components 3 and 4 for forming a circulating transfer path for rollers into the frame body l; 6 is a side plate for forming roller transfer surfaces on both sides; 7 is a dust seal interposed between the pedestal and the guide shaft 6, 8 is a screw hole for attaching the pedestal to the moving table, and 9 is a side plate 5. 10 is a bolt hole for fixing the guide shaft 6 to the mounting base. As shown in the figure, the linear motion guide of the present invention includes a gantry main body 1 for configuring a gantry.
架台本体内に装着される上記部品３と４により形成され
る循積径路内に供給した多数のころ。A large number of rollers are fed into the circulation path formed by the parts 3 and 4 mounted inside the frame body.
並に架台に適用する案内用軸６とより成り、これらの構
成部品中、架台本体ＩＫついては図示のように単純な直
方体形状ブロックの底面に開口端を有し、適応する案内
用軸との間に僅かの隙間を保ち、また案内用軸の両側面
に対応して成形した両日筒面に連らなる軸方向の内周面
を成形したものでちゃ、案内用軸については、軸方向の
直角断面が簡単な矩形状を基調とした軸の両側面ＫＦｇ
！Ｊ示の台形状軸方向の溝を成形した。Among these component parts, the mount main body IK has an open end at the bottom of a simple rectangular parallelepiped block as shown in the figure, and has a guide shaft 6 that is applied to the mount. The inner circumferential surface in the axial direction is molded to maintain a slight gap between the guide shafts, and the inner circumferential surface in the axial direction is molded to correspond to both sides of the guide shaft. KFg on both sides of the shaft based on a simple rectangular cross section
! A trapezoidal axial groove shown in J was formed.
簡単な形状より成る。Consists of simple shapes.
したがってこれらの平面と円筒面で形成された構成部品
は成形加工に際しても１通常の切削ならびに研削加工法
により高度の仕上り精度を期待することができる。Therefore, a high degree of finishing accuracy can be expected from the component parts formed by these planes and cylindrical surfaces by ordinary cutting and grinding methods when molding them.
添付第３図■乃至［Ｆ］は添付第１図、 ｆａ２図で示
した。軸３と、該軸の軸方向両端面に固定される部品４
との部分組立図の正面図と両側面図。Attached Figures 3 ■ to [F] are shown in attached Figure 1 and fa2. A shaft 3 and parts 4 fixed to both axial end surfaces of the shaft
A front view and both side views of a partially assembled drawing.
及び下面図と部分拡大図である。図示のように軸３には
、二組のころの循環用の転動溝が溝底を軸方向の長円形
状に、また二組の溝が軸方向の両端部で立体的に交差し
５るように 上記長円形状の溝底の軸方向の長さを異に
して成形し。and a bottom view and a partially enlarged view. As shown in the figure, the shaft 3 has two sets of rolling grooves for circulation of the rollers, the groove bottoms of which have an elliptical shape in the axial direction, and two sets of grooves that intersect three-dimensionally at both ends in the axial direction. The groove bottom of the above-mentioned oval shape is formed with different lengths in the axial direction.
該軸の軸方向両端部には２図示のように側板４を、軸に
適合する軸方向の片側端面に、二組の循環転動溝に対応
して相互に交差する凸部を成形１２．該凸部をころの転
動溝中に隙間なく嵌合するとともに、凸部の軸方向の端
面には、軸３の軸方向長円形状の溝底形状に対応してこ
ろの交差した循環径路を構成するための２円弧状の凹面
を、各々の循環径路に応じて軸方向の段差を与えて成形
し、上記軸３とその側板４で形成された。互に交差する
二組のころの循環径路中に１図示のようにころ２を供給
したものである。As shown in FIG. 2, side plates 4 are formed on both ends of the shaft in the axial direction, and convex portions that intersect with each other corresponding to the two sets of circulating rolling grooves are formed on one end surface in the axial direction that fits the shaft. The convex portion is fitted into the rolling groove of the roller without a gap, and the axial end face of the convex portion is provided with a circulation path where the rollers intersect, corresponding to the axially oval groove bottom shape of the shaft 3. Two circular arc-shaped concave surfaces were formed by providing steps in the axial direction according to each circulation path, and were formed by the shaft 3 and its side plate 4. As shown in Figure 1, rollers 2 are provided in the circulation path of two sets of rollers that intersect with each other.
また図中の１１は側板４の軸３への固定ねじ。Reference numeral 11 in the figure is a fixing screw for fixing the side plate 4 to the shaft 3.
１２は荷重負荷範囲で転動するころの転勤溝中からの脱
落防止のための板金で、第３図０に示すように、ころの
内筒面の軸方向両端部の逃げＷＪＫ図示のように、僅か
の隙間を保って配置され、ねじ１３１Ｃよシ軸３に固定
される。Reference numeral 12 denotes a metal plate for preventing the rollers rolling in the load range from falling out of the transfer groove. , are arranged with a slight gap and fixed to the shaft 3 by the screw 131C.
添付第４図（４）乃至Ｃ）は上記ころの転動溝を成形し
丸軸３の軸方向の正面図と側面図で９図中の１４はころ
の転動溝で９図示のように転動溝底は各々の循！ｌ径路
に対応して軸方向の長さを異にした軸方向の長円形状を
なし、また軸３の外周面の形状は、架台本体ｌの軸方向
内周面両側に成形し九、案内用軸６の側面に相対して開
口端を有している軸方向の円筒面に零に近い隙間を設定
し嵌合しさるように、軸方向の円ｆｔＪ面とし、上記架
台内の円筒面の開口部には、案内用軸６０両側面に成形
した台形状の軸方向台形溝の形状に対応し、これとの間
に僅かの隙間を保ち、軸方向台形状の面に成形される。Attached Figures 4 (4) to C) are a front view and a side view of the round shaft 3 in the axial direction after forming the rolling grooves of the rollers, and 14 in Figure 9 is the rolling groove of the rollers as shown in Figure 9. Each rolling groove bottom has its own circulation! The shaft 3 has an oval shape in the axial direction with different lengths in the axial direction corresponding to the path, and the shape of the outer circumferential surface of the shaft 3 is formed on both sides of the inner circumferential surface in the axial direction of the gantry main body L. A near-zero gap is set on the axial cylindrical surface that has an open end facing the side surface of the shaft 6, and the cylindrical surface in the mount is made into an axial circular ftJ surface so that they fit together. The opening corresponds to the shape of the trapezoidal axial trapezoidal groove formed on both sides of the guide shaft 60, and is formed into an axial trapezoidal surface with a slight gap between the guide shaft 60 and the trapezoidal groove.
この外回中の１５は上記軸３に対する側板４固定用の穴
、１６は軸方向長円形状の２組のころの転動溝底が、軸
方向の両端で交差位置に成形される＋方の転動溝に対す
る切欠の開口部である。In this outer rotation, 15 is a hole for fixing the side plate 4 to the shaft 3, and 16 is a hole in which the rolling groove bottoms of two sets of axially oval rollers are formed at intersecting positions at both ends in the axial direction. This is the opening of the notch for the rolling groove.
添付第５図（４）乃至０は、上記軸３の軸方向の両端面
に固定する側板４の正面図と両側面図。Attached FIGS. 5(4) to 5(a) are a front view and both side views of the side plate 4 fixed to both end surfaces of the shaft 3 in the axial direction.
並びに正面図の断面図を示した、上記のように側板４の
片側側面には、軸３の軸方向の両端部に近く１円弧形状
より成るころの溝底形状に対応して、二組のころの微積
径路を成形するための相互に交差した軸方向の二つの凸
部１７と１８を成形し、該凸部の各々の巾はころの転動
溝巾に一致して、これと隙間なく恢合し、また該軸３と
嵌合する凸部１７，１Ｂの端面は、軸３の溝底形状に対
応して図示の円弧状の円筒面より成シ、更に該円筒面形
状の端面は、相互に立体的に交差するころの循環径路を
形成する丸め２図示のように軸３の軸方向に段差を保ソ
て成形され、その際凸部１７に成形される円弧状端面の
大部分は側板内の円弧状溝形状に成形され、該溝の溝底
は側板４の側面１９に成形された角穴２０に連らなる。As shown above, on one side of the side plate 4, two sets of grooves are provided near both ends of the shaft 3 in the axial direction, corresponding to the shape of the groove bottom of the roller, which is in the shape of an arc. Two convex portions 17 and 18 in the axial direction that intersect with each other are formed to form the microvolume path of the roller, and the width of each convex portion corresponds to the rolling groove width of the roller, and there is a gap between the convex portions 17 and 18. The end surfaces of the convex portions 17 and 1B that fit together with the shaft 3 are made of an arcuate cylindrical surface as shown in the figure, corresponding to the groove bottom shape of the shaft 3, and the end surfaces of the cylindrical surface shape are formed. The rounding 2 forming the circulation path of the rollers intersecting each other three-dimensionally is formed by maintaining a step in the axial direction of the shaft 3 as shown in the figure, and the size of the arc-shaped end surface formed in the convex part 17 at this time is The portion is formed in the shape of an arcuate groove in the side plate, and the groove bottom of the groove is connected to a square hole 20 formed in the side surface 19 of the side plate 4.
また上記の角穴２０は、軸３の軸方向両端部で、軸方向
の長さを異にし、立体的に交差する二つの軸方向長円形
状ころの転動婢の成形において、上記の二つの溝の交差
する位置で、添付第４図の１６に示した位置における内
側で交差する循ｌＩ溝の成形上、外側と内側との両循壜
径路の隔離が不可能になり、これに伴い必要とされる軸
方向の凸部１８における隔壁２１の成形において、これ
を射出成形法で成形する金型の構成上成形されたもので
ある、また図中の２２は側板４を軸３に固定するための
ボルト穴である。In addition, the square holes 20 are formed at both axial end portions of the shaft 3 with different axial lengths, and are used in forming a rolling roller of two axially oval rollers that intersect three-dimensionally. At the position where the two grooves intersect, due to the shaping of the circulation grooves that intersect on the inside at the position shown at 16 in attached Figure 4, it becomes impossible to isolate both the outside and inside circulation channels, and as a result, In the molding of the partition wall 21 in the necessary axial convex portion 18, this was formed due to the configuration of the mold used to mold this by injection molding. Also, 22 in the figure is a part that fixes the side plate 4 to the shaft 3. This is a bolt hole for
つぎに上記互に交差するころの循環転勤径路を構成する
軸３と軸３の＠板４の成形加工について、軸８の軸方向
のころの転勤＃ｌＢ＃′ｉ丸軸からの冷間引抜、あるい
はプレス加工における冷間押出し等の成形後のフライス
加工による軸方向両端部の円弧状溝底と周辺の軸方向の
台形状面の成形を行い、ついで硬化熱処理の終了彼、ス
プライン研削盤等による溝底と溝の両側面の精密加工等
通常の加工方法によｐ高精度の成形が期待される。また
側板４の成形は切削加工方法では、高特度の成形が困難
である反面２合成樹脂、あるいは低融金属の射出成形法
により容易に行うことができ、これに用いられる金型の
成形は通常の加工方法により高精ＩＮＫ成形することが
できる。Next, regarding the forming process of the shaft 3 and the plate 4 of the shaft 3 that constitute the above-mentioned mutually intersecting roller rotation path, the roller transfer in the axial direction of the shaft 8 is performed by cold drawing from a round shaft. Or, by milling after forming such as cold extrusion in press processing, the arcuate groove bottoms at both axial ends and the surrounding trapezoidal surfaces in the axial direction are formed, and then the hardening heat treatment is completed. High-precision molding is expected using conventional processing methods such as precision processing of the groove bottom and both sides of the groove. In addition, while it is difficult to form the side plate 4 with high properties by cutting, it can be easily formed by injection molding of synthetic resin or low-melting metal, and the mold used for this process is High-precision INK molding can be performed using normal processing methods.
添付第６図（４）、ａ３）は本発明直動案内の耐荷重性
に対する説明図で２図因において、架台に作用する上下
、左右方向に作用する荷重は、架台内の荷重支持範囲の
ころ列と、案内用軸に成形した軸方向台形溝の斜面との
接触圧により支持される。また架台に変動荷重が作用す
る場合の予荷重の設定は、架台内で循環転動するころの
直径の選択によって行われ１図の）に示すようにころの
直径を１図（４）の場合よりも大きくした際には、荷重
支持範囲のｉころ列と案内用軸の転勤面間に、これに関
寿する架台本体、ころ、案内用軸等に生じた弾性変形に
伴う接触圧によって予荷重が作用し、動剛性の改善をは
かることができる。その際荷重支持範囲のころと、案内
用軸、並に架台内の転勤面の接触は１例えば図示のよう
に架台本体の両側面に角−妖の使みが生じた際にも、架
台本体内に嵌挿した軸３が、荷重支持範囲のころ２と案
内用軸６０転勤面との完全な接触を維持し、架台本体１
の変形に順応し黴少角又の旋回を生じて、正常に保たれ
、ころと上記転勤面間に片当りを生じることは々い。Attached Figure 6 (4), a3) is an explanatory diagram of the load capacity of the linear motion guide of the present invention. It is supported by the contact pressure between the roller row and the slope of the axial trapezoidal groove formed on the guide shaft. In addition, when a variable load is applied to the frame, the preload setting is done by selecting the diameter of the rollers that circulate and roll within the frame. When the load support range is larger than 1, the contact pressure caused by the elastic deformation of the mount body, rollers, guide shaft, etc. that are related to this is applied between the roller row i in the load supporting range and the transfer surface of the guide shaft. A load is applied and dynamic rigidity can be improved. At this time, contact between the rollers in the load-supporting range, the guide shaft, and the transfer surface inside the pedestal is ensured. The shaft 3 inserted into the frame body 1 maintains complete contact between the rollers 2 in the load-bearing range and the transfer surface of the guide shaft 60.
It adapts to the deformation of the roller and rotates at a low angle to maintain its normal state, and uneven contact between the roller and the transfer surface is unlikely to occur.
添付第７図囚、乃至口は本発明直動案内において、架台
の上下、左右方向に作用する荷重とこれに対応する直動
案内の負荷容量に関する説明図で、はじめに図の（４）
との）において添付第３図に示したように互に交差して
形成された。軸方向の長さを異にする二つの循環径路中
に供給したころの総数が相違すると共に、荷重支持間Ｈ
のころの数も異り、従って例えば図の囚に示した案内用
軸の両側面の軸方向台形溝の斜面に配置した二つの荷重
支持範囲のころ列において。Attached Figures 7 to 7 are explanatory diagrams regarding the loads acting in the vertical and horizontal directions of the pedestal and the corresponding load capacity of the linear motion guide in the linear motion guide of the present invention.
3), the two sections were formed so as to intersect with each other as shown in the attached Figure 3. The total number of rollers supplied to the two circulation paths with different axial lengths is different, and the load support distance H
The number of rollers is also different, thus, for example, in the rows of rollers in the two load-bearing areas arranged on the slopes of the axial trapezoidal grooves on both sides of the guide shaft shown in the upper part of the figure.
ころＫｆ！＋纏を施した径路中のころの数が、ころに斜
線を施さない側のころの数よりも多い場合には１図中の
下方のべ声ンル図で示したよ５に。KoroKf! If the number of rollers in the path with + lines is greater than the number of rollers on the side where the rollers are not shaded, please refer to 5 as shown in the bottom corner diagram in Figure 1.
直動案内としての負荷容量は左右方向では対称的に同一
であるが、上下方向には、上向に作用する荷重より吃下
向に作用する荷重に対しての負荷容量が大である。図（
Ｂ）Ｋ示し九実施例では。The load capacity as a linear motion guide is symmetrically the same in the left-right direction, but in the vertical direction, the load capacity is larger for loads acting downward than for loads acting upward. figure(
B) In the nine embodiments shown in K.
図（４）の場合と異り上向に作用する荷重への負荷容量
の方が、下向に作用する荷重に対する負荷容量よりも大
である。オた図のＣ）では、ころのａ項径路の構成部分
は図の（４）、ω）と同一で、案内用軸の両側面に成形
した。ころの転勤面となる軸方向の斜面の傾き角を相違
させ、これに架台内の上記ころの循環径路を対応させて
構成したもので、この実施例では図中のベクトル図に示
すように、上方の負荷容量に対し下方への負荷容量を大
にすることができる。一般に各種機械類に対するこの種
直動案内の適用においては。Unlike the case in FIG. 4, the load capacity for loads acting upward is larger than the load capacity for loads acting downward. In Figure C), the components of the a-term path of the rollers are the same as those in Figure (4) and ω), and are molded on both sides of the guide shaft. The inclination angles of the slopes in the axial direction, which are the transfer surfaces of the rollers, are made to differ, and the circulation path of the rollers in the frame is made to correspond to this.In this embodiment, as shown in the vector diagram in the figure, The downward load capacity can be increased relative to the upward load capacity. In general, in the application of this type of linear motion guide to various types of machinery.
水平面内で上方より作用する荷重のもとに往復動をする
移動台の外に、上下方向に往復動をする移動台の前後、
左右の１方向ａ面に直動案内を配置して拘束する場合の
ように、移動台に固定した架台の上下の位置の相違によ
り９図示した架台の上方と下方に対する荷重の大きさが
異り、直動案内に作用する荷重に対応し、負荷容量の選
択の可能性が重ｌ！になる。本発明の直動案内では図示
のよ５に、架台と案内用軸の形状。In addition to the moving table that reciprocates under a load applied from above in a horizontal plane, the front and back of the moving table that reciprocates in the vertical direction,
As in the case where a linear motion guide is placed and restrained in one direction (left and right) on plane A, the magnitude of the load on the upper and lower sides of the gantry shown in Figure 9 will differ due to the difference in the vertical position of the gantry fixed to the moving platform. , corresponding to the load acting on the linear motion guide, the possibility of selecting the load capacity is heavy! become. In the linear motion guide of the present invention, as shown in the figure, the shape of the pedestal and the guide shaft.
あるーは寸法等に何部の変更を畳することなく。Without having to make any changes to dimensions etc.
架台内の、荷重支持Ｉｉ８のころの数を１４ＫＬｌ二つ
のころ列の案内用軸の転勤面に対する配置の交替ＱみＫ
よシ、上記上下方内に負荷容量を異にし九直動案内管実
現することができる。The number of rollers for load support Ii8 in the frame is 14KLl Alternation of the arrangement of the guide shafts of the two roller rows with respect to the transfer plane Q
Alternatively, nine linear motion guide tubes can be realized with different load capacities in the upper and lower directions.
以上本発明においては、案内用軸と、移動台を支持し九
架台との間に循環して荷重を支持する転動体を介在させ
九直動案内において１球と比較し耐荷性、耐久性等にお
いて優れたころを転動体に採用し、構造簡単で高精度、
かつ耐荷重性、耐久性のほか、静的荷重に対する静画性
において優れているばかシでなく、動剛性の向上に不可
欠な予荷重の設定を容易に、Ｌか本合理的に設定しうる
とともに、架台に作用する荷重の方向と大きさに適応し
た負荷容量の配置が可能である。また本発明直動案内に
おける案内軸、架台本体、循環転勤径路の形成に関与す
る構成部品等は何れも通常の切削、研削加工、ブレス加
工、並に合成樹脂の射出成形法尋を合理的に適用するこ
とができ、高精度、高性能の直動案内を容易に実現する
ことができる。As described above, in the present invention, a rolling element that circulates and supports the load is interposed between the guide shaft and the movable table and the nine mounts, and in the nine linear motion guide, the load bearing capacity, durability, etc. are improved compared to one ball. Adopting excellent rollers for the rolling elements, the structure is simple and highly accurate.
In addition to its load-bearing capacity and durability, it is also excellent in static image performance against static loads, and the preload that is essential for improving dynamic rigidity can be easily and rationally set. At the same time, it is possible to arrange the load capacity in accordance with the direction and magnitude of the load acting on the frame. In addition, the guide shaft, mount body, and components involved in the formation of the circulation transfer path in the linear motion guide of the present invention can all be processed by normal cutting, grinding, pressing, and injection molding of synthetic resin. It is possible to easily realize high precision, high performance linear motion guide.
添付第１図と第２図は本発明直動案内の正面図と側面図
、＠３図はころの循環径路の構成部の部分組立図、第４
はころの循環径路構成用の転動溝を成形した軸の説明図
、第５図は同じくころの循環径路構成用の側板の説明図
、第６図と第７図は本発明直動案内の耐荷重に関する説
明図である。また上記図中の記号に対応して１、架台本
体
２ ころ
３、 ころの転動溝を成形した軸
４、軸３の側板
民 架体本体１の側板
６、 案内用軸
７、 ダストシール
８ 架台固定用ねじ穴
９、 側板５固定用ねじ
１０、案内用軸６固定用ボルト穴
１１ １１板４固定用ねじ
１２、、 ころの脱落防止用板金
１３ 板金１２固定用ねじ
１４、 軸３に成形したころの転動溝１１ 側板４
固定用ねじ穴
１６、 ころの転動溝底の切欠部
１７、１８’ 側板４の軸方向凸部
１９ ＠板４の軸方向片ｌＩ！端面
２０、端面１９に成形した角穴
２１、軸方向の凸部工８に成形した転勤ｌｌｌＩＣ壁
２２、＠板４の固定用ねじ穴
特許出願人
須 田
千 （左 行ｌ１１Ｆ −對昭不［
１夕２年／／ １１２ｒ日
井孔イｆＴ−′ｒ 長′白 島 １（１春
椿１ 殿１４＜Ｃ牛の浸水
・）召ｔｕ ｓ ｅｒ 、＜ｒ； 特許鮪 ’Ｅ０９
４５５２目２ 発明の名称
１ｒイ動室内
３ ＠市をする者
虫イ牛 と ｔｎ’■ ｆ系 セ許出加 人４ ン市
１− ａ合の日付 昭和ｓ ６１＋−】ｏ ＋１２７１
１５ 補正の７４ψ
ｌｖｉイ１１（４１２−５ｉン１）
６ 補正の内零 ど−ン１１（祇の・
由 リ ”’ ；に九〇
５２圀
（
１−Ａ′ｃ′ＪAttached Figures 1 and 2 are a front view and a side view of the linear motion guide of the present invention, Figure 3 is a partially assembled view of the components of the roller circulation path, and Figure 4 is a partially assembled view of the roller circulation path component.
Fig. 5 is an explanatory diagram of a shaft with rolling grooves formed thereon for configuring a circulation path for rollers, Fig. 5 is an explanatory view of a side plate for configuring a circulation path for rollers, and Figs. It is an explanatory diagram regarding load capacity. Also, corresponding to the symbols in the above figure, 1, frame body 2, rollers 3, shaft 4 with roller rolling grooves formed, side plate of shaft 3, side plate 6 of frame body 1, guide shaft 7, dust seal 8, frame Fixing screw holes 9, side plate 5 fixing screws 10, guide shaft 6 fixing bolt holes 11, plate 4 fixing screws 12, sheet metal 13 for preventing rollers from falling off, sheet metal 12 fixing screws 14, molded on the shaft 3 Roller rolling groove 11 Side plate 4
Fixing screw hole 16, notches 17, 18' at the bottom of the rolling groove of the roller, axial protrusion 19 on the side plate 4 @ axial piece lI of the plate 4! End face 20, square hole 21 formed on end face 19, transfer lllIC wall 22 formed on axial convex part 8, screw hole for fixing @ plate 4 Patent applicant Su Tasen (left row 11F - 對昭ふ [
1st night 2nd year // 112r Hii Koi fT-'r Cho' Hakushima 1 (1st spring
Camellia 1 Tono 14 <C Cow's soaking・) tu s er, <r; Patent tuna 'E09
4552 eyes 2 Name of the invention 1r i moving room 3 @ city playing person insect i cow and tn'■ f series Sekiyoshi 4 n city 1- a Date of match Showa s 61+-】o +1271
15 Correction of 74ψ lvii 11 (412-5in 1) 6 Correction of zero Don 11 (Gino・
9052 Kuni (1-A'c'J)
Claims (1)
する架台との間に、循環転勤を繰返して荷重を支持する
多数のころを介在させ九直動案内において、軸方向に直
角な断面形状が矩形状より成る軸の各々の両側面に傾斜
し九２面と平行面とより成る台形溝を軸方向に成形し、
＃両側面における各々の台形溝の二つの斜面を軸に荷重
を支持するころの転勤面として成形した案内用軸６と、
軸６！ｌＣ適合して往復動をする架台は。 外周面が直方体形状より成り、軸６に適応して底面に開
口した軸方向の凹部と、該凹部の両側面ＫＦｉ、軸６の
両側面に成形した上記軸方向の台形溝に対応して開口端
を有している軸方向の穴を成形した。鞍状の架台本体１
と、該架台本体ｌの上記軸方向の凹部の両側面に開目端
を有している軸方向の穴に適合させ、案内用軸１の上記
ころの転勤面に対応して、ころの転動溝を成形した軸３
と、＃軸３の側板４とにより構成したころの循環径路の
構成部分、および骸循漂径路中に多数のころを供給した
後、架台本体ｌに対する上記循環径路構成部分の軸方向
位置ぎめ用の側板５よ構成部、また上記架台内における
軸３とその側板４とで構成し九、ころの循環転勤径路の
形成について、軸３の周辺の軸方向と、軸方向両端部に
成形されるころの転動溝は。 案内用軸６の側面の台形溝内斜面の各々に対して、軸心
からの垂直方向に位置した軸３の片側周辺位置の軸方向
に荷重支持範囲のころの転動溝が、また骸軸方向転動溝
と相対する周辺位置の軸方向に循環のための軸方向転動
溝とが、互に平行に成形され、″またこれらの平行溝の
溝底面は、軸方向の両端で円弧状の曲面に連らなり。 これらの溝底の形状に対応して軸方向両端部の溝の側面
形状が定着る。また上記の溝底が軸方向長円形状より成
るころの転動溝は、案内用軸側面の上記軸方向台形溝の
二つの斜面に対応して細心よりの各々の斜面への垂直方
向に位置する軸の周辺に独立して成形されると共に、軸
３の軸方向の両端面では双方の溝が交差し、これらの案
内溝によって形成される軸方向長円形状のころの循環径
路の、軸方向の両端部で相互間にころの直径よりも僅か
に大きな段差を与え。 各々の循環径路中のころが相互に接触することなく転動
することができるように、軸３においては、上記の軸方
向長円形状より成る溝底の成形において、軸方向の両端
で交差する双方の溝底間に、ころの直径よりも大きい段
差を与えて成形し、また軸３０側板４においては、軸３
と接触する軸方向の片側端面に、上記軸３０両端面で互
に交差して成形されたころの案内溝と嵌合する。相互に
交差させて成形した軸方向の凸部の端面を、上記軸３の
各々の循環溝の溝底の軸方向両端部に成形した円弧状の
凸面に対応して、軸方向の両端部にころの循環径路を形
成するための円弧状の凹面に成形し、″また軸３の軸方
向両港で、各々の溝の成形において上記双方の案内溝の
交差する位置で、一方の案内溝が他方の案内溝底に対し
て開口された際の両案内溝を分離するための隔壁２１を
成形したことを特徴とする直動案内。 （２） 特許請求の範囲（１）記載の直動案内におい
て、ころの転勤用案内溝を成形し７た軸３の外周面の、
架台本体ｌの取付穴に嵌合させる範囲の形状を円筒形状
に成形し、架台内の荷重支持範囲のころが、案内用軸６
のころの転＠面に順応し、軸方向の片当りを回避して転
動することができるようにしたことを特命とする直動案
内。 （３）特許請求の範囲（１）記載の直動案内において、
循環転動するころの軸方向端部の円周面には傾斜逃げ面
が成形され、該ころを供給し丸軸３の転勤案内溝中で、
ころが案内用軸６０転勤面との同時接触を保ち荷重を支
持する範囲において、板金１２の軸方向の両端面を上記
ころの傾斜逃げ面に適用し、架台を案内用軸６から取外
した際の軸３からのころの脱落を防止したことを特徴と
する直動案内。[Claims] 113 In a nine-direction guide in which a large number of rollers that support a load by repeating cyclic transfer are interposed between a guide shaft and a frame that supports the reciprocating table, Forming in the axial direction a trapezoidal groove having a rectangular cross-section perpendicular to the axial direction, and sloping trapezoidal grooves consisting of 92 planes and parallel planes on both sides of each shaft;
#A guide shaft 6 formed by forming the two slopes of each trapezoidal groove on both sides as roller transfer surfaces that support loads as axes;
Axis 6! A frame that is compatible with IC and reciprocates. The outer circumferential surface has a rectangular parallelepiped shape, and an axial recess opening at the bottom to accommodate the shaft 6, and openings corresponding to the axial trapezoidal grooves formed on both sides KFi of the recess and the axial trapezoidal grooves formed on both sides of the shaft 6. An axial hole was formed with an end. Saddle-shaped mount body 1
The rollers are fitted into axial holes having open ends on both sides of the axial recess of the mount body l, and the rollers are aligned in correspondence with the roller transfer surfaces of the guide shaft 1. Shaft 3 with molded dynamic grooves
and the side plate 4 of the #shaft 3, and after supplying a large number of rollers to the skeleton circulation path, a roller for axial positioning of the circulation path component with respect to the mount body l. The side plate 5 and the side plate 4 are formed in the mount, and are formed in the axial direction around the shaft 3 and at both ends in the axial direction to form a circulating transfer path for the rollers. The rolling groove of the roller. For each of the slopes in the trapezoidal groove on the side surface of the guide shaft 6, the rolling grooves of the rollers in the load supporting range in the axial direction at the peripheral position on one side of the shaft 3 located perpendicularly from the shaft center are The directional rolling groove and the axial rolling groove for circulation in the axial direction at the peripheral position facing each other are formed parallel to each other, and the bottom surfaces of these parallel grooves are arcuate at both ends in the axial direction. Corresponding to the shape of these groove bottoms, the side shapes of the grooves at both ends in the axial direction are fixed.Furthermore, the rolling groove of a roller whose groove bottom has an elliptical shape in the axial direction is Corresponding to the two slopes of the above-mentioned axial trapezoidal groove on the side surface of the guide shaft, the grooves are formed independently around the shaft located in the direction perpendicular to each slope, and are formed at both axial ends of the shaft 3. Both grooves intersect with each other on the surface, and a step slightly larger than the diameter of the roller is provided between them at both axial ends of the axially oval circulation path of the roller formed by these guide grooves. In order to allow the rollers in each circulation path to roll without contacting each other, in the shaft 3, in forming the groove bottom of the above-mentioned axially oval shape, the rollers intersect at both ends in the axial direction. A step larger than the diameter of the roller is provided between the bottoms of both grooves, and the side plate 4 of the shaft 30 is formed with a step larger than the diameter of the roller.
The one end surface in the axial direction that contacts the shaft 30 is fitted with guide grooves of rollers formed so as to intersect with each other on both end surfaces of the shaft 30. The end surfaces of the axial convex portions formed to intersect with each other are formed at both axial ends in correspondence with the arc-shaped convex surfaces formed at both axial ends of the groove bottom of each circulation groove of the shaft 3. It is formed into an arcuate concave surface to form a circulation path for the rollers, and at both ports in the axial direction of the shaft 3, one guide groove is formed at the intersection of the two guide grooves in forming each groove. A linear motion guide characterized in that a partition wall 21 is formed to separate both guide grooves when they are opened to the bottom of the other guide groove. (2) A linear motion guide according to claim (1). In , the outer circumferential surface of the shaft 3 on which the roller transfer guide groove was formed 7,
The area to be fitted into the mounting hole of the pedestal main body l is formed into a cylindrical shape, and the rollers in the load supporting area within the pedestal are aligned with the guide shaft 6.
A linear motion guide whose special purpose is to adapt to the rolling surface of the rollers and allow rolling while avoiding uneven contact in the axial direction. (3) In the linear motion guide described in claim (1),
An inclined relief surface is formed on the circumferential surface of the axial end of the roller that rotates in circulation, and the roller is fed into the transfer guide groove of the round shaft 3.
In the range where the rollers maintain simultaneous contact with the transfer surface of the guide shaft 60 and support the load, both end surfaces of the sheet metal 12 in the axial direction are applied to the inclined relief surfaces of the rollers, and when the mount is removed from the guide shaft 6. A linear motion guide characterized by preventing rollers from falling off the shaft 3.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9455281A JPS58622A (en) | 1981-06-20 | 1981-06-20 | Direct-acting guide |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9455281A JPS58622A (en) | 1981-06-20 | 1981-06-20 | Direct-acting guide |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS58622A true JPS58622A (en) | 1983-01-05 |
| JPS6224646B2 JPS6224646B2 (en) | 1987-05-29 |
Family
ID=14113473
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9455281A Granted JPS58622A (en) | 1981-06-20 | 1981-06-20 | Direct-acting guide |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58622A (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59212516A (en) * | 1983-05-13 | 1984-12-01 | Hiroshi Teramachi | Linear sliding bearing |
| JPS60139912A (en) * | 1983-12-28 | 1985-07-24 | Tsubakimoto Seikou:Kk | Roller type bearing for linear motion |
| US4702623A (en) * | 1985-10-01 | 1987-10-27 | Sro Kugellagerwerke, J. Schmid-Roost | Linear bearing for continuous longitudinal movement |
| US4765754A (en) * | 1987-05-12 | 1988-08-23 | The United States Of America As Represented By The Secretary Of Commerce | Inclined contact recirculating roller bearing |
| JPH064427U (en) * | 1992-06-23 | 1994-01-21 | プルトンチエン株式会社 | Ball circulation type linear guide |
| DE4431286A1 (en) * | 1993-10-07 | 1995-04-13 | Rixen Wolfgang | Linear guide |
| US6318895B1 (en) | 1999-03-25 | 2001-11-20 | INA Wälzlager Schaeffler oHG | Linear rolling bearing element |
| JP2004504569A (en) * | 2000-07-25 | 2004-02-12 | イナーシエツフレル コマンディートゲゼルシャフト | Linear rolling bearing |
| EP1653097A1 (en) * | 2003-07-25 | 2006-05-03 | THK Co., Ltd. | Linear guide device with offset-load prevention mechanism |
| JP2018063730A (en) * | 2015-06-30 | 2018-04-19 | キヤノンマーケティングジャパン株式会社 | Program, information processing device, and processing method thereof |
| JP3217850U (en) * | 2018-06-22 | 2018-09-06 | 上銀科技股▲分▼有限公司 | Linear guide with lubricating oil passage |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1971845U (en) * | 1967-07-13 | 1967-11-02 | Guenter Goebel | ROLLER BEARING. |
| JPS53152043U (en) * | 1977-05-06 | 1978-11-30 |
-
1981
- 1981-06-20 JP JP9455281A patent/JPS58622A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1971845U (en) * | 1967-07-13 | 1967-11-02 | Guenter Goebel | ROLLER BEARING. |
| JPS53152043U (en) * | 1977-05-06 | 1978-11-30 |
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59212516A (en) * | 1983-05-13 | 1984-12-01 | Hiroshi Teramachi | Linear sliding bearing |
| JPS6148006B2 (en) * | 1983-05-13 | 1986-10-22 | Hiroshi Teramachi | |
| JPS60139912A (en) * | 1983-12-28 | 1985-07-24 | Tsubakimoto Seikou:Kk | Roller type bearing for linear motion |
| US4702623A (en) * | 1985-10-01 | 1987-10-27 | Sro Kugellagerwerke, J. Schmid-Roost | Linear bearing for continuous longitudinal movement |
| US4765754A (en) * | 1987-05-12 | 1988-08-23 | The United States Of America As Represented By The Secretary Of Commerce | Inclined contact recirculating roller bearing |
| JPH064427U (en) * | 1992-06-23 | 1994-01-21 | プルトンチエン株式会社 | Ball circulation type linear guide |
| DE4431286A1 (en) * | 1993-10-07 | 1995-04-13 | Rixen Wolfgang | Linear guide |
| DE4431286C2 (en) * | 1993-10-07 | 1998-05-28 | Rixen Wolfgang | Linear guide |
| US6318895B1 (en) | 1999-03-25 | 2001-11-20 | INA Wälzlager Schaeffler oHG | Linear rolling bearing element |
| JP2004504569A (en) * | 2000-07-25 | 2004-02-12 | イナーシエツフレル コマンディートゲゼルシャフト | Linear rolling bearing |
| JP4681209B2 (en) * | 2000-07-25 | 2011-05-11 | シエツフレル コマンディートゲゼルシャフト | Linear rolling bearing |
| EP1653097A1 (en) * | 2003-07-25 | 2006-05-03 | THK Co., Ltd. | Linear guide device with offset-load prevention mechanism |
| EP1653097A4 (en) * | 2003-07-25 | 2011-11-30 | Thk Co Ltd | Linear guide device with offset-load prevention mechanism |
| JP2018063730A (en) * | 2015-06-30 | 2018-04-19 | キヤノンマーケティングジャパン株式会社 | Program, information processing device, and processing method thereof |
| JP3217850U (en) * | 2018-06-22 | 2018-09-06 | 上銀科技股▲分▼有限公司 | Linear guide with lubricating oil passage |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6224646B2 (en) | 1987-05-29 |
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